EP3147078B1 - Handheld machine tool - Google Patents

Handheld machine tool Download PDF

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Publication number
EP3147078B1
EP3147078B1 EP16189706.1A EP16189706A EP3147078B1 EP 3147078 B1 EP3147078 B1 EP 3147078B1 EP 16189706 A EP16189706 A EP 16189706A EP 3147078 B1 EP3147078 B1 EP 3147078B1
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EP
European Patent Office
Prior art keywords
gear
ring
ring gear
planet carrier
toothing
Prior art date
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Application number
EP16189706.1A
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German (de)
French (fr)
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EP3147078A1 (en
Inventor
Jochen Erhardt
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Hilti AG
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Hilti AG
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Publication date
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Publication of EP3147078A1 publication Critical patent/EP3147078A1/en
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools

Definitions

  • the present invention relates to a handheld power tool, in particular an electric screwdriver according to the preamble of claim 1 and as shown in FIG EP 2 631 038 A1 known.
  • the hand machine tool according to the invention is equipped with the features according to claim 1. Further modifications can be found in the subclaims.
  • the planetary gear with the switching ring can be built compactly.
  • Fig. 1 shows an electric screwdriver 1 as an example of a handheld power tool.
  • the electric screwdriver 1 has a tool holder 2 in which a rotating tool 3, for example a drill or a screwdriver bit, can be inserted and locked.
  • An electric motor 4 drives the tool holder 2 about a working axis 5 .
  • the electric motor 4 is arranged in a machine housing 6 to which a handle 7 for holding and guiding the electric screwdriver 1 is attached during operation.
  • the user can put the electric screwdriver 1 into operation by means of a system switch 8.
  • the electric motor 4 is supplied with power when the user operates the system switch 8.
  • a The power source can be a battery pack 9 attached to the machine housing 6 or the handle 7 or a mains connection.
  • a switchable planetary gear 10 is arranged in the drive train between the electric motor 4 and the tool holder 2.
  • a slide 11 outside the machine housing 6 actuates the planetary gear 10.
  • the slide 11 can be shifted by the user into a first switching position or a second switching position.
  • the slide 11 can be moved along the transmission axis 12 or transversely to the transmission axis 12 , in the latter case a shift gate converts the circumferential movement into an axial movement.
  • the planetary gear 10 changes its reduction ratio depending on the switching position of the slide 11.
  • the planetary gear 10 has a sun gear 13, a planet carrier 14 with several planet gears 15 and a first ring gear 16 arranged on a gear axis 12.
  • the sun gear 13 is preferably arranged on the drive side; the first ring gear 16 is arranged on the output side.
  • the sun gear 13 can, for example, be coupled directly to the electric motor 4.
  • On the exemplary first ring gear 16 a gear 17 is arranged, which meshes with a further gear.
  • the planet carrier 14 has three shafts 18 or bearings, on each of which a planet gear 15 is rotatably mounted about the axis of the shaft 18.
  • the number of planet gears 15 is exemplary and is preferably in the range between three and seven planet gears 15.
  • the planet gears 15 each have two different toothings 19, 20.
  • the first toothing 19 has a larger diameter than the second toothing 20.
  • the number of teeth of the first toothing 19 and the second toothing 20 is the same.
  • the first toothing 19 meshes with the sun gear 13 and the first ring gear 16.
  • a width of the first toothing 19 is preferably equal to a width of the sun gear 13 and the toothing of the first ring gear 16. The width specifies the dimension along the transmission axis 12 .
  • the second toothing 20 can be wider than the first toothing 19 .
  • the second toothing 20 meshes neither with the sun gear 13 nor with the first ring gear 16.
  • a second ring gear 21 is also arranged coaxially on the transmission axis 12.
  • the second ring gear 21 is freely rotatable with respect to the first ring gear 16.
  • the first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance.
  • the second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15.
  • the second ring gear 21 is preferably as wide as the second toothing 20.
  • An outer diameter of the second ring gear 21 is smaller than an outer diameter of the first ring gear 16.
  • the outer diameter of the second ring gear 21 and an outer diameter of the planetary carrier 14 can advantageously be identical.
  • the second ring gear 21 and the planet carrier 14 are arranged adjacent along the gear axis 12 at a fixed, unchangeable distance.
  • the planetary gear 10 is arranged in a gear housing 22 which is fastened in the machine housing 6 or is formed by the machine housing 6 .
  • the planetary gear 10 has a switching ring 23 which is displaceable along the gear axis 12.
  • the switching ring 23 is coupled to the slide 11 in such a way that the switching ring 23 is in a first position ( Figs. 2, 4 and 5 ) reaches when the slide 11 is in the first switching position and the second position ( Figures 6, 7 and 8 ) arrives when the slide 11 is in the second switching position.
  • the connection of the switching ring 23 to the slide 11 can take place via a rigid linkage or via tracking springs.
  • the switching ring 23 is prevented from rotating about the transmission axis 12 in the transmission housing 22 .
  • the switching ring 23 can have radial projections 24 which engage in axially extending grooves 25 in the gear housing 22.
  • the radial projections 24 have, for example, a semi-cylindrical cross section, but their cross section can also have a different shape, for example prismatic, rectangular.
  • the grooves 25 have a corresponding complementary cross section, and to allow a guide along the transmission axis 12 of rotation in order to inhibit the transmission axis 12th
  • the switching ring 23 can have axially extending grooves and the gear housing can have radial projections which engage in one another analogously.
  • the switching ring 23 overlaps along the gear axis 12 with the planet carrier 14; In the second position, the shift ring 23 overlaps along the gear axis 12 with the second ring gear 21.
  • the shift ring 23 which is prevented from rotating, blocks either the planet carrier 14 or the second ring gear 21 from rotating about the gear axis 12. The reduction of the planetary gear 10 changes accordingly .
  • the exemplary switching ring 23 has claws 26 projecting radially inward.
  • the second ring gear 21 has recesses 27 complementary to the claws 26 and the planetary carrier 14 has recesses 28 complementary to the claws 26 .
  • the switching ring 23 engages with the claws 26 either exclusively in the second ring gear 21 or in the planet carrier 14 .
  • the shape of the claws 26 and associated recesses 27, 28 are designed in such a way that a sufficient form fit is formed for transmitting a torque from the switching ring 23 to the second ring gear 21 or the planet carrier 14 .
  • the exemplary jaws 26 have one semi-cylindrical cross-section, the cross-section can also be prismatic, rectangular, etc.
  • the switching ring 23 can be provided with cutouts, into which claws of the second ring gear 21 and claws of the planet carrier 14 engage.
  • the switching ring 23 is arranged between the second ring gear 21 and the planet carrier 14 and engages either with end-shaped claws 26 in the second ring gear 21 or in the planet carrier 14 to keep one of the two elements rotating to prevent the transmission axis 12 .
  • FIGS. 9 to 12 show an embodiment of a planetary gear 29.
  • the planetary gear 29 has on a transmission axis 12 is arranged a sun gear 13, a planet carrier 14 having a plurality of planet gears 15 and a first ring gear 16.
  • the planet carrier 14 has four shafts 18 and bearings, on each of which a planetary gear 15 to the axis of the shaft 18 is rotatably mounted.
  • the planet gears 15 each have two different toothings 19, 20.
  • the first toothing 19 has a larger diameter than the second toothing 20.
  • the number of teeth of the first toothing 19 and the second toothing 20 is the same.
  • the first toothing 19 meshes with the sun gear 13 and the first ring gear 16.
  • a second ring gear 21 is arranged coaxially on the transmission axis 12.
  • the second ring gear 21 is freely rotatable with respect to the first ring gear 16.
  • the first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance.
  • the second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15.
  • the planetary gear 29 has a switching ring 30 which is displaceable along the gear axis 12.
  • the switching ring 23 is prevented from rotating by cams 31 engaging in the gear housing 22.
  • the switching ring 30 is coupled to the slide 11 in such a way that the switching ring 30 reaches a first position when the slide 11 is in the first switching position and that moves into a second position when the slide 11 is in the second switching position.
  • the switching ring 23 has a first spur toothing 32 which, in the first position, engages in a spur toothing 33 of the second ring gear 21.
  • the switching ring 23 has a second spur toothing 34 which, in the second position, engages in a spur toothing 35 of the planet carrier 14.
  • the switching ring 23 is accordingly arranged between the second ring gear 21 and the planet carrier 14 or their spur teeth 33, 35 . In the first position, the switching ring 23 inhibits the second ring gear 21 from rotating and releases the planet carrier 14 to rotate; In the second position, the switching ring 23 prevents the planet carrier 14 from rotating and releases the second ring gear 21 to rotate.

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

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine, insbesondere einen Elektroschrauber nach dem Oberbegriff von Anspruch 1 und wie aus EP 2 631 038 A1 bekannt.The present invention relates to a handheld power tool, in particular an electric screwdriver according to the preamble of claim 1 and as shown in FIG EP 2 631 038 A1 known.

Aus ergonomischen Gesichtspunkten erweist sich ein kurzer Aufbau von Elektroschraubern als vorteilhaft.From an ergonomic point of view, a short construction of electric screwdrivers is advantageous.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Die erfindungsgemäße Handwerkzeugmaschine ist mit den Merkmalen nach Anspruch 1 ausgestattet. Weitere Modifikationen sind den Unteransprüchen zu entnehmen.The hand machine tool according to the invention is equipped with the features according to claim 1. Further modifications can be found in the subclaims.

Das Planetengetriebe mit dem Schaltring lässt sich kompakt aufbauen.The planetary gear with the switching ring can be built compactly.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die nachfolgende Beschreibung erläutert die Erfindung anhand von exemplarischen Ausführungsformen und Figuren. In den Figuren zeigen:

Fig. 1
einen Elektroschrauber,
Fig. 2
ein Planetengetriebe in erster Schaltstellung im Längsschnitt in der Ebene II-II;
Fig.3
das Planetengetriebe im Querschnitt in der Ebene III-III;
Fig. 4
das Planetengetriebe in erster Schaltstellung im Querschnitt in der Ebene IV-IV;
Fig. 5
das Planetengetriebe in erster Schaltstellung im Querschnitt in der Ebene V-V;
Fig. 6
ein Planetengetriebe in zweiter Schaltstellung im Längsschnitt in der Ebene II-II;
Fig. 7
das Planetengetriebe in zweiter Schaltstellung im Querschnitt in der Ebene VII-VII;
Fig. 8
das Planetengetriebe in zweiter Schaltstellung im Querschnitt in der Ebene VIII-VIII;
Fig. 9
ein Planetengetriebe im Längsschnitt;
Fig. 10
das Planetengetriebe im Querschnitt in der Ebene X-X
Fig. 11
das Planetengetriebe im Querschnitt in der Ebene XI-XI
Fig. 12
das Planetengetriebe in einer Explosionsdarstellung
The following description explains the invention on the basis of exemplary embodiments and figures. In the figures show:
Fig. 1
an electric screwdriver,
Fig. 2
a planetary gear in the first switching position in longitudinal section in plane II-II;
Fig. 3
the planetary gear in cross section in the plane III-III;
Fig. 4
the planetary gear in the first switching position in cross section in plane IV-IV;
Fig. 5
the planetary gear in the first switching position in cross section in the plane VV;
Fig. 6
a planetary gear in the second switching position in longitudinal section in plane II-II;
Fig. 7
the planetary gear in the second switching position in cross section in plane VII-VII;
Fig. 8
the planetary gear in the second switching position in cross section in plane VIII-VIII;
Fig. 9
a planetary gear in longitudinal section;
Fig. 10
the planetary gear in cross section in plane XX
Fig. 11
the planetary gear in cross section in plane XI-XI
Fig. 12
the planetary gear in an exploded view

Gleiche oder funktionsgleiche Elemente werden durch gleiche Bezugszeichen in den Figuren indiziert, soweit nicht anders angegeben.Identical or functionally identical elements are indicated by the same reference symbols in the figures, unless otherwise stated.

AUSFÜHRUNGSFORMEN DER ERFINDUNGEMBODIMENTS OF THE INVENTION

Fig. 1 zeigt einen Elektroschrauber 1 als Beispiel für eine Handwerkzeugmaschine. Der Elektroschrauber 1 hat einen Werkzeughalter 2, in welchem ein drehendes Werkzeug 3, z.B. ein Bohrer, ein Schrauberbit, eingesetzt und verriegelt werden kann. Ein Elektromotor 4 treibt den Werkzeughalter 2 um eine Arbeitsachse 5 an. Der Elektromotor 4 ist in einem Maschinengehäuse 6 angeordnet, an welchem ein Handgriff 7 zum Halten und Führen des Elektroschraubers 1 während des Betriebs befestigt ist. Der Anwender kann den Elektroschrauber 1 mittels eines Systemschalters 8 in Betrieb nehmen. Der Elektromotor 4 wird mit Strom versorgt, wenn der Anwender den Systemschalter 8 betätigt. Eine Stromquelle kann ein an dem Maschinengehäuse 6 oder dem Handgriff 7 befestigtes Batteriepaket 9 oder ein Netzanschluss sein. Fig. 1 shows an electric screwdriver 1 as an example of a handheld power tool. The electric screwdriver 1 has a tool holder 2 in which a rotating tool 3, for example a drill or a screwdriver bit, can be inserted and locked. An electric motor 4 drives the tool holder 2 about a working axis 5 . The electric motor 4 is arranged in a machine housing 6 to which a handle 7 for holding and guiding the electric screwdriver 1 is attached during operation. The user can put the electric screwdriver 1 into operation by means of a system switch 8. The electric motor 4 is supplied with power when the user operates the system switch 8. A The power source can be a battery pack 9 attached to the machine housing 6 or the handle 7 or a mains connection.

In dem Antriebsstrang zwischen dem Elektromotor 4 und dem Werkzeughalter 2 ist ein schaltbares Planetengetriebe 10 angeordnet. Ein Schieber 11 außerhalb des Maschinengehäuses 6 betätigt das Planetengetriebe 10. Der Schieber 11 kann von dem Anwender in eine erste Schaltposition oder eine zweite Schaltposition verschoben werden. Der Schieber 11 kann längs der Getriebeachse 12 oder quer zu der Getriebeachse 12 bewegt werden, wobei bei letzterem eine Schaltkulisse die umfängliche Bewegung in eine axiale Bewegung umsetzt. Das Planetengetriebe 10 ändert seine Untersetzung in Abhängigkeit der Schaltposition des Schiebers 11. A switchable planetary gear 10 is arranged in the drive train between the electric motor 4 and the tool holder 2. A slide 11 outside the machine housing 6 actuates the planetary gear 10. The slide 11 can be shifted by the user into a first switching position or a second switching position. The slide 11 can be moved along the transmission axis 12 or transversely to the transmission axis 12 , in the latter case a shift gate converts the circumferential movement into an axial movement. The planetary gear 10 changes its reduction ratio depending on the switching position of the slide 11.

Das Planetengetriebe 10 hat auf einer Getriebeachse 12 angeordnet ein Sonnenrad 13, einen Planetenträger 14 mit mehreren Planetenrädern 15 und ein erstes Hohlrad 16. Das Sonnenrad 13 ist vorzugsweise antriebsseitig angeordnet; das erste Hohlrad 16 ist abtriebsseitig angeordnet. Das Sonnenrad 13 kann beispielsweise direkt mit dem Elektromotor 4 gekoppelt sein. An dem beispielhaften ersten Hohlrad 16 ist ein Zahnrad 17 angeordnet, das mit einem weiteren Getriebe kämmt. Der Planetenträger 14 hat drei Wellen 18 oder Lager, auf denen jeweils ein Planetenrad 15 um die Achse der Welle 18 drehbar gelagert ist. Die Zahl der Planetenräder 15 ist beispielhaft und liegt vorzugsweise im Bereich zwischen drei und sieben Planetenrädern 15. The planetary gear 10 has a sun gear 13, a planet carrier 14 with several planet gears 15 and a first ring gear 16 arranged on a gear axis 12. The sun gear 13 is preferably arranged on the drive side; the first ring gear 16 is arranged on the output side. The sun gear 13 can, for example, be coupled directly to the electric motor 4. On the exemplary first ring gear 16 , a gear 17 is arranged, which meshes with a further gear. The planet carrier 14 has three shafts 18 or bearings, on each of which a planet gear 15 is rotatably mounted about the axis of the shaft 18. The number of planet gears 15 is exemplary and is preferably in the range between three and seven planet gears 15.

Die Planetenräder 15 haben jeweils zwei verschiedene Verzahnungen 19, 20. Die erste Verzahnung 19 hat einen größeren Durchmesser als die zweite Verzahnung 20. Die Anzahl der Zähne der ersten Verzahnung 19 und der zweiten Verzahnung 20 ist gleich. Die erste Verzahnung 19 kämmt mit dem Sonnenrad 13 und dem ersten Hohlrad 16. Eine Breite der ersten Verzahnung 19 ist vorzugsweise gleich einer Breite des Sonnenrads 13 und der Verzahnung des ersten Hohlrads 16. Die Breite gibt die Abmessung längs der Getriebeachse 12 an. Die zweite Verzahnung 20 kann breiter als die erste Verzahnung 19 sein. Die zweite Verzahnung 20 kämmt weder mit dem Sonnenrad 13 noch mit dem ersten Hohlrad 16. Ein zweites Hohlrad 21 ist ebenfalls koaxial auf der Getriebeachse 12 angeordnet. Das zweite Hohlrad 21 ist gegenüber dem ersten Hohlrad 16 frei drehbar. Das erste Hohlrad 16 und das zweite Hohlrad 21 sind benachbart längs der Getriebeachse 12 und in einem festen, unveränderlichem Abstand angeordnet. Das zweite Hohlrad 21 kämmt dauerhaft mit der zweiten Verzahnung 20 der Planetenräder 15. Vorzugsweise ist das zweite Hohlrad 21 so breit wie die zweite Verzahnung 20. Ein Außendurchmesser des zweiten Hohlrads 21 ist geringer als ein Außendurchmesser des ersten Hohlrads 16. The planet gears 15 each have two different toothings 19, 20. The first toothing 19 has a larger diameter than the second toothing 20. The number of teeth of the first toothing 19 and the second toothing 20 is the same. The first toothing 19 meshes with the sun gear 13 and the first ring gear 16. A width of the first toothing 19 is preferably equal to a width of the sun gear 13 and the toothing of the first ring gear 16. The width specifies the dimension along the transmission axis 12 . The second toothing 20 can be wider than the first toothing 19 . The second toothing 20 meshes neither with the sun gear 13 nor with the first ring gear 16. A second ring gear 21 is also arranged coaxially on the transmission axis 12. The second ring gear 21 is freely rotatable with respect to the first ring gear 16. The first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance. The second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15. The second ring gear 21 is preferably as wide as the second toothing 20. An outer diameter of the second ring gear 21 is smaller than an outer diameter of the first ring gear 16.

Der Außendurchmesser des zweiten Hohlrads 21 und ein Außendurchmesser des Planetenträgers 14 können vorteilhafterweise identisch sein. Das zweite Hohlrad 21 und der Planetenträger 14 sind längs der Getriebeachse 12 benachbart in einem festen, unveränderlichen Abstand angeordnet.The outer diameter of the second ring gear 21 and an outer diameter of the planetary carrier 14 can advantageously be identical. The second ring gear 21 and the planet carrier 14 are arranged adjacent along the gear axis 12 at a fixed, unchangeable distance.

Das Planetengetriebe 10 ist in einem Getriebegehäuse 22 angeordnet, welches in dem Maschinengehäuse 6 befestigt ist oder durch das Maschinengehäuse 6 ausgebildet ist. Das Planetengetriebe 10 weist einen Schaltring 23 auf, der längs der Getriebeachse 12 verschiebbar ist. Der Schaltring 23 ist mit dem Schieber 11 derart gekoppelt, dass der Schaltring 23 in eine ersten Stellung (Fig. 2, 4 und 5) gelangt, wenn der Schieber 11 in der ersten Schaltposition ist, und der in eine zweite Stellung (Fig. 6, 7 und 8) gelangt, wenn der Schieber 11 in der zweiten Schaltposition ist. Die Anbindung des Schaltrings 23 an den Schieber 11 kann über ein starres Gestänge oder über nachführende Federn erfolgen. Der Schaltring 23 ist in dem Getriebegehäuse 22 gegen ein Drehen um die Getriebeachse 12 gehemmt. Beispielsweise kann der Schaltring 23 radiale Vorsprünge 24 aufweisen, welche in axial verlaufende Nuten 25 in dem Getriebegehäuse 22 eingreifen. Die radialen Vorsprünge 24 haben beispielhaft einen halbzylindrischen Querschnitt, deren Querschnitt kann jedoch auch eine andere Form, z.B. prismatisch, rechteckig, aufweisen. Die Nuten 25 haben einen entsprechend komplementären Querschnitt, um eine Führung längs der Getriebeachse 12 zu ermöglichen und eine Drehung um die Getriebeachse 12 zu hemmen. Alternativ oder zusätzlich kann der Schaltring 23 axial verlaufende Nuten und das Getriebegehäuse radiale Vorsprünge aufweisen, die analog in einander eingreifen.The planetary gear 10 is arranged in a gear housing 22 which is fastened in the machine housing 6 or is formed by the machine housing 6 . The planetary gear 10 has a switching ring 23 which is displaceable along the gear axis 12. The switching ring 23 is coupled to the slide 11 in such a way that the switching ring 23 is in a first position ( Figs. 2, 4 and 5 ) reaches when the slide 11 is in the first switching position and the second position ( Figures 6, 7 and 8 ) arrives when the slide 11 is in the second switching position. The connection of the switching ring 23 to the slide 11 can take place via a rigid linkage or via tracking springs. The switching ring 23 is prevented from rotating about the transmission axis 12 in the transmission housing 22 . For example, the switching ring 23 can have radial projections 24 which engage in axially extending grooves 25 in the gear housing 22. The radial projections 24 have, for example, a semi-cylindrical cross section, but their cross section can also have a different shape, for example prismatic, rectangular. The grooves 25 have a corresponding complementary cross section, and to allow a guide along the transmission axis 12 of rotation in order to inhibit the transmission axis 12th As an alternative or in addition, the switching ring 23 can have axially extending grooves and the gear housing can have radial projections which engage in one another analogously.

In der ersten Stellung überlappt der Schaltring 23 längs der Getriebeachse 12 mit dem Planetenträger 14; in der zweiten Stellung überlappt der Schaltring 23 längs der Getriebeachse 12 mit zweiten Hohlrad 21. Der selbst am Drehen gehinderte Schaltring 23 blockiert somit wahlweise den Planetenträger 14 oder das zweite Hohlrad 21 am Drehen um die Getriebeachse 12. Die Untersetzung des Planetengetriebes 10 ändert sich entsprechend.In the first position, the switching ring 23 overlaps along the gear axis 12 with the planet carrier 14; In the second position, the shift ring 23 overlaps along the gear axis 12 with the second ring gear 21. The shift ring 23 , which is prevented from rotating, blocks either the planet carrier 14 or the second ring gear 21 from rotating about the gear axis 12. The reduction of the planetary gear 10 changes accordingly .

Der beispielhafte Schaltring 23 hat radial nach innen vorstehende Klauen 26. Das zweite Hohlrad 21 weist zu den Klauen 26 komplementäre Aussparungen 27 und der Planetenträger 14 weist zu den Klauen 26 komplementäre Aussparungen 28 auf. Der Schaltring 23 greift entsprechend seiner Stellung mit den Klauen 26 wahlweise exklusiv in das zweite Hohlrad 21 oder in den Planetenträger 14 ein. Die Form der Klauen 26 und zugehörigen Aussparungen 27, 28 sind derart gestaltet, dass sich ein ausreichender Formschluss zum Übertragen eines Drehmoments von dem Schaltring 23 auf das zweite Hohlrad 21 bzw. den Planetenträger 14 ausbildet. Die beispielhaften Klauen 26 haben einen halbzylindrischen Querschnitt, der Querschnitt kann ebenfalls prismatisch, rechteckig etc. sein. Ferner kann anstelle oder zusätzlich der Schaltring 23 mit Aussparungen versehen sein, in welche Klauen des zweiten Hohlrads 21 und Klauen des Planetenträgers 14 eingreifen. Bei einer weiteren, wenn auch weniger bevorzugte Ausgestaltung, ist der Schaltring 23 zwischen dem zweiten Hohlrad 21 und dem Planetenträger 14 angeordnet und greift entweder mit stirnförmigen Klauen 26 in das zweite Hohlrad 21 oder in den Planetenträger 14 ein, um eines der beiden Elemente am Drehen um die Getriebeachse 12 zu hindern.The exemplary switching ring 23 has claws 26 projecting radially inward. The second ring gear 21 has recesses 27 complementary to the claws 26 and the planetary carrier 14 has recesses 28 complementary to the claws 26 . Depending on its position, the switching ring 23 engages with the claws 26 either exclusively in the second ring gear 21 or in the planet carrier 14 . The shape of the claws 26 and associated recesses 27, 28 are designed in such a way that a sufficient form fit is formed for transmitting a torque from the switching ring 23 to the second ring gear 21 or the planet carrier 14 . The exemplary jaws 26 have one semi-cylindrical cross-section, the cross-section can also be prismatic, rectangular, etc. Furthermore, instead of or in addition, the switching ring 23 can be provided with cutouts, into which claws of the second ring gear 21 and claws of the planet carrier 14 engage. In a further, albeit less preferred embodiment, the switching ring 23 is arranged between the second ring gear 21 and the planet carrier 14 and engages either with end-shaped claws 26 in the second ring gear 21 or in the planet carrier 14 to keep one of the two elements rotating to prevent the transmission axis 12 .

Fig. 9 bis Fig. 12 zeigen eine Ausgestaltung eines Planetengetriebes 29. Das Planetengetriebe 29 hat auf einer Getriebeachse 12 angeordnet ein Sonnenrad 13, einen Planetenträger 14 mit mehreren Planetenrädern 15 und ein erstes Hohlrad 16. Der Planetenträger 14 hat vier Wellen 18 oder Lager, auf denen jeweils ein Planetenrad 15 um die Achse der Welle 18 drehbar gelagert ist. Die Planetenräder 15 haben jeweils zwei verschiedene Verzahnungen 19, 20. Die erste Verzahnung 19 hat einen größeren Durchmesser als die zweite Verzahnung 20. Die Anzahl der Zähne der ersten Verzahnung 19 und der zweiten Verzahnung 20 ist gleich. Die erste Verzahnung 19 kämmt mit dem Sonnenrad 13 und dem ersten Hohlrad 16. Ein zweites Hohlrad 21 ist koaxial auf der Getriebeachse 12 angeordnet. Das zweite Hohlrad 21 ist gegenüber dem ersten Hohlrad 16 frei drehbar. Das erste Hohlrad 16 und das zweite Hohlrad 21 sind benachbart längs der Getriebeachse 12 und in einem festen, unveränderlichen Abstand angeordnet. Das zweite Hohlrad 21 kämmt dauerhaft mit der zweiten Verzahnung 20 der Planetenräder 15. FIGS. 9 to 12 show an embodiment of a planetary gear 29. The planetary gear 29 has on a transmission axis 12 is arranged a sun gear 13, a planet carrier 14 having a plurality of planet gears 15 and a first ring gear 16. The planet carrier 14 has four shafts 18 and bearings, on each of which a planetary gear 15 to the axis of the shaft 18 is rotatably mounted. The planet gears 15 each have two different toothings 19, 20. The first toothing 19 has a larger diameter than the second toothing 20. The number of teeth of the first toothing 19 and the second toothing 20 is the same. The first toothing 19 meshes with the sun gear 13 and the first ring gear 16. A second ring gear 21 is arranged coaxially on the transmission axis 12. The second ring gear 21 is freely rotatable with respect to the first ring gear 16. The first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance. The second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15.

Das Planetengetriebe 29 weist einen Schaltring 30 auf, der längs der Getriebeachse 12 verschiebbar ist. Der Schaltring 23 ist durch in das Getriebegehäuse 22 eingreifende Nocken 31 am Drehen gehindert. Der Schaltring 30 ist mit dem Schieber 11 derart gekoppelt, dass der Schaltring 30 in eine erste Stellung gelangt, wenn der Schieber 11 in der ersten Schaltposition ist, und der in eine zweite Stellung gelangt, wenn der Schieber 11 in der zweiten Schaltposition ist. Der Schaltring 23 hat eine erste Stirnverzahnung 32, welche in der ersten Stellung in eine Stirnverzahnung 33 des zweiten Hohlrads 21 eingreift. Der Schaltring 23 hat eine zweite Stirnverzahnung 34, die in der zweiten Stellung in eine Stirnverzahnung 35 des Planetenträgers 14 eingreift. Der Schaltring 23 ist entsprechend zwischen dem zweiten Hohlrad 21 und dem Planetenträger 14 bzw. deren Stirnverzahnungen 33, 35 angeordnet. In der ersten Stellung hemmt der Schaltring 23 das zweite Hohlrad 21 am Drehen und gibt den Planetenträger 14 zum Drehen frei; in der zweiten Stellung hemmt der Schaltring 23 den Planetenträger 14 am Drehen und gibt das zweite Hohlrad 21 zum Drehen frei.The planetary gear 29 has a switching ring 30 which is displaceable along the gear axis 12. The switching ring 23 is prevented from rotating by cams 31 engaging in the gear housing 22. The switching ring 30 is coupled to the slide 11 in such a way that the switching ring 30 reaches a first position when the slide 11 is in the first switching position and that moves into a second position when the slide 11 is in the second switching position. The switching ring 23 has a first spur toothing 32 which, in the first position, engages in a spur toothing 33 of the second ring gear 21. The switching ring 23 has a second spur toothing 34 which, in the second position, engages in a spur toothing 35 of the planet carrier 14. The switching ring 23 is accordingly arranged between the second ring gear 21 and the planet carrier 14 or their spur teeth 33, 35 . In the first position, the switching ring 23 inhibits the second ring gear 21 from rotating and releases the planet carrier 14 to rotate; In the second position, the switching ring 23 prevents the planet carrier 14 from rotating and releases the second ring gear 21 to rotate.

Claims (4)

  1. Hand-held power tool (1) having
    a tool holder (2) for retaining a tool,
    an electric motor (4) for driving the tool holder (2),
    a shiftable planetary gear (10), which is mounted in a gear housing (22) between the tool holder (2) and the electric motor (4),
    wherein the planetary gear (10) has a sun gear (13), a planet carrier (14), a set of planet gears (15), which are mounted on the planet carrier (14), a first ring gear (16) and a second ring gear (21), wherein the planet gears (15) have a first toothing formation (19), which meshes with the first ring gear (16) and the sun gear (13) and a second toothing formation (20), which meshes with the second ring gear (21),
    a shifting ring (23), which can be displaced axially in the gear-mechanism housing (22) between a first setting and a second setting, wherein the shifting ring (23), in the first setting, engages in the second ring gear (21), wherein the shifting ring (23) is arranged in a rotationally fixed manner in the gear-mechanism housing (22),
    a manually actuable actuating element (11), which, in a first position, forces the shifting ring into the first setting and which, in a second position, forces the shifting ring into the second setting,
    wherein the first toothing formation (19) has a first diameter and the second toothing formation (20) has a second diameter, wherein the first diameter is greater than the second diameter, characterized in that the shifting ring (23), in the second setting, engages in the planet carrier (14), and
    the first toothing formation (19) and the second toothing formation (20) have the same number of teeth.
  2. Hand-held power tool according to Claim 1, characterized in that the shifting ring (23) is arranged between the second ring gear (21) and the planet carrier (14) and, in the first setting, engages in the second ring gear (21) and, in the second setting, engages in the planet carrier (14).
  3. Hand-held power tool according to Claim 2, characterized in that the shifting ring (23) has a first spur-toothing formation (32), which is directed towards the second ring gear (21), and a second spur-toothing formation (34), which is directed towards the planet carrier (14), wherein the second ring gear (21) has a spur-toothing formation (33) which is complementary to the first spur-toothing formation (32), and the planet carrier (14) has a spur-toothing formation (35) which is complementary to the second spur-toothing formation (34).
  4. Hand-held power tool according to one of the preceding claims, characterized in that an axial distance between the first ring gear (16) and the second ring gear (21) is unalterable.
EP16189706.1A 2015-09-22 2016-09-20 Handheld machine tool Active EP3147078B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15186196.0A EP3147077A1 (en) 2015-09-22 2015-09-22 Power driven hand tool

Publications (2)

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EP3147078A1 EP3147078A1 (en) 2017-03-29
EP3147078B1 true EP3147078B1 (en) 2021-02-24

Family

ID=54196834

Family Applications (2)

Application Number Title Priority Date Filing Date
EP15186196.0A Withdrawn EP3147077A1 (en) 2015-09-22 2015-09-22 Power driven hand tool
EP16189706.1A Active EP3147078B1 (en) 2015-09-22 2016-09-20 Handheld machine tool

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Application Number Title Priority Date Filing Date
EP15186196.0A Withdrawn EP3147077A1 (en) 2015-09-22 2015-09-22 Power driven hand tool

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017119807A1 (en) * 2017-08-29 2019-02-28 Festool Gmbh The handheld machine tool
DE102017119808A1 (en) * 2017-08-29 2019-02-28 Festool Gmbh The handheld machine tool
DE102018131747A1 (en) 2018-12-11 2020-06-18 Schaeffler Technologies AG & Co. KG Planetary gear with planetary stages that can be switched via planet gears
DE102019220245A1 (en) * 2019-12-19 2021-06-24 Robert Bosch Gmbh Hand machine tool with a planetary gear
CN113446364B (en) * 2021-03-25 2022-03-08 深圳市汇能达塑料有限公司 Planetary gear box structure for table type food processor

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

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Title
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Also Published As

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

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