EP2347865B1 - Electrical tool - Google Patents

Electrical tool Download PDF

Info

Publication number
EP2347865B1
EP2347865B1 EP10196699.2A EP10196699A EP2347865B1 EP 2347865 B1 EP2347865 B1 EP 2347865B1 EP 10196699 A EP10196699 A EP 10196699A EP 2347865 B1 EP2347865 B1 EP 2347865B1
Authority
EP
European Patent Office
Prior art keywords
coupling
stroke
drive wheel
ring
toothed drive
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
EP10196699.2A
Other languages
German (de)
French (fr)
Other versions
EP2347865A1 (en
Inventor
Armin Eisenhardt
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.)
Techtronic Industries GmbH
Original Assignee
AEG Electric Tools GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by AEG Electric Tools GmbH filed Critical AEG Electric Tools GmbH
Publication of EP2347865A1 publication Critical patent/EP2347865A1/en
Application granted granted Critical
Publication of EP2347865B1 publication Critical patent/EP2347865B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0038—Tools having a rotation-only mode
    • 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
    • B25D2250/165—Overload clutches, torque limiters
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the present invention relates to a power tool according to the preamble of patent claim 1, in particular a manually operated power tool, preferably a hammer drill.
  • a power tool such as a hammer drill
  • a power tool includes a drive motor, a tool spindle for rotationally driving a tool, a rotary drive gear for coupling the drive motor to the tool spindle, a hammer mechanism for hammering the tool, a hammer mechanism for coupling the drive motor to the hammer mechanism, and a switching device for activating and deactivating the striking mechanism.
  • the present invention is concerned with the problem of providing for such a power tool an improved or at least another embodiment, which is characterized in particular by a compact design.
  • This problem is solved according to the invention by the subject matter of the independent claim.
  • Advantageous embodiments are the subject of the dependent claims.
  • the invention is based on the general idea to equip the switching device with a clutch which is integrated into the force path of the percussion gear and which has an actuating stroke for engagement and disengagement, ie for activating and deactivating the impact mechanism.
  • the switching device is designed such that a stroke direction of this actuating stroke extends transversely to the axis of rotation of the tool spindle or parallel to a rotational axis of a manually rotatable actuatable element of the switching device extends.
  • the actuating stroke can extend both transversely to the axis of rotation of the tool spindle and parallel to the axis of rotation of the actuating element.
  • the actuating stroke of the clutch corresponds to a linear adjustment movement of a corresponding coupling member, which causes the engagement or disengagement of the clutch.
  • the orientation of the actuating stroke transverse to the axis of rotation of the tool spindle or parallel to the axis of rotation of the actuating element and the integration of the coupling in the percussion gear allows a spatially close arrangement of the switching device on the tool spindle, which can be a total of a compact design for the power tool realize.
  • the coupling can be integrated into the force path of the percussion gear mechanism in a particularly simple manner, in that the percussion gear mechanism has an input-side drive gear which is rotatably mounted about an axis of rotation, and the percussion gear mechanism has an output-side crank drive wheel, which is rotatably mounted about the axis of rotation of the drive gear wheel and activated Schlagtechnik drives a connecting rod of the striking mechanism.
  • the clutch comprises in the hammer mechanism a coupling ring which is arranged coaxially to the axis of rotation of the drive gear on the crank gear and is arranged axially adjustable and rotationally fixed on the crank drive.
  • this coupling ring interacts with the drive gear, such that the coupling ring transmits torque from the drive gear to the crank gear in the engaged state, while in the disengaged state no torque transmission from the drive gear via the coupling ring to the crank drive.
  • the design presented here leads to a particularly compact integration of the clutch in the percussion gearbox.
  • the drive gear on a side facing the crank gear on a Mit supportivekontur while the coupling ring on a drive gear facing axial side complementary to Mit supportivekontur the drive gear Mit leisurekontur which cooperates in the engaged state of the coupling ring for torque transmission with the Mit demandingkontur the drive gear and in disengaged state axially free of it.
  • the axial Mit resumekonturen can transmit large torques and require little installation space.
  • the switching device has an actuating device for engagement and disengagement of the coupling, which couples a manually operable actuating element with an adjustable coupling member of the clutch.
  • the coupling member is expediently the coupling ring.
  • the actuating element which is preferably arranged on the outside of a housing of the power tool, makes it possible to engage in the percussion gear mechanism or in the clutch in order to engage or disengage it.
  • the actuating device may be equipped with a lifting element which is coupled via at least one parallel to the axis of rotation of the drive gear arm portion with the coupling ring, so that a direction away from the drive gear stroke adjustment of the lifting element parallel to the axis of rotation of the drive gear entrains the clutch ring and disengages.
  • the actuating device engages with the respective arm portion of the lifting element, the crank drive wheel to come into engagement with the coupling ring. This allows a particularly space-saving arrangement of the actuator coaxial with the axis of rotation of the drive gear.
  • to realize a rotationally fixed and axially adjustable coupling between the coupling ring and the crank drive be provided to equip the crank drive in an axial section with an outer driver contour and to provide the coupling ring with a complementary inner driver contour, so that the Coupling ring on these Mitêturgituren rotationally fixed and axially adjustable is arranged on the crank drive wheel.
  • Particularly expedient is a development in which the driver contours are designed as polygonal profiles. These allow a particularly high torque transmission with low wear.
  • the proposed construction allows a particularly compact design with high reliability.
  • Corresponding Fig. 1 includes a power tool 1, which is manually operable and is configured in the example as a hammer drill, a housing 41, the z. B. has an L-shape, since a spindle portion 59 of the housing 41 and a motor portion 60 of the housing 41 are arranged offset by approximately 90 ° to each other.
  • a tool spindle 3 extends, which carries a tool holder 61 at its end protruding from the housing 41.
  • a drive motor 2 is housed.
  • the longitudinal direction of the spindle section 59 is defined by the axis of rotation 8 of the tool spindle 3 and extends parallel thereto.
  • the longitudinal axis of the motor portion 60 is defined by the axis of rotation 18 of a drive shaft of the drive motor 2 and extends parallel thereto.
  • the housing 41 has a handle portion 62, which in the example at two spaced ends on the one hand on the spindle portion 59 and on the other hand attached to the motor section 60.
  • a handle portion 62 of the hammer drill 1 and the power tool 1 may be connected by a cable 63 to an external power supply.
  • the hammer drill 1 can also be equipped with a rechargeable battery, so that it can be operated independently of a power grid.
  • Fig. 1 shows the hammer drill 1 in an upright or vertical typical working position, in which the spindle portion 59 is oriented horizontally, while the motor portion 60 is oriented vertically.
  • an upper side 64 and a lower side 65 are defined on the hammer drill 1 or on its housing 41.
  • An actuating element 28 of a switching device 7 is arranged on the upper side 64 in a region of the housing 41 marked II. Said area II is located vertically above the motor portion 60, in particular in the region of a connection point 66 between handle portion 62 and spindle portion 59.
  • the switching device 7 is used to activate and deactivate a hammer mill or hammer operation of the hammer drill 1.
  • the switching device 7 has the actuator 28 which is manually operable to turn on or off the hammer mill.
  • the actuating element 28 is arranged rotatably about a rotation axis 37.
  • the axis of rotation 37 extends in the example parallel to the axis of rotation 18 of the drive motor. 2
  • such a manually operable hammer drill 1 comprises a drive motor 2, a tool spindle 3, a rotary drive gear 4, a striking mechanism 5, a percussion gear 6 and a switching device 7.
  • the tool spindle 3 rotates in operation about a rotation axis 8 and serves for the rotational driving of a not shown here Tool, in particular a percussion drill.
  • the rotary drive gear 4 couples the drive motor. 2 with the tool spindle 3.
  • the striking mechanism 5 is used for hammering driving the tool.
  • the Schlagtechnik 2 works pneumatically.
  • the percussion gear 6 couples the drive motor 2 with the striking mechanism 5.
  • the switching device 7 the striking mechanism 5 can be activated and deactivated. When the impact mechanism 5 is deactivated, the hammer drill 1 can be used as a pure drilling machine, so that the respective tool is then driven only in a rotating and non-hammering manner.
  • the switching device 7 is equipped with a coupling 9, which is integrated in a - indicated by a broken line - power path 10 of the percussion gear 6.
  • the coupling 9 has an actuating stroke 11, indicated by a double arrow, which extends transversely to the axis of rotation 8 of the tool spindle 3.
  • the actuating stroke 11 is characterized by the direction of movement of a coupling member 12, in which the coupling member 12 for engagement and disengagement of the clutch 9 is adjustable.
  • coupling member 12 When coupling member 12 is in the embodiments presented here is a coupling ring, which is also referred to below with 12.
  • This coupling ring 12 is arranged in the percussion gear 6.
  • the drive gear 13 meshes with a drive pinion 15 of a drive shaft 16 of the drive motor 2.
  • the drive gear 13 is rotatably mounted about an axis of rotation 17 in the power path 10, the coupling ring 12 between an input side drive gear 13 of the percussion gear 6 and the output side crank drive , which in the example extends axially parallel to a rotation axis 18 of the drive shaft 16 of the drive motor 2.
  • the drive gear 13 is rotatably mounted on a stationary shaft 19.
  • the crank gear 14 is also rotatably supported about the rotation axis 17 of the drive gear 13.
  • crank gear 14 is also rotatably mounted on the stationary shaft 19.
  • activated Schlagwerk 5 drives the Crankshaft 14, a connecting rod 20 of the percussion mechanism 5, which, for example, a piston 21 oscillatingly drives, which is mounted in a stroke-adjustable manner in the hollow tool spindle 3.
  • the coupling ring 12 is arranged coaxially to the axis of rotation 17 of the drive gear 13 on the crank gear 14, in such a way that it is axially adjustable on the crank gear 14 and at the same time is rotatably coupled thereto. Achieves this axial adjustability while rotating non-locking according to the embodiment of Fig. 2 to 5 for example by an axial toothing.
  • the crank drive wheel 14 has an axial section 22 which extends coaxially to the axis of rotation 17 of the drive gear 13.
  • This axial section 22 has radially outwardly an axially extending driver contour 23 which cooperates with a complementary driver contour 56 of the coupling ring 12.
  • the two co-operating Mitauerkonturen 23, 56 allow a rotationally fixed and axially adjustable arrangement of the coupling ring 12 on the cylindrical portion 22 of the crank drive gear 14.
  • Fig. 7 an embodiment in which the crank drive wheel 14 has an external polygonal profile 57, while the coupling ring 12 has an internal polygonal profile 58, which is formed complementary to the outer polygonal profile 57.
  • the cooperating polygonal profiles 57, 58 realize a rotationally fixed and axially displaceable coupling between coupling ring 12 and crank drive wheel 14.
  • the outer driver contour 23 of the crank drive wheel 14 is designed as an external polygonal profile, while the inner driver contour 56 of the coupling ring 12 is designed as a complementary, internal polygonal profile 58.
  • the drive gear 13 has a driver contour 24 on an axial side facing the crank drive wheel 14.
  • the coupling ring 12 also has, on an axial side facing the drive gearwheel 13, a driver contour 25 that is shaped to be complementary to the driver contour 24 of the drive gearwheel 13.
  • the two Mit supportivekonturen 24, 25 cooperate for torque transmission, while they are released in the disengaged state of the coupling ring 12 from each other, so that no torque transmission takes place.
  • FIGS. 2 and 3 the engaged state of the coupling ring 12 and the coupling 9 is shown.
  • the axial cam contours 24, 25 of the drive gear 13 and the clutch ring 12 are engaged with each other and close the power path 10 to transmit torque from the drive gear 13 via the clutch ring 12 to the crank drive 14.
  • the coupling 9 and the coupling ring 12 thus the striking mechanism 5 is activated.
  • the switching device 7 is equipped with an actuator 27 in the embodiments presented here.
  • This comprises a manually operable actuating element 28 and a lifting element 29.
  • the actuating device 27 couples the coupling ring 12 with the actuating element 28 in order to be able to engage or disengage the coupling 9 or the coupling ring 12.
  • the movement is transmitted by means of the lifting element 29.
  • This has at least one arm portion 30, which extends parallel to the axis of rotation 17 of the drive gear 13.
  • the lifting element 29 in each case has two such arm sections 30, which are arranged diametrically opposite one another with respect to the axis of rotation 17 of the drive gearwheel 13. In other words, the two arm portions 30 face each other at an angle of 180 °.
  • the respective arm portion 30 is coupled to the coupling ring 12, such that a direction away from the drive gear 13 stroke adjustment of the lifting element 29 which extends parallel to the axis of rotation 17 of the drive gear 13, the coupling ring 12 entrains and disengages or engages in opposite stroke direction.
  • the lifting element 29 has a ring portion 31, from which the two arm portions 30 protrude, which is aligned coaxially to the axis of rotation 17 of the drive gear 13 and which is located on a side facing away from the drive gear 13 side of the crank gear 14.
  • the arm sections 30 laterally overlap the crank drive wheel 14 and terminate in the region of the coupling ring 12.
  • the arm portions 30 are reinforced with stiffening brackets 32.
  • the stiffening brackets 32 are substantially U-shaped and engage behind the coupling ring 12.
  • a U-base 33 of the respective stiffening bracket 32 lies flat against the rest of the body of the respective arm portion 30. A respect.
  • proximal U-leg 34 causes the engagement or the engaging behind the coupling ring 12. A respect.
  • distal U-leg 35 engages in a corresponding recess in the ring portion 31 a.
  • the actuating device 27 can in particular with regard to Fig. 6 be equipped with a lifting drive 36.
  • Said lifting drive 36 can convert a manual actuation of the actuating element 28 into a stroke adjustment of the lifting element 29.
  • the lifting drive 36 is designed so that it converts a rotary actuation of the actuating element 28 about an axis of rotation 37 in a parallel to this axis of rotation 37 oriented stroke adjustment of the lifting element 29.
  • the axis of rotation 37 of the actuating element 28 coincides with the axis of rotation 17 of the drive gear 13, so that the stroke of the lifting element 29 extends parallel to the axis of rotation 17.
  • the lifting drive 36 acts together with the annular portion 31 of the lifting element 29.
  • the ring section 31 according to the embodiment shown here may have at least one radially inwardly projecting sliding body 38. In the example, three such sliding bodies 38 are provided, which are arranged distributed uniformly relative to each other in the circumferential direction.
  • the lifting drive 36 has a sleeve 39 which is rotatable coaxially with the ring portion 31.
  • This sleeve 39 has radially outside at least one ramp 40 which rises axially in the circumferential direction of the sleeve 39.
  • a ramp 40 is provided per slider 38.
  • the sleeve 39 has three circumferentially spaced ramps 40.
  • the respective ramp 40 in each case cooperates with one of the sliding bodies 38, such that a rotary adjustment of the sleeve 39 is converted into a stroke adjustment of the lifting element 29.
  • the lifting element 29 is rotatably disposed in the housing 41 or in a housing portion of the hammer drill 1, but stored adjustable in stroke.
  • the sliding body 38 slide along the respective ramp 40, resulting in a stroke adjustment of the lifting element 29.
  • the ramps 40 may be equipped at its lower end and / or at its upper end with a latching step 42.
  • the slider 38 engages upon reaching the respective end position in the respective latching step 42, whereby a haptic tactile non-positive locking arises in the manner of a pressure point, which obstructs or prevents an automatic adjustment of the sleeve 39 and thus of the actuating element 28.
  • the actuator 28 is rotatably connected to the sleeve 39.
  • a screw 43 is screwed from the inside through the sleeve 29 in the actuator 28.
  • the actuating element 28 is arranged on an outer side of the housing 41 of the hammer drill 1.
  • the sleeve 39 is disposed on an inner side of the housing 41.
  • a seal 44 may be arranged, which seals the housing 41 in the region of a passage opening 45. This seal 44 is so designed to allow rotational movements of the sleeve 39.
  • the sleeve 39 may have a cylindrical extension 46 which projects through the through hole 45 from the inside of the housing 41 into the outer side.
  • the extension 46 has a plurality of radial interruptions 47, in which engage portions of the actuating element 28 positively. This is, for example, in Fig. 2 recognizable.
  • the lifting element 29 has in the region of its arm portions 30 outwardly projecting longitudinal guides 48, in accordance with the Fig. 3 and 5 Guide elements 49 of the housing 41 engage. This gives the lifting element 29 a secure linear guide, which supports precise stroke adjustment.
  • an engagement spring 50 may be provided which drives the clutch ring 12 against the drive gear 13 axially.
  • the engagement spring 50 thus drives the coupling ring 12 in the engaged state.
  • the rotary drive gear 4 may suitably have a ring gear 51 with an axial spur toothing, which also meshes the drive pinion 15 of the drive motor 2 diametrically opposite the drive gear 13.
  • the ring gear 51 is rotatably mounted on the tool spindle 3 and cooperates with a torque clutch 52.
  • the torque clutch 52 has a driver ring 53 which is rotatably and axially displaceably arranged on the tool spindle 3 and is biased by means of a biasing spring 54 against the ring gear 51.
  • Coupling body 55 allow the entrainment of the ring 53 and thus the tool spindle 3.

Description

Die vorliegende Erfindung betrifft ein Elektrowerkzeug gemäß dem Oberbegriff des Patentanspruchs 1, insbesondere ein manuell betätigbares Elektrowerkzeug, vorzugsweise einen Bohrhammer.The present invention relates to a power tool according to the preamble of patent claim 1, in particular a manually operated power tool, preferably a hammer drill.

Ein derartiges Elektrowerkzeug geht beispielsweise aus der EP 1 950 009 A1 hervor. Üblicherweise umfasst ein Elektrowerkzeug, wie zum Beispiel ein Bohrhammer, einen Antriebsmotor, eine Werkzeugspindel zum drehenden Antreiben eines Werkzeugs, ein Drehantriebsgetriebe zum Koppeln des Antriebsmotors mit der Werkzeugspindel, ein Schlagwerk zum hämmernden Antreiben des Werkzeugs, ein Schlagwerksgetriebe zum Koppeln des Antriebsmotors mit dem Schlagwerk sowie eine Schalteinrichtung zum Aktivieren und Deaktivieren des Schlagwerks.Such a power tool is for example from the EP 1 950 009 A1 out. Typically, a power tool, such as a hammer drill, includes a drive motor, a tool spindle for rotationally driving a tool, a rotary drive gear for coupling the drive motor to the tool spindle, a hammer mechanism for hammering the tool, a hammer mechanism for coupling the drive motor to the hammer mechanism, and a switching device for activating and deactivating the striking mechanism.

Die vorliegende Erfindung beschäftigt sich mit dem Problem, für ein derartiges Elektrowerkzeug eine verbesserte oder zumindest eine andere Ausführungsform anzugeben, die sich insbesondere durch eine kompakte Bauform auszeichnet. Dieses Problem wird erfindungsgemäß durch den Gegenstand des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.The present invention is concerned with the problem of providing for such a power tool an improved or at least another embodiment, which is characterized in particular by a compact design. This problem is solved according to the invention by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.

Die Erfindung beruht auf dem allgemeinen Gedanken, die Schalteinrichtung mit einer Kupplung auszustatten, die in den Kraftpfad des Schlagwerksgetriebes eingebunden ist und die zum Einrücken und Ausrücken, also zum Aktivieren und Deaktivieren des Schlagwerks einen Betätigungshub aufweist. Dabei ist die Schalteinrichtung so ausgestaltet, dass eine Hubrichtung dieses Betätigungshubs sich quer zur Drehachse der Werkzeugspindel erstreckt oder sich parallel zu einer Drehachse eines manuell drehbetätigbaren Betätigungselements der Schalteinrichtung erstreckt. Ebenso kann sich der Betätigungshub sowohl quer zur Drehachse der Werkzeugspindel als auch parallel zur Drehachse des Betätigungselements erstrecken. Der Betätigungshub der Kupplung entspricht dabei einer linearen Verstellbewegung eines entsprechenden Kupplungsglieds, das das Einrücken bzw. das Ausrücken der Kupplung bewirkt. Die Orientierung des Betätigungshubs quer zur Drehachse der Werkzeugspindel bzw. parallel zur Drehachse des Betätigungselements und die Integration der Kupplung in das Schlagwerksgetriebe ermöglicht eine räumlich nahe Anordnung der Schalteinrichtung an der Werkzeugspindel, wodurch sich insgesamt ein kompakter Aufbau für das Elektrowerkzeug realisieren lässt. Die Kupplung kann besonders einfach in den Kraftpfad des Schlagwerksgetriebes eingebunden werden, dadurch dass das Schlagwerksgetriebe ein eingangsseitiges Antriebszahnrad aufweist, das um eine Drehachse drehbar gelagert ist, und das Schlagwerksgetriebe ein ausgangsseitiges Kurbeltriebrad aufweist, das um die Drehachse des Antriebszahnrads drehbar gelagert ist und bei aktiviertem Schlagwerk ein Pleuel des Schlagwerks antreibt. Die Kupplung umfasst im Schlagwerksgetriebe einen Kupplungsring, der koaxial zur Drehachse des Antriebszahnrads am Kurbeltriebrad angeordnet ist und am Kurbeltriebrad axial verstellbar und drehfest angeordnet ist. Zum Einrücken und Ausrücken der Kupplung wirkt nun dieser Kupplungsring mit dem Antriebszahnrad zusammen, derart, dass der Kupplungsring im eingerückten Zustand Drehmoment vom Antriebszahnrad auf das Kurbeltriebrad überträgt, während im ausgerückten Zustand keine Drehmomentübertragung vom Antriebszahnrad über den Kupplungsring an das Kurbeltriebrad erfolgt. Die hier vorgestellte Bauweise führt zu einer besonders kompakten Integration der Kupplung in das Schlagwerksgetriebe.The invention is based on the general idea to equip the switching device with a clutch which is integrated into the force path of the percussion gear and which has an actuating stroke for engagement and disengagement, ie for activating and deactivating the impact mechanism. In this case, the switching device is designed such that a stroke direction of this actuating stroke extends transversely to the axis of rotation of the tool spindle or parallel to a rotational axis of a manually rotatable actuatable element of the switching device extends. Likewise, the actuating stroke can extend both transversely to the axis of rotation of the tool spindle and parallel to the axis of rotation of the actuating element. The actuating stroke of the clutch corresponds to a linear adjustment movement of a corresponding coupling member, which causes the engagement or disengagement of the clutch. The orientation of the actuating stroke transverse to the axis of rotation of the tool spindle or parallel to the axis of rotation of the actuating element and the integration of the coupling in the percussion gear allows a spatially close arrangement of the switching device on the tool spindle, which can be a total of a compact design for the power tool realize. The coupling can be integrated into the force path of the percussion gear mechanism in a particularly simple manner, in that the percussion gear mechanism has an input-side drive gear which is rotatably mounted about an axis of rotation, and the percussion gear mechanism has an output-side crank drive wheel, which is rotatably mounted about the axis of rotation of the drive gear wheel and activated Schlagwerk drives a connecting rod of the striking mechanism. The clutch comprises in the hammer mechanism a coupling ring which is arranged coaxially to the axis of rotation of the drive gear on the crank gear and is arranged axially adjustable and rotationally fixed on the crank drive. For engaging and disengaging the clutch now this coupling ring interacts with the drive gear, such that the coupling ring transmits torque from the drive gear to the crank gear in the engaged state, while in the disengaged state no torque transmission from the drive gear via the coupling ring to the crank drive. The design presented here leads to a particularly compact integration of the clutch in the percussion gearbox.

Entsprechend der Erfindung weist das Antriebszahnrad an einer dem Kurbeltriebrad zugewandten Axialseite eine Mitnehmerkontur auf, während der Kupplungsring an einer dem Antriebszahnrad zugewandten Axialseite eine zur Mitnehmerkontur des Antriebszahnrads komplementäre Mitnehmerkontur aufweist, die im eingerückten Zustand des Kupplungsrings zur Drehmomentübertragung mit der Mitnehmerkontur des Antriebszahnrads zusammenwirkt und im ausgerückten Zustand axial davon freikommt. Die axialen Mitnehmerkonturen können große Drehmomente übertragen und benötigen nur wenig Einbauraum.According to the invention, the drive gear on a side facing the crank gear on a Mitnehmerkontur, while the coupling ring on a drive gear facing axial side complementary to Mitnehmerkontur the drive gear Mitnehmerkontur which cooperates in the engaged state of the coupling ring for torque transmission with the Mitnehmerkontur the drive gear and in disengaged state axially free of it. The axial Mitnehmerkonturen can transmit large torques and require little installation space.

Besonders zweckmäßig ist nun eine Weiterbildung, bei welcher die Schalteinrichtung eine Betätigungseinrichtung zum Einrücken und Ausrücken der Kupplung aufweist, die ein manuell betätigbares Betätigungselement mit einem verstellbaren Kupplungsglied der Kupplung koppelt. Beim Kupplungsglied handelt es sich zweckmäßig um den Kupplungsring. Das vorzugsweise außen an einem Gehäuse des Elektrowerkzeugs angeordnete Betätigungselement ermöglicht den Eingriff in das Schlagwerksgetriebe bzw. in die Kupplung, um diese einzurücken bzw. auszurücken.Particularly useful is now a development in which the switching device has an actuating device for engagement and disengagement of the coupling, which couples a manually operable actuating element with an adjustable coupling member of the clutch. The coupling member is expediently the coupling ring. The actuating element, which is preferably arranged on the outside of a housing of the power tool, makes it possible to engage in the percussion gear mechanism or in the clutch in order to engage or disengage it.

Vorzugsweise kann die Betätigungseinrichtung mit einem Hubelement ausgestattet sein, das über wenigstens einen parallel zur Drehachse des Antriebszahnrads verlaufenden Armabschnitt mit dem Kupplungsring gekoppelt ist, sodass eine vom Antriebszahnrad weggerichtete Hubverstellung des Hubelements parallel zur Drehachse des Antriebszahnrads den Kupplungsring mitnimmt und ausrückt. Auf diese Weise übergreift die Betätigungseinrichtung mit dem jeweiligen Armabschnitt des Hubelements das Kurbeltriebrad, um mit dem Kupplungsring in Eingriff zu kommen. Dies ermöglicht eine besonders raumsparende Anordnung der Betätigungseinrichtung koaxial zur Drehachse des Antriebszahnrads.Preferably, the actuating device may be equipped with a lifting element which is coupled via at least one parallel to the axis of rotation of the drive gear arm portion with the coupling ring, so that a direction away from the drive gear stroke adjustment of the lifting element parallel to the axis of rotation of the drive gear entrains the clutch ring and disengages. In this way, the actuating device engages with the respective arm portion of the lifting element, the crank drive wheel to come into engagement with the coupling ring. This allows a particularly space-saving arrangement of the actuator coaxial with the axis of rotation of the drive gear.

Gemäß einer anderen vorteilhaften Ausführungsform kann zur Realisierung einer drehfesten und axial verstellbaren Kopplung zwischen dem Kupplungsring und dem Kurbeltriebrad vorgesehen sein, das Kurbeltriebrad in einem Axialabschnitt mit einer außen liegenden Mitnehmerkontur auszustatten und den Kupplungsring mit einer dazu komplementären innen liegenden Mitnehmerkontur zu versehen, so dass der Kupplungsring über diese Mitnehmerkonturen drehfest und axial verstellbar am Kurbeltriebrad angeordnet ist. Besonders zweckmäßig ist dabei eine Weiterbildung, bei welcher die Mitnehmerkonturen als Polygonprofile ausgestaltet sind. Diese ermöglichen eine besonders hohe Drehmomentübertragung bei geringem Verschleiß. Die vorgeschlagene Bauweise ermöglicht einen besonders kompakten Aufbau bei hoher Funktionssicherheit.According to another advantageous embodiment, to realize a rotationally fixed and axially adjustable coupling between the coupling ring and the crank drive be provided to equip the crank drive in an axial section with an outer driver contour and to provide the coupling ring with a complementary inner driver contour, so that the Coupling ring on these Mitnehmerkonturen rotationally fixed and axially adjustable is arranged on the crank drive wheel. Particularly expedient is a development in which the driver contours are designed as polygonal profiles. These allow a particularly high torque transmission with low wear. The proposed construction allows a particularly compact design with high reliability.

Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen.Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Es zeigen, jeweils schematisch,

Fig. 1
eine Seitenansicht eines als Bohrhammer ausgestalteten Elektrowerkzeugs,
Fig. 2
einen Längsschnitt des Bohrhammers in einem in Fig. 1 mit II markierten Bereich einer Schalteinrichtung bei aktiviertem Schlagwerk,
Fig. 3
einen Querschnitt des Bohrhammers entsprechend Schnittlinien III in Fig. 2,
Fig. 4
einen Längsschnitt wie in Fig. 2, jedoch bei deaktiviertem Schlagwerk,
Fig. 5
einen Querschnitt des Bohrhammers entsprechend Schnittlinien V in Fig. 4,
Fig. 6
eine auseinandergezogene, perspektivische Ansicht einer Betätigungseinrichtung und eines Gehäuseabschnitts,
Fig. 7
eine auseinander gezogene, perspektivische Ansicht im Bereich einer Kupplung bei einer anderen Ausführungsform.
Show, in each case schematically,
Fig. 1
a side view of a designed as a hammer drill power tool,
Fig. 2
a longitudinal section of the hammer drill in a in Fig. 1 with II marked area of a switching device with activated striking mechanism,
Fig. 3
a cross section of the hammer drill according to section lines III in Fig. 2 .
Fig. 4
a longitudinal section as in Fig. 2 , but with deactivated percussion,
Fig. 5
a cross section of the hammer drill according to section lines V in Fig. 4 .
Fig. 6
an exploded perspective view of an actuator and a housing portion,
Fig. 7
an exploded perspective view in the region of a coupling in another embodiment.

Entsprechend Fig. 1 umfasst ein Elektrowerkzeug 1, das manuell betätigbar ist und im Beispiel als Bohrhammer ausgestaltet ist, ein Gehäuse 41, das z. B. eine L-Form besitzt, da ein Spindelabschnitt 59 des Gehäuses 41 und ein Motorabschnitt 60 des Gehäuses 41 etwa um 90° zueinander versetzt angeordnet sind. Im Spindelabschnitt 59 erstreckt sich eine Werkzeugspindel 3, die an ihrem aus dem Gehäuse 41 herausstehenden Ende eine Werkzeugaufnahme 61 trägt. Im Inneren des Motorabschnitts 60 ist ein Antriebsmotor 2 untergebracht. Die Längsrichtung des Spindelabschnitts 59 ist durch die Drehachse 8 der Werkzeugspindel 3 definiert und erstreckt sich dazu parallel. Die Längsachse des Motorabschnitts 60 ist durch die Drehachse 18 einer Antriebswelle des Antriebsmotors 2 definiert und erstreckt sich dazu parallel.Corresponding Fig. 1 includes a power tool 1, which is manually operable and is configured in the example as a hammer drill, a housing 41, the z. B. has an L-shape, since a spindle portion 59 of the housing 41 and a motor portion 60 of the housing 41 are arranged offset by approximately 90 ° to each other. In the spindle section 59, a tool spindle 3 extends, which carries a tool holder 61 at its end protruding from the housing 41. Inside the motor section 60, a drive motor 2 is housed. The longitudinal direction of the spindle section 59 is defined by the axis of rotation 8 of the tool spindle 3 and extends parallel thereto. The longitudinal axis of the motor portion 60 is defined by the axis of rotation 18 of a drive shaft of the drive motor 2 and extends parallel thereto.

Parallel zum Motorgehäuse 60 besitzt das Gehäuse 41 einen Griffabschnitt 62, der im Beispiel an zwei voneinander beabstandeten Enden einerseits am Spindelabschnitt 59 und andererseits am Motorabschnitt 60 angebracht ist. Über den Griffabschnitt 62 kann der Bohrhammer 1 bzw. das Elektrowerkzeug 1 mit einem Kabel 63 an eine externe Stromversorgung angeschlossen sein. Bei einer alternativen Ausführungsform kann der Bohrhammer 1 auch mit einem Akku ausgestattet sein, so dass er unabhängig von einem Stromnetz betrieben werden kann.Parallel to the motor housing 60, the housing 41 has a handle portion 62, which in the example at two spaced ends on the one hand on the spindle portion 59 and on the other hand attached to the motor section 60. About the handle portion 62 of the hammer drill 1 and the power tool 1 may be connected by a cable 63 to an external power supply. In an alternative embodiment, the hammer drill 1 can also be equipped with a rechargeable battery, so that it can be operated independently of a power grid.

Fig. 1 zeigt den Bohrhammer 1 in einer aufrechten oder vertikalen typischen Arbeitsposition, in welcher der Spindelabschnitt 59 horizontal orientiert ist, während der Motorabschnitt 60 vertikal orientiert ist. Hierdurch werden am Bohrhammer 1 bzw. an dessen Gehäuse 41 eine Oberseite 64 und eine Unterseite 65 definiert. Ein Betätigungselement 28 einer Schalteinrichtung 7 ist in einem mit II gekennzeichneten Bereich des Gehäuses 41 an der Oberseite 64 angeordnet. Besagter Bereich II befindet sich vertikal oberhalb des Motorabschnitts 60, insbesondere im Bereich einer Anschlussstelle 66 zwischen Griffabschnitt 62 und Spindelabschnitt 59. Die Schalteinrichtung 7 dient zum Aktivieren und Deaktivieren eines Hammerwerks oder Hammerbetriebs des Bohrhammers 1. Bei deaktivierten Hammerbetrieb kann der Bohrhammer 1 als reine Bohrmaschine verwendet werden. Die Schalteinrichtung 7 besitzt das Betätigungselement 28, das manuell betätigbar ist, um das Hammerwerk zuzuschalten oder abzuschalten. Hierzu ist das Betätigungselement 28 um eine Drehachse 37 drehbar angeordnet. Die Drehachse 37 erstreckt sich im Beispiel parallel zur Drehachse 18 des Antriebsmotors 2. Fig. 1 shows the hammer drill 1 in an upright or vertical typical working position, in which the spindle portion 59 is oriented horizontally, while the motor portion 60 is oriented vertically. As a result, an upper side 64 and a lower side 65 are defined on the hammer drill 1 or on its housing 41. An actuating element 28 of a switching device 7 is arranged on the upper side 64 in a region of the housing 41 marked II. Said area II is located vertically above the motor portion 60, in particular in the region of a connection point 66 between handle portion 62 and spindle portion 59. The switching device 7 is used to activate and deactivate a hammer mill or hammer operation of the hammer drill 1. When disabled hammer operation of the hammer drill 1 as a pure drill be used. The switching device 7 has the actuator 28 which is manually operable to turn on or off the hammer mill. For this purpose, the actuating element 28 is arranged rotatably about a rotation axis 37. The axis of rotation 37 extends in the example parallel to the axis of rotation 18 of the drive motor. 2

Entsprechend den Fig. 2 bis 5 umfasst ein solcher manuell betätigbarer Bohrhammer 1 einen Antriebsmotor 2, eine Werkzeugspindel 3, ein Drehantriebsgetriebe 4, ein Schlagwerk 5, ein Schlagwerksgetriebe 6 und eine Schalteinrichtung 7. Die Werkzeugspindel 3 rotiert im Betrieb um eine Drehachse 8 und dient zum drehenden Antreiben eines hier nicht dargestellten Werkzeugs, insbesondere eines Schlagbohrers. Das Drehantriebsgetriebe 4 koppelt den Antriebsmotor 2 mit der Werkzeugspindel 3. Das Schlagwerk 5 dient zum hämmernden Antreiben des Werkzeugs. Im Beispiel arbeitet das Schlagwerk 2 pneumatisch. Das Schlagwerksgetriebe 6 koppelt den Antriebsmotor 2 mit dem Schlagwerk 5. Mit Hilfe der Schalteinrichtung 7 kann das Schlagwerk 5 aktiviert und deaktiviert werden. Bei deaktiviertem Schlagwerk 5 kann der Bohrhammer 1 als reine Bohrmaschine genutzt werden, sodass das jeweilige Werkzeug dann nur drehend und nicht hämmernd angetrieben ist.According to the Fig. 2 to 5 such a manually operable hammer drill 1 comprises a drive motor 2, a tool spindle 3, a rotary drive gear 4, a striking mechanism 5, a percussion gear 6 and a switching device 7. The tool spindle 3 rotates in operation about a rotation axis 8 and serves for the rotational driving of a not shown here Tool, in particular a percussion drill. The rotary drive gear 4 couples the drive motor. 2 with the tool spindle 3. The striking mechanism 5 is used for hammering driving the tool. In the example the Schlagwerk 2 works pneumatically. The percussion gear 6 couples the drive motor 2 with the striking mechanism 5. With the help of the switching device 7, the striking mechanism 5 can be activated and deactivated. When the impact mechanism 5 is deactivated, the hammer drill 1 can be used as a pure drilling machine, so that the respective tool is then driven only in a rotating and non-hammering manner.

Die Schalteinrichtung 7 ist mit einer Kupplung 9 ausgestattet, die in einen - mit unterbrochener Linie angedeuteten - Kraftpfad 10 des Schlagwerksgetriebes 6 eingebunden ist. Die Kupplung 9 besitzt einen durch einen Doppelpfeil angedeuteten Betätigungshub 11, der sich quer zur Rotationsachse 8 der Werkzeugspindel 3 erstreckt. Der Betätigungshub 11 charakterisiert sich durch die Bewegungsrichtung eines Kupplungsglieds 12, in der das Kupplungsglied 12 zum Einrücken und Ausrücken der Kupplung 9 verstellbar ist.The switching device 7 is equipped with a coupling 9, which is integrated in a - indicated by a broken line - power path 10 of the percussion gear 6. The coupling 9 has an actuating stroke 11, indicated by a double arrow, which extends transversely to the axis of rotation 8 of the tool spindle 3. The actuating stroke 11 is characterized by the direction of movement of a coupling member 12, in which the coupling member 12 for engagement and disengagement of the clutch 9 is adjustable.

Beim Kupplungsglied 12 handelt es sich bei den hier vorgestellten Ausführungsformen um einen Kupplungsring, der im Folgenden ebenfalls mit 12 bezeichnet wird. Dieser Kupplungsring 12 ist im Schlagwerksgetriebe 6 angeordnet. Im Kraftpfad 10 befindet sich der Kupplungsring 12 zwischen einem eingangsseitigen Antriebszahnrad 13 des Schlagwerksgetriebes 6 und einem ausgangsseitigen Kurbeltriebrad 14 des Schlagwerksgetriebes 6. Das Antriebszahnrad 13 kämmt mit einem Antriebsritzel 15 einer Antriebswelle 16 des Antriebsmotors 2. Das Antriebszahnrad 13 ist um eine Drehachse 17 drehbar gelagert, die sich im Beispiel achsparallel zu einer Drehachse 18 der Antriebswelle 16 des Antriebsmotors 2 erstreckt. Dabei ist das Antriebszahnrad 13 an einer stehenden Welle 19 drehbar gelagert. Das Kurbeltriebrad 14 ist ebenfalls um die Drehachse 17 des Antriebszahnrads 13 drehbar gelagert. Im Beispiel ist das Kurbeltriebrad 14 ebenfalls an der stehenden Welle 19 drehbar gelagert. Bei aktiviertem Schlagwerk 5 treibt das Kurbeltriebrad 14 ein Pleuel 20 des Schlagwerks 5 an, das bspw. einen Kolben 21 oszillierend antreibt, der in der hohlen Werkzeugspindel 3 hubverstellbar gelagert ist.When coupling member 12 is in the embodiments presented here is a coupling ring, which is also referred to below with 12. This coupling ring 12 is arranged in the percussion gear 6. The drive gear 13 meshes with a drive pinion 15 of a drive shaft 16 of the drive motor 2. The drive gear 13 is rotatably mounted about an axis of rotation 17 in the power path 10, the coupling ring 12 between an input side drive gear 13 of the percussion gear 6 and the output side crank drive , which in the example extends axially parallel to a rotation axis 18 of the drive shaft 16 of the drive motor 2. The drive gear 13 is rotatably mounted on a stationary shaft 19. The crank gear 14 is also rotatably supported about the rotation axis 17 of the drive gear 13. In the example, the crank gear 14 is also rotatably mounted on the stationary shaft 19. With activated Schlagwerk 5 drives the Crankshaft 14, a connecting rod 20 of the percussion mechanism 5, which, for example, a piston 21 oscillatingly drives, which is mounted in a stroke-adjustable manner in the hollow tool spindle 3.

Der Kupplungsring 12 ist koaxial zur Drehachse 17 des Antriebszahnrads 13 am Kurbeltriebrad 14 angeordnet, und zwar so, dass er am Kurbeltriebrad 14 axial verstellbar ist und gleichzeitig damit drehfest gekoppelt ist. Erreicht wird diese axiale Verstellbarkeit bei gleichzeitiger drehfester Sicherung entsprechend der Ausführungsform der Fig. 2 bis 5 bspw. durch eine Axialverzahnung. Bei den hier dargestellten Ausführungsbeispielen besitzt das Kurbeltriebrad 14 einen Axialabschnitt 22, der sich koaxial zur Drehachse 17 des Antriebszahnrads 13 erstreckt. Dieser Axialabschnitt 22 weist radial außen eine axial verlaufende Mitnehmerkontur 23 auf, die mit einer dazu komplementären Mitnehmerkontur 56 des Kupplungsrings 12 zusammenwirkt. In der Folge ermöglichen die beiden miteinander zusammenwirkenden Mitnehmerkonturen 23, 56 eine drehfeste und axial verstellbare Anordnung des Kupplungsrings 12 am zylindrischen Abschnitt 22 des Kurbeltriebrads 14. Bspw. besitzt die eine Mitnehmerkontur 23 entsprechend den Fig. 2 bis 5 zumindest einen Axialsteg, während die andere Mitnehmerkontur 56 komplementär dazu zumindest eine axial verlaufende Aufnahmenut aufweist. Alternativ dazu zeigt Fig. 7 eine Ausführungsform, bei welcher das Kurbeltriebrad 14 ein außen liegendes Polygonprofil 57 aufweist, während der Kupplungsring 12 ein innen liegendes Polygonprofil 58 aufweist, das komplementär zum außen liegenden Polygonprofil 57 geformt ist. Im ineinander gesteckten Zustand realisieren die miteinander zusammenwirkenden Polygonprofile 57, 58 eine drehfeste und axial verschiebbare Kopplung zwischen Kupplungsring 12 und Kurbeltriebrad 14.The coupling ring 12 is arranged coaxially to the axis of rotation 17 of the drive gear 13 on the crank gear 14, in such a way that it is axially adjustable on the crank gear 14 and at the same time is rotatably coupled thereto. Achieves this axial adjustability while rotating non-locking according to the embodiment of Fig. 2 to 5 for example by an axial toothing. In the embodiments shown here, the crank drive wheel 14 has an axial section 22 which extends coaxially to the axis of rotation 17 of the drive gear 13. This axial section 22 has radially outwardly an axially extending driver contour 23 which cooperates with a complementary driver contour 56 of the coupling ring 12. As a result, the two co-operating Mitnehmerkonturen 23, 56 allow a rotationally fixed and axially adjustable arrangement of the coupling ring 12 on the cylindrical portion 22 of the crank drive gear 14. For example. has the one Mitnehmerkontur 23 according to the Fig. 2 to 5 at least one axial web, while the other cam contour 56 has complementary thereto at least one axially extending receiving groove. Alternatively to this shows Fig. 7 an embodiment in which the crank drive wheel 14 has an external polygonal profile 57, while the coupling ring 12 has an internal polygonal profile 58, which is formed complementary to the outer polygonal profile 57. In the nested state, the cooperating polygonal profiles 57, 58 realize a rotationally fixed and axially displaceable coupling between coupling ring 12 and crank drive wheel 14.

Bei der in Fig. 7 wiedergegebenen Ausführungsform ist die außen liegende Mitnehmerkontur 23 des Kurbeltriebrads 14 als außen liegendes Polygonprofil ausgestaltet, während die innen liegende Mitnehmerkontur 56 des Kupplungsrings 12 als dazu komplementäres, innen liegendes Polygonprofil 58 ausgestaltet ist.At the in Fig. 7 reproduced embodiment, the outer driver contour 23 of the crank drive wheel 14 is designed as an external polygonal profile, while the inner driver contour 56 of the coupling ring 12 is designed as a complementary, internal polygonal profile 58.

Bei dem in Fig. 7 wiedergegebenen Abschnitt der Kupplung 9 sind zusätzlich zum Kurbeltriebrad 14 und zum Kupplungsring 12 außerdem das Antriebszahnrad 13, ein Nadellager 67 zum Lagern des Antriebszahnrads 13 an der Welle 19, eine Scheibe 68, eine Einrückfeder 50 zum axialen Vorspannen des Kupplungsrings 12 gegen das Antriebszahnrad 13, ein Nadellager 69 zum Lagern des Kurbeltriebrads 14 an der Welle 19, eine Scheibe 70 und ein Sicherungsring 71 dargestellt.At the in Fig. 7 reproduced portion of the clutch 9 are in addition to the crank gear 14 and the clutch ring 12 also the drive gear 13, a needle bearing 67 for supporting the drive gear 13 on the shaft 19, a disc 68, a clutch spring 50 for axially biasing the clutch ring 12 against the drive gear 13, a needle bearing 69 for supporting the crank gear 14 on the shaft 19, a disc 70 and a locking ring 71 shown.

Das Antriebszahnrad 13 weist an einer dem Kurbeltriebrad 14 zugewandten Axialseite eine Mitnehmerkontur 24 auf. Der Kupplungsring 12 weist an einer dem Antriebszahnrad 13 zugewandten Axialseite ebenfalls eine Mitnehmerkontur 25 auf, die komplementär zur Mitnehmerkontur 24 des Antriebszahnrads 13 geformt ist. Im eingerückten Zustand des Kupplungsrings 12 bzw. der Kupplung 9 wirken die beiden Mitnehmerkonturen 24, 25 zur Drehmomentübertragung zusammen, während sie im ausgerückten Zustand des Kupplungsrings 12 voneinander freikommen, sodass keine Drehmomentübertragung erfolgt. Beispielsweise besitzt die eine Mitnehmerkontur 24 zumindest einen in Fig. 2 erkennbaren Stift, während die andere Mitnehmerkontur 25 komplementär dazu zumindest eine Stiftaufnahme aufweist, in welche der Stift axial eingreifen kann.The drive gear 13 has a driver contour 24 on an axial side facing the crank drive wheel 14. The coupling ring 12 also has, on an axial side facing the drive gearwheel 13, a driver contour 25 that is shaped to be complementary to the driver contour 24 of the drive gearwheel 13. In the engaged state of the clutch ring 12 and the clutch 9, the two Mitnehmerkonturen 24, 25 cooperate for torque transmission, while they are released in the disengaged state of the coupling ring 12 from each other, so that no torque transmission takes place. For example, has a driver contour 24 at least one in Fig. 2 recognizable pin, while the other cam contour 25 has complementary thereto at least one pin receptacle, in which the pin can engage axially.

In den Fig. 2 und 3 ist der eingerückte Zustand des Kupplungsrings 12 bzw. der Kupplung 9 wiedergegeben. Die axialen Mitnehmerkonturen 24, 25 des Antriebszahnrads 13 und des Kupplungsrings 12 stehen miteinander in Eingriff und schließen den Kraftpfad 10, um Drehmoment vom Antriebszahnrad 13 über den Kupplungsring 12 auf das Kurbeltriebrad 14 zu übertragen. Im eingerückten Zustand der Kupplung 9 bzw. des Kupplungsrings 12 ist somit das Schlagwerk 5 aktiviert.In the FIGS. 2 and 3 the engaged state of the coupling ring 12 and the coupling 9 is shown. The axial cam contours 24, 25 of the drive gear 13 and the clutch ring 12 are engaged with each other and close the power path 10 to transmit torque from the drive gear 13 via the clutch ring 12 to the crank drive 14. In the engaged state the coupling 9 and the coupling ring 12 thus the striking mechanism 5 is activated.

Im Unterschied dazu zeigen die Fig. 4 und 5 das deaktivierte Schlagwerk 5. Hierzu ist der Kupplungsring 12 bzw. die Kupplung 9 ausgerückt, sodass die einander zugeordneten Mitnehmerkonturen 24, 25 von Antriebszahnrad 13 und Kupplungsring 12 voneinander freikommen. Erkennbar ist in Fig. 4 und 5 ein Axialabstand 26, der einen Eingriff bzw. eine Drehmomentübertragung verhindert. Der Kraftpfad 10 ist dadurch unterbrochen.In contrast, the show 4 and 5 the deactivated striking mechanism 5. For this purpose, the coupling ring 12 and the clutch 9 is disengaged, so that the associated driver contours 24, 25 of drive gear 13 and coupling ring 12 free from each other. Is recognizable in 4 and 5 an axial distance 26 which prevents engagement or torque transmission. The force path 10 is interrupted.

Die Schalteinrichtung 7 ist bei den hier vorgestellten Ausführungsformen mit einer Betätigungseinrichtung 27 ausgestattet. Diese umfasst ein manuell betätigbares Betätigungselement 28 sowie ein Hubelement 29. Die Betätigungseinrichtung 27 koppelt den Kupplungsring 12 mit dem Betätigungselement 28, um die Kupplung 9 bzw. den Kupplungsring 12 einrücken bzw. ausrücken zu können. Die Bewegungsübertragung erfolgt dabei mittels des Hubelements 29. Dieses weist zumindest einen Armabschnitt 30 auf, der sich parallel zur Drehachse 17 des Antriebszahnrads 13 erstreckt. Bei den hier vorgestellten Beispielen weist das Hubelement 29 jeweils zwei derartige Armabschnitte 30 auf, die bezogen auf die Drehachse 17 des Antriebszahnrads 13 diametral zueinander angeordnet sind. Mit anderen Worten, die beiden Armabschnitte 30 liegen sich mit einem Winkel von 180° gegenüber. Hierdurch sind sie beidseitig der Drehachse 17 des Antriebszahnrads 13 angeordnet. Der jeweilige Armabschnitt 30 ist mit dem Kupplungsring 12 gekoppelt, derart, dass eine vom Antriebszahnrad 13 weggerichtete Hubverstellung des Hubelements 29, die sich parallel zur Drehachse 17 des Antriebszahnrads 13 erstreckt, den Kupplungsring 12 mitnimmt und ausrückt bzw. bei entgegen gesetzter Hubrichtung einrückt.The switching device 7 is equipped with an actuator 27 in the embodiments presented here. This comprises a manually operable actuating element 28 and a lifting element 29. The actuating device 27 couples the coupling ring 12 with the actuating element 28 in order to be able to engage or disengage the coupling 9 or the coupling ring 12. The movement is transmitted by means of the lifting element 29. This has at least one arm portion 30, which extends parallel to the axis of rotation 17 of the drive gear 13. In the examples presented here, the lifting element 29 in each case has two such arm sections 30, which are arranged diametrically opposite one another with respect to the axis of rotation 17 of the drive gearwheel 13. In other words, the two arm portions 30 face each other at an angle of 180 °. As a result, they are arranged on both sides of the axis of rotation 17 of the drive gear 13. The respective arm portion 30 is coupled to the coupling ring 12, such that a direction away from the drive gear 13 stroke adjustment of the lifting element 29 which extends parallel to the axis of rotation 17 of the drive gear 13, the coupling ring 12 entrains and disengages or engages in opposite stroke direction.

Das Hubelement 29 besitzt einen Ringabschnitt 31, von dem die beiden Armabschnitte 30 abstehen, der koaxial zur Drehachse 17 des Antriebszahnrads 13 ausgerichtet ist und der sich an einer vom Antriebszahnrad 13 abgewandten Seite des Kurbeltriebrads 14 befindet. Die Armabschnitte 30 überlappen seitlich das Kurbeltriebrad 14 und enden im Bereich des Kupplungsrings 12. Im Beispiel der Fig. 3, 5 und 6 sind die Armabschnitte 30 mit Versteifungsklammern 32 verstärkt. Die Versteifungsklammern 32 sind im Wesentlichen U-förmig gestaltet und hintergreifen den Kupplungsring 12. Insbesondere liegt eine U-Basis 33 des jeweiligen Versteifungsbügels 32 flächig am übrigen Körper des jeweiligen Armabschnitts 30 an. Ein bzgl. des Kupplungsrings 12 proximaler U-Schenkel 34 bewirkt den Eingriff bzw. das Hintergreifen des Kupplungsrings 12. Ein bzgl. des Kupplungsrings 12 distaler U-Schenkel 35 greift in eine entsprechende Aussparung im Ringabschnitt 31 ein. Durch die Aussteifung des Hubelements 29 mit Hilfe der Bügel 32 kann das Hubelement 29 aus Kunststoff spritzgeformt werden, während die Versteifungsbügel 32 bspw. aus Metall hergestellt sind.The lifting element 29 has a ring portion 31, from which the two arm portions 30 protrude, which is aligned coaxially to the axis of rotation 17 of the drive gear 13 and which is located on a side facing away from the drive gear 13 side of the crank gear 14. The arm sections 30 laterally overlap the crank drive wheel 14 and terminate in the region of the coupling ring 12. In the example of FIG Fig. 3 . 5 and 6 the arm portions 30 are reinforced with stiffening brackets 32. The stiffening brackets 32 are substantially U-shaped and engage behind the coupling ring 12. In particular, a U-base 33 of the respective stiffening bracket 32 lies flat against the rest of the body of the respective arm portion 30. A respect. Of the coupling ring 12 proximal U-leg 34 causes the engagement or the engaging behind the coupling ring 12. A respect. Of the coupling ring 12 distal U-leg 35 engages in a corresponding recess in the ring portion 31 a. By stiffening the lifting element 29 by means of the bracket 32, the lifting element 29 can be injection molded from plastic, while the stiffening bracket 32 are, for example. Made of metal.

Die Betätigungseinrichtung 27 kann insbesondere im Hinblick auf Fig. 6 mit einem Hubantrieb 36 ausgestattet sein. Besagter Hubantrieb 36 kann eine manuelle Betätigung des Betätigungselements 28 in eine Hubverstellung des Hubelements 29 umwandeln. Dabei ist der Hubantrieb 36 so konzipiert, dass er eine Drehbetätigung des Betätigungselements 28 um eine Drehachse 37 in eine parallel zu dieser Drehachse 37 orientierte Hubverstellung des Hubelements 29 umwandelt. Bei den hier bevorzugten Beispielen fällt die Drehachse 37 des Betätigungselements 28 mit der Drehachse 17 des Antriebszahnrads 13 zusammen, so dass sich auch der Hub des Hubelementes 29 parallel zur Drehachse 17 erstreckt. Der Hubantrieb 36 wirkt dabei mit dem Ringabschnitt 31 des Hubelements 29 zusammen. Hierzu kann der Ringabschnitt 31 entsprechend der hier gezeigten Ausführungsform zumindest einen radial nach innen vorstehenden Gleitkörper 38 aufweisen. Im Beispiel sind drei derartige Gleitkörper 38 vorgesehen, die relativ zueinander in Umfangsrichtung gleichmäßig verteilt angeordnet sind.The actuating device 27 can in particular with regard to Fig. 6 be equipped with a lifting drive 36. Said lifting drive 36 can convert a manual actuation of the actuating element 28 into a stroke adjustment of the lifting element 29. In this case, the lifting drive 36 is designed so that it converts a rotary actuation of the actuating element 28 about an axis of rotation 37 in a parallel to this axis of rotation 37 oriented stroke adjustment of the lifting element 29. In the examples preferred here, the axis of rotation 37 of the actuating element 28 coincides with the axis of rotation 17 of the drive gear 13, so that the stroke of the lifting element 29 extends parallel to the axis of rotation 17. The lifting drive 36 acts together with the annular portion 31 of the lifting element 29. For this purpose, the ring section 31 according to the embodiment shown here may have at least one radially inwardly projecting sliding body 38. In the example, three such sliding bodies 38 are provided, which are arranged distributed uniformly relative to each other in the circumferential direction.

Der Hubantrieb 36 weist eine Hülse 39 auf, die koaxial zum Ringabschnitt 31 drehbar ist. Diese Hülse 39 weist radial außen zumindest eine Rampe 40 auf, die in der Umfangsrichtung der Hülse 39 axial ansteigt. Im Beispiel ist je Gleitkörper 38 eine solche Rampe 40 vorgesehen. Dementsprechend weist die Hülse 39 drei in Umfangsrichtung verteilt angeordnete Rampen 40 auf. Die jeweilige Rampe 40 wirkt jeweils mit einem der Gleitkörper 38 zusammen, derart, dass eine Drehverstellung der Hülse 39 in eine Hubverstellung des Hubelements 29 umgewandelt wird. Das Hubelement 29 ist im Gehäuse 41 oder in einem Gehäuseabschnitt des Bohrhammers 1 drehfest angeordnet, jedoch hubverstellbar gelagert. Bei einer Drehverstellung der Hülse 39 gleiten die Gleitkörper 38 entlang der jeweiligen Rampe 40 ab, wodurch es zu einer Hubverstellung des Hubelements 29 kommt. Um die jeweilige obere oder untere Endstellung des Hubelements 29 zu sichern, können die Rampen 40 an ihrem unteren Ende und/oder an ihrem oberen Ende mit einer Raststufe 42 ausgestattet sein. Der Gleitkörper 38 greift bei Erreichen der jeweiligen Endstellung in die jeweilige Raststufe 42 ein, wodurch eine haptisch fühlbare kraftschlüssige Sicherung nach Art eines Druckpunkts entsteht, die ein selbsttätiges Verstellen der Hülse 39 und somit des Betätigungselements 28 behindert oder verhindert.The lifting drive 36 has a sleeve 39 which is rotatable coaxially with the ring portion 31. This sleeve 39 has radially outside at least one ramp 40 which rises axially in the circumferential direction of the sleeve 39. In the example, such a ramp 40 is provided per slider 38. Accordingly, the sleeve 39 has three circumferentially spaced ramps 40. The respective ramp 40 in each case cooperates with one of the sliding bodies 38, such that a rotary adjustment of the sleeve 39 is converted into a stroke adjustment of the lifting element 29. The lifting element 29 is rotatably disposed in the housing 41 or in a housing portion of the hammer drill 1, but stored adjustable in stroke. Upon a rotational adjustment of the sleeve 39, the sliding body 38 slide along the respective ramp 40, resulting in a stroke adjustment of the lifting element 29. In order to secure the respective upper or lower end position of the lifting element 29, the ramps 40 may be equipped at its lower end and / or at its upper end with a latching step 42. The slider 38 engages upon reaching the respective end position in the respective latching step 42, whereby a haptic tactile non-positive locking arises in the manner of a pressure point, which obstructs or prevents an automatic adjustment of the sleeve 39 and thus of the actuating element 28.

Das Betätigungselement 28 ist mit der Hülse 39 drehfest verbunden. Bspw. ist hierzu eine Schraube 43 von innen durch die Hülse 29 in das Betätigungselement 28 eingeschraubt. Das Betätigungselement 28 ist an einer Außenseite des Gehäuses 41 des Bohrhammers 1 angeordnet. Im Unterschied dazu ist die Hülse 39 an einer Innenseite des Gehäuses 41 angeordnet. Zwischen der Hülse 39 und dem Gehäuse 41 kann eine Dichtung 44 angeordnet sein, die das Gehäuse 41 im Bereich einer Durchgangsöffnung 45 dichtet. Diese Dichtung 44 ist dabei so konzipiert, dass sie Drehbewegungen der Hülse 39 zulässt. Zur drehfesten Verbindung zwischen Betätigungselement 28 und Hülse 39 kann die Hülse 39 einen zylindrischen Fortsatz 46 aufweisen, der durch die Durchgangsöffnung 45 von der Innenseite des Gehäuses 41 in die Außenseite vorsteht. Der Fortsatz 46 besitzt mehrere radiale Unterbrechungen 47, in welche Abschnitte des Betätigungselements 28 formschlüssig eingreifen. Dies ist bspw. in Fig. 2 erkennbar.The actuator 28 is rotatably connected to the sleeve 39. For example. For this purpose, a screw 43 is screwed from the inside through the sleeve 29 in the actuator 28. The actuating element 28 is arranged on an outer side of the housing 41 of the hammer drill 1. In contrast, the sleeve 39 is disposed on an inner side of the housing 41. Between the sleeve 39 and the housing 41, a seal 44 may be arranged, which seals the housing 41 in the region of a passage opening 45. This seal 44 is so designed to allow rotational movements of the sleeve 39. For the rotationally fixed connection between the actuating element 28 and the sleeve 39, the sleeve 39 may have a cylindrical extension 46 which projects through the through hole 45 from the inside of the housing 41 into the outer side. The extension 46 has a plurality of radial interruptions 47, in which engage portions of the actuating element 28 positively. This is, for example, in Fig. 2 recognizable.

Das Hubelement 29 besitzt im Bereich seiner Armabschnitte 30 nach außen abstehende Längsführungen 48, in die entsprechend den Fig. 3 und 5 Führungselemente 49 des Gehäuses 41 eingreifen. Hierdurch erhält das Hubelement 29 eine sichere Linearführung, was eine präzise Hubverstellung unterstützt.The lifting element 29 has in the region of its arm portions 30 outwardly projecting longitudinal guides 48, in accordance with the Fig. 3 and 5 Guide elements 49 of the housing 41 engage. This gives the lifting element 29 a secure linear guide, which supports precise stroke adjustment.

Des Weiteren kann wie in den Fig. 2 bis 5 und 7 gezeigt eine Einrückfeder 50 vorgesehen sein, die den Kupplungsring 12 gegen das Antriebszahnrad 13 axial antreibt. Die Einrückfeder 50 treibt somit den Kupplungsring 12 in den eingerückten Zustand an.Furthermore, as in the Fig. 2 to 5 and 7 shown an engagement spring 50 may be provided which drives the clutch ring 12 against the drive gear 13 axially. The engagement spring 50 thus drives the coupling ring 12 in the engaged state.

Das Drehantriebsgetriebe 4 kann zweckmäßig ein Tellerrad 51 mit einer axialen Stirnverzahnung besitzen, das ebenfalls das Antriebsritzel 15 des Antriebsmotors 2 diametral gegenüber dem Antriebszahnrad 13 kämmt. Das Tellerrad 51 ist dabei an der Werkzeugspindel 3 drehbar gelagert und wirkt mit einer Drehmomentkupplung 52 zusammen. Die Drehmomentkupplung 52 besitzt einen Mitnehmerring 53, der drehfest und axial verstellbar an der Werkzeugspindel 3 angeordnet ist und mit Hilfe einer Vorspannfeder 54 gegen das Tellerrad 51 vorgespannt ist. Kopplungskörper 55 ermöglichen die Mitnahme des Rings 53 und somit der Werkzeugspindel 3. Übersteigt das vom Tellerrad 51 auf die Werkzeugspindel 3 übertragene Drehmoment einen vorbestimmten Grenzwert, verdrängen die Kopplungskörper 55 den Ring 53 gegen die Vorspannung der Feder 54, wodurch das Tellerrad 51 auch bei stehender Werkzeugspindel 3 weiter drehen kann.The rotary drive gear 4 may suitably have a ring gear 51 with an axial spur toothing, which also meshes the drive pinion 15 of the drive motor 2 diametrically opposite the drive gear 13. The ring gear 51 is rotatably mounted on the tool spindle 3 and cooperates with a torque clutch 52. The torque clutch 52 has a driver ring 53 which is rotatably and axially displaceably arranged on the tool spindle 3 and is biased by means of a biasing spring 54 against the ring gear 51. Coupling body 55 allow the entrainment of the ring 53 and thus the tool spindle 3. Exceeds the transmitted from the ring gear 51 to the tool spindle 3 torque exceeds a predetermined limit, displace the coupling body 55, the ring 53 against the bias of the spring 54, whereby the ring gear 51 even when stationary Tool spindle 3 can continue to rotate.

Claims (9)

  1. Electric tool, in particular a hammer drill which can be actuated manually,
    - having a drive motor (2),
    - having a tool spindle (3) for rotatably driving a tool,
    - having a rotary drive gear mechanism (4) for coupling the drive motor (2) to the tool spindle (3),
    - having a striking mechanism (5) for the hammering driving of the tool,
    - having a striking mechanism gear mechanism (6) for coupling the drive motor (2) to the striking mechanism (5),
    - having a switching device (7) for activating and deactivating the striking mechanism (5),
    - wherein the switching device (7) has a coupling (9) which is incorporated in a force path (10) of the striking mechanism gear mechanism (6) and which has an actuation stroke (11) for retracting and deploying the coupling (9),
    - wherein the actuation stroke (11) extends transversely relative to the rotation axis (8) of the tool spindle (3) and/or parallel with a rotation axis (37) of an actuation element (28) of the switching device (7), which element can be rotated manually in order to deploy and retract the coupling (9), wherein the striking mechanism gear mechanism (6) has an input-side toothed drive wheel (13) which is rotatably supported about a rotation axis (17),
    characterised in
    - that the striking mechanism gear mechanism (6) has an output-side crank gear wheel (14) which is rotatably supported about the rotation axis (17) of the toothed drive wheel (13) and which, when the striking mechanism (5) is activated, drives a connecting rod (20) of the striking mechanism (5),
    - that the coupling (9) in the striking mechanism gear mechanism (6) has a coupling ring (12) which is arranged coaxially with respect to the rotation axis (17) of the toothed drive wheel (13) on the crank gear wheel (14) and which is arranged on the crank gear wheel (14) in an axially adjustable and rotationally secure manner,
    - that the toothed drive wheel (13) has an axial carrier contour (24) at an axial side facing the crank gear wheel (14),
    - that the coupling ring (12) has at an axial side facing the toothed drive wheel (13) an axial carrier contour (25) which complements the carrier contour (24) of the toothed drive wheel (13) and which in the retracted state of the coupling ring (12) cooperates with the carrier contour (24) of the toothed drive wheel (13) in order to transmit torque and is axially released therefrom in the deployed state.
  2. Electric tool according to claim 1
    characterised in
    that the crank gear wheel (14) has at an axial portion (22) which is arranged coaxially with respect to the rotation axis (17) of the toothed drive wheel (13) radially at the outer side a carrier contour (23) which cooperates with a complementary internal carrier contour (56) of the coupling ring (12) so that the coupling ring (12) is arranged on the axial portion (22) of the crank gear wheel (14) in a rotationally secure and axially adjustable manner.
  3. Electric tool according to claim 1 or 2,
    characterised in
    that the crank gear wheel (14) has an outer polygonal profile (57) whilst the coupling ring (12) has a complementary inner polygonal profile (58), wherein the coupling ring (12) is arranged by means of these polygonal profiles (57, 58) in a rotationally secure and axially adjustable manner on the crank gear wheel (14).
  4. Electric tool according to any one of claims 1 to 3,
    characterised in
    - that the switching device (7) has an actuation device (27) for retracting and deploying the coupling (9), which couples the actuation element (28) which can be actuated manually with a coupling member (12) with adjustable stroke,
    - wherein in particular there may be provision for the actuation device (27) to have a stroke element (29) which is coupled by means of at least one arm portion (30) which extends parallel with the rotation axis (17) of the toothed drive wheel (13) to the coupling ring (12) so that a stroke adjustment of the stroke element (29) which is directed away from the toothed drive wheel (13) carries and deploys the coupling ring (12) parallel with the rotation axis (17) of the toothed drive wheel (13).
  5. Electric tool according to claim 4,
    characterised in
    - that the actuation device (27) has a stroke drive (36) which converts a manual rotary actuation of the actuation element (28) into a stroke adjustment of the stroke element (29),
    - wherein there may optionally be provision for the stroke drive (36) to cooperate with a ring portion (31) of the stroke element (29), which ring portion is axially parallel with the rotation axis (17) of the toothed drive wheel (13) and from which the respective arm portion (30) protrudes.
  6. Electric tool according to claim 5,
    characterised in
    - that the ring portion (31) has at least one sliding member (38) which protrudes radially inwards, wherein the stroke drive (36) has a sleeve (39) which can be rotated coaxially relative to the ring portion (31) and which has at the radially outer side at least one ramp (40) which rises axially in a peripheral direction and which cooperates with the sliding member (38) in order to convert a rotational adjustment of the sleeve (39) into a stroke adjustment of the stroke element (29),
    - wherein there may optionally be provision for there to be provided a plurality of sliding members (38) and the same number of ramps (40), which are arranged so as to be distributed in the peripheral direction,
    - wherein there may optionally be provision for the respective ramp (40) to have at the lower end thereof and/or at the upper end thereof a catch step (42) in which the respective sliding member (38) engages when the respective end position is reached.
  7. Electric tool according to claim 6,
    characterised in
    - that the actuation element (28) is connected to the sleeve (39) in a rotationally secure manner,
    - wherein there may optionally be provision for the actuation element (28) to be arranged on an outer side of a housing (41) of the hammer drill (1), whilst the sleeve (39) is arranged at an inner side of the housing (41).
  8. Electric tool at least according to claim 5,
    characterised in
    that the ring portion (31) is arranged coaxially with respect to the rotation axis (17) of the toothed drive wheel (13).
  9. Electric tool at least according to claim 1,
    characterised in
    that there is provided a retraction spring (50) which axially drives the coupling ring (12) against the toothed drive wheel (13).
EP10196699.2A 2010-01-20 2010-12-23 Electrical tool Not-in-force EP2347865B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010004961A DE102010004961A1 (en) 2010-01-20 2010-01-20 power tool

Publications (2)

Publication Number Publication Date
EP2347865A1 EP2347865A1 (en) 2011-07-27
EP2347865B1 true EP2347865B1 (en) 2017-10-04

Family

ID=43880980

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10196699.2A Not-in-force EP2347865B1 (en) 2010-01-20 2010-12-23 Electrical tool

Country Status (4)

Country Link
US (1) US8622148B2 (en)
EP (1) EP2347865B1 (en)
CN (1) CN102126198B (en)
DE (1) DE102010004961A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106797155B (en) * 2015-04-23 2018-04-06 美国轮轴制造公司 The drive system disconnected for power train
CN110177659B (en) * 2017-01-13 2022-10-18 株式会社牧田 Electric tool
CN108869563A (en) * 2018-08-22 2018-11-23 武义华丽电器制造有限公司 A kind of clutch structure of electric hammer
NL2021528B1 (en) * 2018-08-30 2020-04-30 Holmatro B V A tool having a pump and a pump

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3319934A1 (en) * 1982-06-02 1983-12-15 Black & Decker, Inc. (eine Gesellschaft n.d.Ges.d. Staates Delaware), 19711 Newark, Del. Percussion drilling machine
JPH0657567A (en) 1992-07-30 1994-03-01 Asahi Chem Ind Co Ltd Production of covered elastic yarn and apparatus therefor
JP2585072Y2 (en) * 1993-01-19 1998-11-11 リョービ株式会社 Switching mechanism of hammer drill
DE19716976A1 (en) * 1997-04-23 1998-10-29 Bosch Gmbh Robert Power tool
JP4281273B2 (en) * 2000-10-20 2009-06-17 日立工機株式会社 Hammer drill
DE10115119A1 (en) * 2001-03-27 2002-10-02 Hilti Ag Hand-held tool with switching device has gear wheels connected via two circlips
DE10261030A1 (en) * 2002-12-24 2004-07-08 Robert Bosch Gmbh Rotary Hammer
DE102004046627A1 (en) 2004-09-25 2006-03-30 Robert Bosch Gmbh Hand tool, in particular drill and / or percussion hammer
DE102004055236A1 (en) * 2004-11-16 2006-05-18 Robert Bosch Gmbh Hand tool machine e.g. hammer drill, for releasing of screw, has gear that stands in contact with connecting sleeve, where another connecting sleeve has external tooth that rotatably and continuously stands in contact with sprocket pinion
GB0428210D0 (en) * 2004-12-23 2005-01-26 Black & Decker Inc Mode change mechanism
EP1674207B1 (en) * 2004-12-23 2008-12-10 BLACK & DECKER INC. Power tool
US7469752B2 (en) * 2005-12-02 2008-12-30 Makita Corporation Power tool
JP4456559B2 (en) * 2005-12-02 2010-04-28 株式会社マキタ Work tools
DE102006035417B4 (en) * 2006-11-09 2016-12-01 Hilti Aktiengesellschaft Hand tool
JP2008183633A (en) * 2007-01-26 2008-08-14 Makita Corp Hammer drill
DE102007062248A1 (en) * 2007-12-21 2009-06-25 Robert Bosch Gmbh Hand tool with a, at least one rotatably mounted intermediate shaft comprehensive gear device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102010004961A1 (en) 2011-07-21
US20110174510A1 (en) 2011-07-21
US8622148B2 (en) 2014-01-07
CN102126198A (en) 2011-07-20
CN102126198B (en) 2015-05-13
EP2347865A1 (en) 2011-07-27

Similar Documents

Publication Publication Date Title
EP3478992B1 (en) Parking lock unit, and electric drive arrangement having a parking lock
DE102005037559B4 (en) Lockable differential
EP1578564B1 (en) Drill hammer
DE102007020826B4 (en) driving means
DE102010000970B4 (en) Height-adjustable actuating device
EP2318184B1 (en) Switchable gear in a hand-held power tool
EP2837466B1 (en) Clamping unit, in particular for use in a machining centre or a turning or milling center
CH697940B1 (en) Portable power tool, in particular a drilling and / or percussion hammer.
DE102011084499A1 (en) tool attachment
DE102009047543A1 (en) capper
EP2347865B1 (en) Electrical tool
EP3748200A1 (en) Differential lock
EP3456479B1 (en) Drive train assembly for a powered machine tool
DE102012214938B4 (en) Gear arrangement for a driven machine tool and machine tool with such a gear arrangement
EP2158998A2 (en) Tool revolver
EP1652631B1 (en) Motor driven power tool
DE102009034964B4 (en) Chuck for a hand machine tool
DE2313895C2 (en) Actuating device for valves
DE202006006273U1 (en) Screw driver for screwing and unscrewing screws in or from workpieces, has motor driven drive shaft and tool holder which is arranged at output shaft that is coaxial to drive shaft
EP2248958B1 (en) Sliding sunroof
EP1579939A1 (en) Tool
DE102006042458B4 (en) driving means
EP2314419B1 (en) Motor-driven tool device
DE202019103359U1 (en) Linear drive with coupling
EP3461594A1 (en) Actuator and gearbox assembly for a driven machine tool

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20120126

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170703

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 933559

Country of ref document: AT

Kind code of ref document: T

Effective date: 20171015

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010014218

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20171004

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180104

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180104

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180204

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180105

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010014218

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

26N No opposition filed

Effective date: 20180705

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171223

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180831

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20171231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171223

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180104

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 933559

Country of ref document: AT

Kind code of ref document: T

Effective date: 20171223

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171223

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20101223

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171004

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20211228

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502010014218

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230701