EP2129494B1 - Hand machine tool - Google Patents

Hand machine tool Download PDF

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Publication number
EP2129494B1
EP2129494B1 EP08708625.2A EP08708625A EP2129494B1 EP 2129494 B1 EP2129494 B1 EP 2129494B1 EP 08708625 A EP08708625 A EP 08708625A EP 2129494 B1 EP2129494 B1 EP 2129494B1
Authority
EP
European Patent Office
Prior art keywords
hammer piston
piston
hammer
axial distance
power tool
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.)
Not-in-force
Application number
EP08708625.2A
Other languages
German (de)
French (fr)
Other versions
EP2129494A1 (en
Inventor
Andre Ullrich
Thomas Bernhardt
Tobias Herr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2129494A1 publication Critical patent/EP2129494A1/en
Application granted granted Critical
Publication of EP2129494B1 publication Critical patent/EP2129494B1/en
Not-in-force 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
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/065—Details regarding assembling of the tool

Definitions

  • the invention relates to a hand tool according to the preamble of claim 1.
  • Such a hand tool is from the GB 2 085 345 A known.
  • the handheld power tool includes a transmission device which has a running in the axial direction Wegensteinin.
  • the invention relates to a hand tool with a hammer mechanism, which has a run over a guide length racket and a hammer piston having a contact point and a active bottom with a bottom surface, and with a transmission device having a running in the axial direction Wegauer.
  • the contact point and the active bottom surface have an axial distance, which has at least the guide length of the racket.
  • a "contact point” is to be understood in particular a point which is provided for applying a drive bearing, in particular a wobble finger of the drive bearing, to the hammer piston and through which a pivot axis of a relative pivoting movement of the wobble finger with respect to the hammer piston.
  • a drive bearing in particular a wobble finger of the drive bearing
  • a "guide length” is intended to mean a length of a guide tube, such as a hammer tube or a pot piston, over which a guide surface extends to a guide of the racket.
  • the percussion can be particularly simple and inexpensive in different hand tool machines with different transmission devices that have different Druckwegenburgn integrated.
  • the hammer piston along the axial distance has a substantially constant diameter, whereby a particularly simple production of the hammer piston can be achieved.
  • a substantially identical diameter is to be understood in particular as meaning that the diameter can only change in an edge region along the axial distance.
  • the edge region is at most 20% of the axial distance and particularly advantageously at most 10% of the axial distance.
  • the hammer piston has a connecting web which extends at least partially along the axial distance, it is possible in this case to achieve a particularly lightweight hammer piston with an advantageous material saving during manufacture.
  • FIG. 1 a hand tool 10a formed by a hammer drill is shown.
  • the hand tool 10a comprises a housing 40a and in a front region a tool holder 42a for receiving a tool.
  • the handheld power tool 10a comprises a main handle 44a for actuating the handheld power tool 10a and for transmitting power from an operator to the handheld power tool 10a.
  • the hand tool 10a a drive unit 46a formed by an electric motor.
  • the torque of the drive unit 46a formed by a drive torque is transmitted via a transmission device 22a of the handheld power tool 10a to a pneumatic impact mechanism 12a and / or to a rotating output means formed by a hammer tube 48a ( FIG. 2 ).
  • the transmission device 22a has an intermediate shaft 50a, on the drive-side end of which a toothed wheel 52a is arranged, by means of which the drive torque of the drive unit 46a is transmitted to the intermediate shaft 50a during operation of the handheld power tool 10a. From the intermediate shaft 50a, the drive torque is transmitted to a drive bearing 56a and / or to a gear 72a of the transmission device 22a via a driving toothing 54a pressed onto the intermediate shaft 50a to generate a rotation of the hammer tube 48a or of a tool located in the tool receptacle 42a.
  • the hammer mechanism 12a comprises a hammer piston 14a, a beater 32a and an anvil 58a ( FIG. 2 ).
  • the hammer piston 14a formed by a pot piston 38a has an active bottom 18a with an active bottom surface 20a and a coupling point 60a for coupling a wobble finger 62a of the drive bearing 56a (FIG. Figures 2 and 3 ).
  • the coupling point 60a comprises a circular recess 64a.
  • an abutment point 16a is arranged, which lies on a pivot axis 66a of the wobble finger 62a, wherein the pivot axis 66a is arranged perpendicular to the plane of the drawing ( FIG. 3 ).
  • the active bottom 18a is arranged in a region of the hammer piston 14a facing the racket 32a and, during operation of the handheld power tool 10a, moves back and forth along an axial direction 24a to generate a striking pulse.
  • the active bottom surface 20a is the surface of the active bottom 18a facing the racket 32a.
  • a piston cylinder 68a of the hammer piston 14a is arranged, in which the racket 32a is guided.
  • the transmission device 22a has two different gear stages to a transmission of two different drive speeds or rotational speeds to the hammer tube 48a or on a rotatably connected to the hammer tube 48a gear unit 70a.
  • two toothed wheels 72a, 74a are mounted on the intermediate shaft 50a, the first toothed wheel 72a being rotatably connectable to the intermediate shaft 50a and, in addition, slidably mounted on the intermediate shaft 50a along the axial direction 24a.
  • the first gear 72a is displaced by a Heidelbergwegner 26a on the intermediate shaft 50a, wherein in a first switching position, the first gear 72a, the driving torque on the hammer tube 48a and the gear unit 70a and in a second switching position on the second gear 74a transmits. From the second gear 74a, the drive torque is further transmitted to the gear unit 70a.
  • the gear unit 70a comprises two transmission stages which correspond to a drive torque transmission with one of the two gear wheels 72a, 74a ( FIG. 2 ).
  • the shifting between the different gear stages within the transmission device 22a requires a longer alignment of the transmission unit 22a in the axial direction 24a by at least the shift path length 26a than a conventional one-gear transmission device 22a.
  • the longer orientation of the transmission device 22a is accommodated within the striking mechanism 12a by means of the hammer piston 14a.
  • An axial distance 28a between the active bottom surface 20a and the contact point 16a is greater than the Wegner 26a and equal to a guide length 30a of the racket 32a within the piston cylinder 68a.
  • the hammer piston 14a has a substantially equal diameter 36a.
  • FIGS. 4 to 6 is one each to the FIGS. 1 to 3 alternative hammer piston 14b, 14c, 14d of a percussion shown.
  • Essentially consistent components, features and functions are basically numbered with the same reference numerals. To distinguish the embodiments, however, the reference numerals of the embodiments, the letters a to d are added. The following description is essentially limited to the differences from the embodiment in the FIGS. 1 to 3 , wherein with respect to the same components, features and functions on the description of the embodiment in the FIGS. 1 to 3 can be referenced.
  • FIG. 4 is another hammer piston 14b shown with a piston cylinder 68b.
  • the hammer piston 14b has a coupling point 60b, which is formed by a web-shaped recess 64b.
  • the hammer piston 14b has a same diameter 36b.
  • a diameter 76b of the hammer piston 14b is smaller than the diameter 36b along the axial distance 28b.
  • the hammer piston 14b has a concave formation 78b on a radially outward surface 80b of the hammer piston 14b.
  • FIG. 5 is another hammer piston 14c shown with a piston cylinder 68c.
  • the hammer piston 14c has a coupling point 60c, which is formed by a web-shaped recess 64c.
  • the web-shaped recess 64c extends along an axial distance 28c between an active bottom surface 20c and an abutment point 16c substantially along an entire active bottom 18c of the hammer piston 14c.
  • the hammer piston 14c also has a same diameter 36c.
  • a diameter 76c of the hammer piston 14c is smaller than the diameter 36c along the axial distance 28c.
  • the hammer piston 14c has a concave formation 78c on a radially outward surface 80c of the hammer piston 14c.
  • FIG. 6 is another hammer piston 14d shown with a piston cylinder 68d.
  • the hammer piston 14d For coupling to a drive bearing 56d or a wobble finger 62d of the drive bearing 56d, the hammer piston 14d has a coupling point 60d, which is formed by a web-shaped recess 64d. Between an active bottom surface 20d and a contact point 16d of the hammer piston 14d, the hammer piston 14d has a connecting web 34d which has a smaller diameter 82d than a diameter 36d in the region of the active bottom surface 20d and a diameter 76d in the region of the coupling point 60d. In the region of the coupling point 60d, the hammer piston 14d has a concave formation 78d on a radially outwardly directed surface 80d of the hammer piston 14d.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Handwerkzeugmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a hand tool according to the preamble of claim 1.

Eine solche Handwerkzeugmaschine ist aus der GB 2 085 345 A bekannt.Such a hand tool is from the GB 2 085 345 A known.

Es ist bereits eine Handwerkzeugmaschine mit einem Schlagwerk, das einen über eine Führungslänge geführten Schläger und einen Hammerkolben aufweist, bekannt. Der Hammerkolben weist dabei einen Anlagepunkt und einen Wirkboden mit einer Wirkbodenfläche auf. Zudem umfasst die Handwerkzeugmaschine eine Getriebevorrichtung, die eine in axialer Richtung verlaufende Schaltweglänge aufweist.It is already a hand tool with a striking mechanism, which has a guided over a guide length racket and a hammer piston, known. The hammer piston has a contact point and a bottom of action with an active bottom surface. In addition, the handheld power tool includes a transmission device which has a running in the axial direction Schaltweglänge.

Vorteile der ErfindungAdvantages of the invention

Die Erfindung geht aus von einer Handwerkzeugmaschine mit einem Schlagwerk, das einen über eine Führungslänge geführten Schläger und einen Hammerkolben aufweist, der einen Anlagepunkt und einen Wirkboden mit einer Wirkbodenfläche aufweist, sowie mit einer Getriebevorrichtung, die eine in axialer Richtung verlaufende Schaltweglänge aufweist.The invention relates to a hand tool with a hammer mechanism, which has a run over a guide length racket and a hammer piston having a contact point and a active bottom with a bottom surface, and with a transmission device having a running in the axial direction Schaltweglänge.

Der Anlagepunkt und die Wirkbodenfläche weisen einen Axialabstand auf, der mindestens die Führungslänge des Schlägers aufweist. In diesem Zusammenhang soll unter einem "Anlagepunkt" insbesondere ein Punkt verstanden werden, der zu einem Anlegen eines Antriebslagers, insbesondere eines Taumelfingers des Antriebslagers, an den Hammerkolben vorgesehen ist und durch den eine Schwenkachse einer relativen Schwenkbewegung des Taumelfingers gegenüber dem Hammerkolben verläuft. Unter einem "Wirkboden" soll ein dem Schläger des Schlagwerks zugewandter Teilbereich des Hammerkolbens verstanden werden, der sich zu einer Erzeugung eines Schlagimpulses des Schlägers in einer translatorischen Richtung hin- und herbewegt. Dabei soll unter einer "Wirkbodenfläche" insbesondere die dem Schläger zugewandte Fläche des Wirkbodens verstanden werden. Unter einer "Führungslänge" soll eine Länge eines Führungsrohrs, wie beispielsweise eines Hammerrohrs oder eines Topfkolbens, verstanden werden, über der sich eine Führungsfläche zu einer Führung des Schlägers erstreckt. Bei einer erfindungsgemäßen Ausgestaltung kann das Schlagwerk besonders einfach und kostengünstig in unterschiedliche Handwerkzeugmaschinen mit unterschiedlichen Getriebevorrichtungen, die unterschiedliche Schaltweglängen aufweisen, integriert werden.The contact point and the active bottom surface have an axial distance, which has at least the guide length of the racket. In this context, a "contact point" is to be understood in particular a point which is provided for applying a drive bearing, in particular a wobble finger of the drive bearing, to the hammer piston and through which a pivot axis of a relative pivoting movement of the wobble finger with respect to the hammer piston. Under a "Wirkboden" should a the racket the percussion facing portion of the hammer piston are understood, which reciprocates to produce a shock pulse of the racket in a translational direction. It should be understood by a "effective bottom surface" in particular the racket facing surface of the active floor. A "guide length" is intended to mean a length of a guide tube, such as a hammer tube or a pot piston, over which a guide surface extends to a guide of the racket. In one embodiment of the invention, the percussion can be particularly simple and inexpensive in different hand tool machines with different transmission devices that have different Schaltweglängen integrated.

Es wird vorgeschlagen, dass der Hammerkolben entlang des Axialabstands einen im Wesentlichen gleich bleibenden Durchmesser aufweist, wodurch eine besonders einfache Herstellung des Hammerkolbens erreicht werden kann. Unter einem "im Wesentlichen gleichen Durchmesser" soll hierbei insbesondere verstanden werden, dass sich der Durchmesser lediglich in einem Randbereich entlang des Axialabstands ändern kann. Vorzugsweise beträgt der Randbereich maximal 20 % des Axialabstands und besonders vorteilhaft maximal 10 % des Axialabstands.It is proposed that the hammer piston along the axial distance has a substantially constant diameter, whereby a particularly simple production of the hammer piston can be achieved. In this case, a "substantially identical diameter" is to be understood in particular as meaning that the diameter can only change in an edge region along the axial distance. Preferably, the edge region is at most 20% of the axial distance and particularly advantageously at most 10% of the axial distance.

Weist der Hammerkolben einen Verbindungssteg auf, der sich zumindest teilweise entlang des Axialabstands erstreckt, kann dabei ein insbesondere leichter Hammerkolben mit einer vorteilhaften Materialeinsparung bei der Herstellung erzielt werden. Vorzugsweise verbindet der Verbindungssteg den Wirkboden mit einer den Anlagepunkt umfassenden Koppelstelle des Hammerkolbens.If the hammer piston has a connecting web which extends at least partially along the axial distance, it is possible in this case to achieve a particularly lightweight hammer piston with an advantageous material saving during manufacture. Preferably connects the connecting web the active soil with a coupling point comprising the attachment point of the hammer piston.

Weitere Bauteile, wie insbesondere ein separates Führungsrohr des Schlägers, Bauraum, Montageaufwand und Kosten können vorteilhaft eingespart werden, wenn der Hammerkolben von einem Topfkolben gebildet ist.Other components, such as in particular a separate guide tube of the racket, space, installation costs and costs can be advantageously saved when the hammer piston is formed by a pot piston.

Zeichnungdrawing

Weitere Vorteile ergeben sich aus der folgenden Zeichnungsbeschreibung. In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestellt. Die Zeichnung, die Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination.Further advantages emerge from the following description of the drawing. In the drawings, embodiments of the invention are shown. The drawing, the description and the claims contain numerous features in combination.

Es zeigen:

Fig. 1
eine erfindungsgemäße Handwerkzeugmaschine in einer Seitenansicht,
Fig. 2
einen Teilbereich einer Handwerkzeugmaschine mit einem erfindungsgemäßen Schlagwerk in einer schematischen Schnittdarstellung,
Fig. 3
einen Hammerkolben in einer Seitenansicht,
Fig. 4
einen alternativen Hammerkolben in einer Seitenansicht,
Fig. 5
einen weiteren Hammerkolben in einer Seitenansicht und
Fig. 6
einen weiteren Hammerkolben in einer Seitenansicht.
Show it:
Fig. 1
a hand tool according to the invention in a side view,
Fig. 2
a partial area of a hand tool with a striking mechanism according to the invention in a schematic sectional representation,
Fig. 3
a hammer piston in a side view,
Fig. 4
an alternative hammer piston in a side view,
Fig. 5
another hammer piston in a side view and
Fig. 6
another hammer piston in a side view.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine von einem Bohrhammer gebildete Handwerkzeugmaschine 10a dargestellt. Die Handwerkzeugmaschine 10a umfasst ein Gehäuse 40a und in einem Frontbereich eine Werkzeugaufnahme 42a zu einer Aufnahme eines Werkzeugs. An einer dem Frontbereich abgewandten Seite umfasst die Handwerkzeugmaschine 10a einen Haupthandgriff 44a zu einem Betätigen der Handwerkzeugmaschine 10a und zu einer Kraftübertragung von einem Bediener auf die Handwerkzeugmaschine 10a. Zu einer Erzeugung eines Drehmoments weist die Handwerkzeugmaschine 10a eine von einem Elektromotor gebildete Antriebseinheit 46a auf. Das von einem Antriebsmoment gebildete Drehmoment der Antriebseinheit 46a wird über eine Getriebevorrichtung 22a der Handwerkzeugmaschine 10a auf ein pneumatisches Schlagwerk 12a und/oder auf ein rotierendes, von einem Hammerrohr 48a gebildetes Abtriebsmittel übertragen (Figur 2).In FIG. 1 a hand tool 10a formed by a hammer drill is shown. The hand tool 10a comprises a housing 40a and in a front region a tool holder 42a for receiving a tool. On a side facing away from the front region, the handheld power tool 10a comprises a main handle 44a for actuating the handheld power tool 10a and for transmitting power from an operator to the handheld power tool 10a. To generate a torque, the hand tool 10a a drive unit 46a formed by an electric motor. The torque of the drive unit 46a formed by a drive torque is transmitted via a transmission device 22a of the handheld power tool 10a to a pneumatic impact mechanism 12a and / or to a rotating output means formed by a hammer tube 48a ( FIG. 2 ).

Die Getriebevorrichtung 22a weist eine Zwischenwelle 50a auf, an deren antriebsseitigem Ende ein Zahnrad 52a angeordnet ist, mittels dessen das Antriebsmoment der Antriebseinheit 46a im Betrieb der Handwerkzeugmaschine 10a auf die Zwischenwelle 50a übertragen wird. Von der Zwischenwelle 50a wird das Antriebsmoment über eine auf der Zwischenwelle 50a aufgepresste Mitnahmeverzahnung 54a auf ein Antriebslager 56a und/oder auf ein Zahnrad 72a der Getriebevorrichtung 22a zu einer Erzeugung einer Rotation des Hammerrohrs 48a bzw. eines in der Werkzeugaufnahme 42a befindlichen Werkzeugs übertragen.The transmission device 22a has an intermediate shaft 50a, on the drive-side end of which a toothed wheel 52a is arranged, by means of which the drive torque of the drive unit 46a is transmitted to the intermediate shaft 50a during operation of the handheld power tool 10a. From the intermediate shaft 50a, the drive torque is transmitted to a drive bearing 56a and / or to a gear 72a of the transmission device 22a via a driving toothing 54a pressed onto the intermediate shaft 50a to generate a rotation of the hammer tube 48a or of a tool located in the tool receptacle 42a.

Das Schlagwerk 12a umfasst einen Hammerkolben 14a, einen Schläger 32a und einen Döpper 58a (Figur 2). Der von einem Topfkolben 38a gebildete Hammerkolben 14a weist einen Wirkboden 18a mit einer Wirkbodenfläche 20a und eine Koppelstelle 60a zu einem Ankoppeln eines Taumelfingers 62a des Antriebslagers 56a auf (Figuren 2 und 3). Die Koppelstelle 60a umfasst eine kreisförmige Ausnehmung 64a. Innerhalb der Koppelstelle 60a ist ein Anlagepunkt 16a angeordnet, der auf einer Schwenkachse 66a des Taumelfingers 62a liegt, wobei die Schwenkachse 66a senkrecht zur Zeichenebene angeordnet ist (Figur 3). Der Wirkboden 18a ist in einem dem Schläger 32a zugewandten Bereich des Hammerkolbens 14a angeordnet und bewegt sich im Betrieb der Handwerkzeugmaschine 10a zur Erzeugung eines Schlagimpulses entlang einer axialen Richtung 24a hin und her. Die Wirkbodenfläche 20a ist die dem Schläger 32a zugewandte Fläche des Wirkbodens 18a. Innerhalb des Hammerrohrs 48a ist ein Kolbenzylinder 68a des Hammerkolbens 14a angeordnet, in dem der Schläger 32a geführt wird.The hammer mechanism 12a comprises a hammer piston 14a, a beater 32a and an anvil 58a ( FIG. 2 ). The hammer piston 14a formed by a pot piston 38a has an active bottom 18a with an active bottom surface 20a and a coupling point 60a for coupling a wobble finger 62a of the drive bearing 56a (FIG. Figures 2 and 3 ). The coupling point 60a comprises a circular recess 64a. Within the coupling point 60a an abutment point 16a is arranged, which lies on a pivot axis 66a of the wobble finger 62a, wherein the pivot axis 66a is arranged perpendicular to the plane of the drawing ( FIG. 3 ). The active bottom 18a is arranged in a region of the hammer piston 14a facing the racket 32a and, during operation of the handheld power tool 10a, moves back and forth along an axial direction 24a to generate a striking pulse. The active bottom surface 20a is the surface of the active bottom 18a facing the racket 32a. Within the hammer tube 48a, a piston cylinder 68a of the hammer piston 14a is arranged, in which the racket 32a is guided.

Die Getriebevorrichtung 22a weist zwei unterschiedliche Getriebestufen auf zu einer Übertragung von zwei unterschiedlichen Antriebsgeschwindigkeiten bzw. Rotationsgeschwindigkeiten auf das Hammerrohr 48a bzw. auf eine drehfest mit dem Hammerrohr 48a verbundene Zahnradeinheit 70a. Hierzu sind auf der Zwischenwelle 50a zwei Zahnräder 72a, 74a gelagert, wobei das erste Zahnrad 72a mit der Zwischenwelle 50a drehfest verbindbar und zudem entlang der axialen Richtung 24a auf der Zwischenwelle 50a verschiebbar gelagert ist. Zu einem Schalten zwischen den unterschiedlichen Antriebsgeschwindigkeiten wird das erste Zahnrad 72a um eine Schaltweglänge 26a auf der Zwischenwelle 50a verschoben, wobei in einer ersten Schaltposition das erste Zahnrad 72a das Antriebsmoment auf das Hammerrohr 48a bzw. auf die Zahnradeinheit 70a und in einer zweiten Schaltposition auf das zweite Zahnrad 74a überträgt. Von dem zweiten Zahnrad 74a wird das Antriebsmoment weiter auf die Zahnradeinheit 70a übertragen. Hierzu umfasst die Zahnradeinheit 70a zwei Übertragungsstufen, die mit jeweils einem der beiden Zahnräder 72a, 74a zu einer Antriebsmomentübertragung korrespondieren (Figur 2).The transmission device 22a has two different gear stages to a transmission of two different drive speeds or rotational speeds to the hammer tube 48a or on a rotatably connected to the hammer tube 48a gear unit 70a. For this purpose, two toothed wheels 72a, 74a are mounted on the intermediate shaft 50a, the first toothed wheel 72a being rotatably connectable to the intermediate shaft 50a and, in addition, slidably mounted on the intermediate shaft 50a along the axial direction 24a. For switching between the different driving speeds, the first gear 72a is displaced by a Schaltweglänge 26a on the intermediate shaft 50a, wherein in a first switching position, the first gear 72a, the driving torque on the hammer tube 48a and the gear unit 70a and in a second switching position on the second gear 74a transmits. From the second gear 74a, the drive torque is further transmitted to the gear unit 70a. For this purpose, the gear unit 70a comprises two transmission stages which correspond to a drive torque transmission with one of the two gear wheels 72a, 74a ( FIG. 2 ).

Das Schalten zwischen den unterschiedlichen Getriebestufen innerhalb der Getriebevorrichtung 22a erfordert eine um mindestens die Schaltweglänge 26a längere Ausrichtung der Getriebeeinheit 22a in der axialen Richtung 24a als eine herkömmliche Getriebevorrichtung 22a mit nur einer Getriebestufe. Der längeren Ausrichtung der Getriebevorrichtung 22a wird innerhalb des Schlagwerks 12a mittels des Hammerkolbens 14a Rechnung getragen. Ein Axialabstand 28a zwischen der Wirkbodenfläche 20a und dem Anlagepunkt 16a ist dabei größer als die Schaltweglänge 26a und gleich groß wie eine Führungslänge 30a des Schlägers 32a innerhalb des Kolbenzylinders 68a. Entlang der Führungslänge 30a wird der Schläger 32a innerhalb des Kolbenzylinders 68a geführt, wobei sich die Führungslänge 30a zusammensetzt aus einer Summe einer Dicke 84a des Schlägers 32a und einer Differenz einer der Wirkbodenfläche 20a zugewandten Endposition 86a und einer der Wirkbodenfläche 20a abgewandten Endposition 88a (Figuren 2 und 3). Entlang des Axialabstands 28a weist der Hammerkolben 14a einen im Wesentlichen gleichen Durchmesser 36a auf.The shifting between the different gear stages within the transmission device 22a requires a longer alignment of the transmission unit 22a in the axial direction 24a by at least the shift path length 26a than a conventional one-gear transmission device 22a. The longer orientation of the transmission device 22a is accommodated within the striking mechanism 12a by means of the hammer piston 14a. An axial distance 28a between the active bottom surface 20a and the contact point 16a is greater than the Schaltweglänge 26a and equal to a guide length 30a of the racket 32a within the piston cylinder 68a. Along the guide length 30a of the racket 32a is guided within the piston cylinder 68a, wherein the guide length 30a composed of a sum of a thickness 84a of the racket 32a and a difference of the active bottom surface 20a facing the end position 86a and the active bottom surface 20a opposite end position 88a ( Figures 2 and 3 ). Along the axial distance 28a, the hammer piston 14a has a substantially equal diameter 36a.

In den Figuren 4 bis 6 ist jeweils ein zu den Figuren 1 bis 3 alternativer Hammerkolben 14b, 14c, 14d eines Schlagwerks dargestellt. Im Wesentlichen gleich bleibende Bauteile, Merkmale und Funktionen sind grundsätzlich mit den gleichen Bezugszeichen beziffert. Zur Unterscheidung der Ausführungsbeispiele sind jedoch den Bezugszeichen der Ausführungsbeispiele die Buchstaben a bis d hinzugefügt. Die nachfolgende Beschreibung beschränkt sich im Wesentlichen auf die Unterschiede zu dem Ausführungsbeispiel in den Figuren 1 bis 3, wobei bezüglich gleich bleibender Bauteile, Merkmale und Funktionen auf die Beschreibung des Ausführungsbeispiels in den Figuren 1 bis 3 verwiesen werden kann.In the FIGS. 4 to 6 is one each to the FIGS. 1 to 3 alternative hammer piston 14b, 14c, 14d of a percussion shown. Essentially consistent components, features and functions are basically numbered with the same reference numerals. To distinguish the embodiments, however, the reference numerals of the embodiments, the letters a to d are added. The following description is essentially limited to the differences from the embodiment in the FIGS. 1 to 3 , wherein with respect to the same components, features and functions on the description of the embodiment in the FIGS. 1 to 3 can be referenced.

In Figur 4 ist ein weiterer Hammerkolben 14b mit einem Kolbenzylinder 68b dargestellt. Zu einer Kopplung an ein Antriebslager 56b bzw. einen Taumelfinger 62b des Antriebslagers 56b weist der Hammerkolben 14b eine Koppelstelle 60b auf, die von einer stegförmigen Ausnehmung 64b gebildet ist. Entlang eines Axialabstands 28b zwischen einer Wirkbodenfläche 20b eines Wirkbodens 18b und einem Anlagepunkt 16b weist der Hammerkolben 14b einen gleichen Durchmesser 36b auf. Im Bereich der Koppelstelle 60b ist ein Durchmesser 76b des Hammerkolbens 14b kleiner als der Durchmesser 36b entlang des Axialabstands 28b. In diesem Bereich weist der Hammerkolben 14b eine konkave Ausformung 78b an einer radial nach außen gerichteten Oberfläche 80b des Hammerkolbens 14b auf.In FIG. 4 is another hammer piston 14b shown with a piston cylinder 68b. For a coupling to a drive bearing 56b or a wobble finger 62b of the drive bearing 56b, the hammer piston 14b has a coupling point 60b, which is formed by a web-shaped recess 64b. Along an axial distance 28b between an active bottom surface 20b of an active bottom 18b and an abutment point 16b, the hammer piston 14b has a same diameter 36b. In the region of the coupling point 60b, a diameter 76b of the hammer piston 14b is smaller than the diameter 36b along the axial distance 28b. In this area, the hammer piston 14b has a concave formation 78b on a radially outward surface 80b of the hammer piston 14b.

In Figur 5 ist ein weiterer Hammerkolben 14c mit einem Kolbenzylinder 68c dargestellt. Zu einer Kopplung an ein Antriebslager 56c bzw. einen Taumelfinger 62c des Antriebslagers 56c weist der Hammerkolben 14c eine Koppelstelle 60c auf, die von einer stegförmigen Ausnehmung 64c gebildet ist. Die stegförmige Ausnehmung 64c erstreckt sich entlang eines Axialabstands 28c zwischen einer Wirkbodenfläche 20c und einem Anlagepunkt 16c im Wesentlichen entlang eines gesamten Wirkbodens 18c des Hammerkolbens 14c. Entlang des Axialabstands 28c weist der Hammerkolben 14c zudem einen gleichen Durchmesser 36c auf. Im Bereich der Koppelstelle 60c ist ein Durchmesser 76c des Hammerkolbens 14c kleiner als der Durchmesser 36c entlang des Axialabstands 28c. In diesem Bereich weist der Hammerkolben 14c eine konkave Ausformung 78c an einer radial nach außen gerichteten Oberfläche 80c des Hammerkolbens 14c auf.In FIG. 5 is another hammer piston 14c shown with a piston cylinder 68c. For a coupling to a drive bearing 56c or a wobble finger 62c of the drive bearing 56c, the hammer piston 14c has a coupling point 60c, which is formed by a web-shaped recess 64c. The web-shaped recess 64c extends along an axial distance 28c between an active bottom surface 20c and an abutment point 16c substantially along an entire active bottom 18c of the hammer piston 14c. Along the axial distance 28c, the hammer piston 14c also has a same diameter 36c. In the region of the coupling point 60c, a diameter 76c of the hammer piston 14c is smaller than the diameter 36c along the axial distance 28c. In this area, the hammer piston 14c has a concave formation 78c on a radially outward surface 80c of the hammer piston 14c.

In Figur 6 ist ein weiterer Hammerkolben 14d mit einem Kolbenzylinder 68d dargestellt. Zu einer Kopplung an ein Antriebslager 56d bzw. einen Taumelfinger 62d des Antriebslagers 56d weist der Hammerkolben 14d eine Koppelstelle 60d auf, die von einer stegförmigen Ausnehmung 64d gebildet ist. Zwischen einer Wirkbodenfläche 20d und einem Anlagepunkt 16d des Hammerkolbens 14d weist der Hammerkolben 14d einen Verbindungssteg 34d auf, der einen kleineren Durchmesser 82d aufweist als ein Durchmesser 36d im Bereich der Wirkbodenfläche 20d und ein Durchmesser 76d im Bereich der Koppelstelle 60d. Im Bereich der Koppelstelle 60d weist der Hammerkolben 14d eine konkave Ausformung 78d an einer radial nach außen gerichteten Oberfläche 80d des Hammerkolbens 14d auf.In FIG. 6 is another hammer piston 14d shown with a piston cylinder 68d. For coupling to a drive bearing 56d or a wobble finger 62d of the drive bearing 56d, the hammer piston 14d has a coupling point 60d, which is formed by a web-shaped recess 64d. Between an active bottom surface 20d and a contact point 16d of the hammer piston 14d, the hammer piston 14d has a connecting web 34d which has a smaller diameter 82d than a diameter 36d in the region of the active bottom surface 20d and a diameter 76d in the region of the coupling point 60d. In the region of the coupling point 60d, the hammer piston 14d has a concave formation 78d on a radially outwardly directed surface 80d of the hammer piston 14d.

Claims (4)

  1. Portable power tool having a percussion mechanism (12a) which has a striker (32a) that is guided along a guide length (30a) and a hammer piston (14a; 14b; 14c; 14d) that has a bearing point (16a; 16b; 16c; 16d) and an active end (18a; 18b; 18c; 18d) with an active-end face (20a; 20b; 20c; 20d), and having a transmission device (22a) which has a switching travel length (26a) extending in the axial direction (24a), characterized in that the bearing point (16a; 16b; 16c; 16d) and the active-end face (20a; 20b; 20c; 20d) are at an axial distance (28a; 28b; 28c; 28d) which has at least the guide length (30a) of the striker (32a).
  2. Portable power tool according to one of the preceding claims, characterized in that the hammer piston (14a; 14b; 14c) has a substantially constant diameter (36a; 36b; 36c) along the axial distance (28a; 28b; 28c).
  3. Portable power tool according to one of the preceding claims, characterized in that the hammer piston (14d) has a connecting bar (34d) which extends at least partially along the axial distance (28d).
  4. Portable power tool according to one of the preceding claims, characterized in that the hammer piston (14a; 14b; 14c; 14d) is formed by a pot-type piston (38a).
EP08708625.2A 2007-03-02 2008-02-04 Hand machine tool Not-in-force EP2129494B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710010181 DE102007010181A1 (en) 2007-03-02 2007-03-02 Hand tool comprises a striking unit with a hammer piston having a contact point and an active base surface forming an axial distance
PCT/EP2008/051321 WO2008107251A1 (en) 2007-03-02 2008-02-04 Hand machine tool

Publications (2)

Publication Number Publication Date
EP2129494A1 EP2129494A1 (en) 2009-12-09
EP2129494B1 true EP2129494B1 (en) 2016-04-13

Family

ID=39362853

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08708625.2A Not-in-force EP2129494B1 (en) 2007-03-02 2008-02-04 Hand machine tool

Country Status (4)

Country Link
EP (1) EP2129494B1 (en)
CN (1) CN101622103B (en)
DE (1) DE102007010181A1 (en)
WO (1) WO2008107251A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008041889A1 (en) * 2008-09-09 2010-03-11 Robert Bosch Gmbh Machine tool and manufacturing method for a machine tool
CN117444906A (en) * 2017-09-30 2024-01-26 苏州宝时得电动工具有限公司 Electric hammer

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3039631A1 (en) * 1980-10-21 1982-05-27 Robert Bosch Gmbh, 7000 Stuttgart DRILLING HAMMER
EP0303651B2 (en) * 1987-03-05 1999-12-01 Robert Bosch Gmbh Process for interrupting the operation of a hand tool, in particular percussion and/or rotation thereof
DE19540391A1 (en) * 1995-10-30 1997-05-07 Hilti Ag Drilling and chiseling device
GB2394437A (en) * 2002-10-23 2004-04-28 Black & Decker Inc Hammer including a piston with wear-reducing washers
CN2685020Y (en) * 2004-03-05 2005-03-16 王晓冬 Electric hammer

Also Published As

Publication number Publication date
EP2129494A1 (en) 2009-12-09
WO2008107251A1 (en) 2008-09-12
CN101622103B (en) 2012-07-18
DE102007010181A1 (en) 2008-09-04
CN101622103A (en) 2010-01-06

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