EP0755756A2 - Hand-hold drilling machine with device for switching between operating modes "drilling" and "percussive drilling" - Google Patents

Hand-hold drilling machine with device for switching between operating modes "drilling" and "percussive drilling" Download PDF

Info

Publication number
EP0755756A2
EP0755756A2 EP96109456A EP96109456A EP0755756A2 EP 0755756 A2 EP0755756 A2 EP 0755756A2 EP 96109456 A EP96109456 A EP 96109456A EP 96109456 A EP96109456 A EP 96109456A EP 0755756 A2 EP0755756 A2 EP 0755756A2
Authority
EP
European Patent Office
Prior art keywords
drilling
intermediate wall
impact drill
axial
spindle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96109456A
Other languages
German (de)
French (fr)
Other versions
EP0755756A3 (en
EP0755756B1 (en
Inventor
Günther Dipl.-Ing. Stark
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.)
Metabowerke GmbH and Co
Original Assignee
Metabowerke GmbH and Co
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 Metabowerke GmbH and Co filed Critical Metabowerke GmbH and Co
Publication of EP0755756A2 publication Critical patent/EP0755756A2/en
Publication of EP0755756A3 publication Critical patent/EP0755756A3/en
Application granted granted Critical
Publication of EP0755756B1 publication Critical patent/EP0755756B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • 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
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle

Definitions

  • the invention relates to an impact drill with an intermediate wall on the motor side, in particular only radial mounting of a drilling spindle, and with an adjusting member for axially adjusting the drilling spindle between an impact drilling operating position and a rotary drilling operating position and with an axial bearing supporting the drilling spindle in the rotary drilling operating position.
  • the drilling spindle executes axial movements in the hammer drilling operating position, which are generated by a hammer mechanism which is generally formed by indexing disks.
  • the one acting on the drilling spindle Axial force is transferred to the machine housing via the striking mechanism.
  • the hammer mechanism is switched off in rotary drilling mode and the drilling spindle performs a pure rotary movement. If the striking mechanism is formed by indexing disks, the axial movement is prevented by disengaging the indexing disks and holding them in this position, which is achieved by an axial displacement of the drilling spindle.
  • the axial force in the drilling spindle caused by the pressing of the drilling machine against the workpiece in the rotary drilling mode is then absorbed by an axial bearing mentioned above.
  • this axial bearing is formed by the end face of the drilling spindle being supported on a housing section, an intermediate wall or a similar component of the machine.
  • Generic impact drills of this type are described, for example, in DE 27 15 682 C3 and in EP 0 399 714 A2. With such an axial bearing of the drilling spindle in rotary drilling operation, however, high surface pressures and thus high temperatures occur due to the small contact surface, and a correspondingly high level of wear occurs.
  • Impact drills have also become known in which roller bearings are used as axial bearings for the drilling spindle.
  • the DT 23 28 462 A1 shows an impact drill in which the drilling spindle is supported with one shoulder on an axial roller bearing in rotary drilling operation.
  • This Axial roller bearing is in turn supported on a longitudinally displaceable bearing bush which radially supports the drilling spindle on the motor side and is in turn guided in a housing section.
  • a bolt running perpendicular to the drilling spindle which has a manually operated rotary knob and an eccentric cam.
  • the eccentric cam presses on the longitudinally displaceable bearing bush and pushes the drilling spindle forward so that the hammer mechanism is switched off.
  • the axial force flow goes from the spindle via the axial bearing, the bearing bush, the eccentric cam to the bolt and from there to the machine housing.
  • the eccentric cam and the bolt must therefore be designed for these loads, which is problematic and expensive.
  • the known impact drill has the problem that the rear spindle bearing is imprecise due to the axial displaceability of the bearing bush.
  • the front spindle bearing is designed as a shoulder bearing, one shoulder of which can be axially displaced by means of a manually operated adjusting ring in the front area of the machine housing.
  • This version requires many individual parts and is therefore complex and expensive. Furthermore, the axial force flow over these many individual parts, which increases wear and susceptibility to failure.
  • a hammer drill of the type described in the introduction in that the axial bearing is a roller bearing and the adjusting element acts on the drill spindle via this roller bearing and is provided between the intermediate wall and a drive wheel arranged on the drill spindle.
  • the invention therefore proposes to arrange a lifting device formed by the adjusting member and the axial roller bearing cooperating therewith between the motor-side intermediate wall and the gear wheel driving the drilling spindle.
  • a hammer drill designed in this way is distinguished by the advantages of using an axial roller bearing and by a relatively short axial force flow from the drilling spindle via the axial roller bearing and the like Adjusting member on the partition without going over the rear radial bearing of the drilling spindle, as is the case with the impact drill known from DE 23 28 462 A1, in which no partition according to the application is provided for the storage of the drilling spindle.
  • the intermediate wall can also be produced inexpensively as a stamped part made of sheet metal or as a sintered part.
  • the adjusting member or the intermediate wall has one component that extends in the axial direction and the other component facing projection, which cooperates with a recess in the other component.
  • the adjusting member can be formed by an adjusting lever which can be pivoted transversely to the drilling spindle, so that the projection can be brought into engagement with the recess or out of engagement with the recess by pivoting the lever and thus an axial displacement of the adjusting lever which can be transferred to the drilling spindle can be achieved.
  • a fixed locking disk is provided between the intermediate wall and the drive wheel arranged on the drilling spindle and is held by the intermediate wall.
  • the force shocks acting in the axial direction can be absorbed by the stable intermediate wall, which is preferably supported over a large part of its circumference on the machine housing.
  • the operative connection between the adjusting member and the drilling spindle could be designed in such a way that the axial bearing is supported on a shoulder or a collar of the drilling spindle; however, the axial roller bearing is preferably supported against the drive wheel seated on the drilling spindle, so that the adjusting element acts on the drive wheel via the axial roller bearing.
  • the axial roller bearing can be formed by this drive wheel, by rolling elements and a bearing shell adjacent to the adjusting element. It can also prove to be advantageous if a thrust washer is provided between the drive wheel and the adjusting element. In an advantageous embodiment of the invention, it is further provided that the adjusting member lies flat against the intermediate wall, so that no high surface pressure and thus no wear occurs when the force acting in the axial direction is transmitted.
  • FIG. 1 shows an impact drill marked overall with reference number 2, the part of the impact drill not affected by the invention being omitted.
  • the hammer drill 2 comprises a drill spindle 4, the is supported radially at its rear end by an intermediate wall 6 inserted in two housing shells by a needle bearing 8. In the front area of the drilling machine, the spindle 4 is additionally supported radially by a deep groove ball bearing 10.
  • a radial ball bearing 12 is also held in the intermediate wall 6, through which an armature shaft 14 is guided and supported.
  • the armature shaft 14 extends through the intermediate wall 6 and has at its front end a pinion 16 which meshes with a drive wheel 18 which is seated on the drilling spindle 4 and is fixed in terms of rotation.
  • An impact mechanism 20 of the impact drill 2 is accommodated between the intermediate wall 6 and the drive wheel 18.
  • the striking mechanism 20 comprises a fixed locking disk 22 which is supported against the intermediate wall 6 and is held thereon.
  • the detent disk 22 has on its end face facing the drive wheel 18 detent teeth 24 which, in percussion drilling operation of the machine, cooperate with detent teeth 26 on the end face of the drive wheel 18 in a manner known per se.
  • adjusting member 30 in the Form of a pivotable in a plane perpendicular to the drilling spindle 4 adjusting lever 32 housed.
  • the adjusting lever 32 has a projection 34 which faces the intermediate wall 6 and which can be latched into a recess 36 formed in the intermediate wall 6.
  • the impact drill 2 is in the impact drilling operating position, in which the ratchet teeth 24 and 26 are engaged. If the adjusting lever 32 is pivoted into a second position perpendicular to the plane of the drawing in FIGS. 1 and 2, the projection 34 slides out of the recess 36 and thereby displaces the adjusting lever 32 to the front.
  • the adjusting lever 32 presses on a thrust washer 38.
  • the thrust washer 38 forms the rear bearing shell 40 of an axial roller bearing 42.
  • the axial roller bearing 42 is formed in the illustrated case by the thrust washer 38, by spherical rolling elements 44 and by the drive wheel 18 forming a front bearing shell.
  • the axial offset of the adjusting lever 32 when pivoting from the percussion drilling operating position into the rotary drilling operating position is thus transmitted directly via the axial roller bearing 42 to the drive wheel 18 and thus to the drilling spindle 4, whereby this is also shifted forward and the locking teeth 24 of the locking disk 22 and the locking teeth 26 of the drive wheel 18 are disengaged.
  • the axial load occurring during drilling operation from the drilling spindle 4 or the drive wheel 18 is via the Axial roller bearing 42, transmitted to the intermediate wall 6 via the adjusting lever 32.
  • a spring 46 is arranged between the adjusting lever 32 and the thrust roller bearing 42, which presses the adjusting lever 32 into the recess 36 in the intermediate wall 6, but also presses the drive wheel 18 and thus the drilling spindle 4 forward in the percussion drilling operating position in such a way that the ratchet teeth 24 and 26 remain out of engagement until the drill spindle is pressed against a workpiece.
  • FIGS. 3 and 5 show a section running perpendicular to the longitudinal axis of the drilling spindle 4 and through the axial roller bearing 42.
  • the impact drill is in the impact drilling operating position; the projections 34 of the adjusting lever 32 are snapped into the recesses 34 in the intermediate wall 6, and the arrangement of adjusting lever 32, axial roller bearing 42 and drive wheel 18 or drilling spindle 4 is in the lower position shown in FIG. 1.
  • the locking disk 22 which can be seen in FIGS. 3 and 5 is shown as an individual part in FIG. It has two feet 48 with which it is centered and held in recesses in the intermediate wall 6. In this case, the catch disk 22 is supported with its surface 50 on the intermediate wall 6 from.
  • the ratchet teeth 24 are located on the opposite side.
  • FIG. 5 shows the adjusting lever 32 in its other swivel position, in which the drilling machine is in the rotary drilling operating position.
  • the projections 34 of the adjusting lever 32 facing the intermediate wall 6 are out of engagement with the recesses 36 of the intermediate wall 6, and the adjusting lever 32 is in the upper position in FIG. 1 and presses the drive wheel 18 and thus the drilling spindle via the axial roller bearing 42 4 forward.
  • the axial load occurring is transmitted via the axial roller bearing 42 to the adjusting lever 32 and from there via the three projections 34 to the intermediate wall 6.
  • FIG. 6 shows a further embodiment of the impact drill according to the invention, which differs from the previously described embodiment in that an intermediate wall 6 'and a detent disk 22' are designed as a one-piece component.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

The electric hammer drill has an axially displaceable drilling spindle (4) supported by an axial roller bearing (42). The adjustment member (30) acts on the spindle through the bearing and is mounted between the partition wall (6) on the engine side and a drive wheel (18) set on the spindle. The adjustment member interacts directly with the partition and either the adjustment member or partition has an axially extended projection (34) facing the relevant other part which interacts with an indentation (36) in the other part.

Description

Die Erfindung betrifft eine Schlagbohrmaschine mit einer motorseitigen Zwischenwand, insbesondere nur radialen Lagerung einer Bohrspindel, und mit einem Verstellorgan zum axialen Verstellen der Bohrspindel zwischen einer Schlagbohrbetriebsstellung und einer Drehbohrbetriebsstellung und mit einem die Bohrspindel in der Drehbohrbetriebsstellung abstützenden Axiallager.The invention relates to an impact drill with an intermediate wall on the motor side, in particular only radial mounting of a drilling spindle, and with an adjusting member for axially adjusting the drilling spindle between an impact drilling operating position and a rotary drilling operating position and with an axial bearing supporting the drilling spindle in the rotary drilling operating position.

Bei Schlagbohrmaschinen führt die Bohrspindel in der Schlagbohrbetriebsstellung Axialbewegungen aus, welche durch ein in der Regel von Rastenscheiben gebildetes Schlagwerk erzeugt werden. Die dabei auf die Bohrspindel einwirkende Axialkraft wird über das Schlagwerk auf das Maschinengehäuse übertragen. Im Drehbohrbetrieb ist das Schlagwerk ausgeschaltet und die Bohrspindel führt eine reine Drehbewegung aus. Ist das Schlagwerk von Rastenscheiben gebildet, so wird die Axialbewegung dadurch unterbunden, daß die Rastenscheiben außer Eingriff gebracht und in dieser Stellung gehalten werden, was durch eine axiale Verschiebung der Bohrspindel erreicht wird. Die durch das Andrücken der Bohrmaschine an das Werkstück im Drehbohrbetrieb hervorgerufene Axialkraft in der Bohrspindel wird dann durch ein vorstehend erwähntes Axiallager aufgenommen. Dieses Axiallager ist im einfachsten Fall dadurch gebildet, daß sich die Stirnfläche der Bohrspindel an einem Gehäuseabschnitt, einer Zwischenwand oder einem ähnlichen Bauteil der Maschine abstützt. Derartige gattungsbildende Schlagbohrmaschinen sind bspw. in der DE 27 15 682 C3 und in der EP 0 399 714 A2 beschrieben. Bei einer derartigen Axiallagerung der Bohrspindel im Drehbohrbetrieb treten jedoch aufgrund der geringen Anlagefläche hohe Flächenpressungen und damit hohe Temperaturen auf, und es entsteht ein dementsprechend hoher Verschleiß.In hammer drills, the drilling spindle executes axial movements in the hammer drilling operating position, which are generated by a hammer mechanism which is generally formed by indexing disks. The one acting on the drilling spindle Axial force is transferred to the machine housing via the striking mechanism. The hammer mechanism is switched off in rotary drilling mode and the drilling spindle performs a pure rotary movement. If the striking mechanism is formed by indexing disks, the axial movement is prevented by disengaging the indexing disks and holding them in this position, which is achieved by an axial displacement of the drilling spindle. The axial force in the drilling spindle caused by the pressing of the drilling machine against the workpiece in the rotary drilling mode is then absorbed by an axial bearing mentioned above. In the simplest case, this axial bearing is formed by the end face of the drilling spindle being supported on a housing section, an intermediate wall or a similar component of the machine. Generic impact drills of this type are described, for example, in DE 27 15 682 C3 and in EP 0 399 714 A2. With such an axial bearing of the drilling spindle in rotary drilling operation, however, high surface pressures and thus high temperatures occur due to the small contact surface, and a correspondingly high level of wear occurs.

Es sind auch Schlagbohrmaschinen bekannt geworden, bei denen Wälzlager als Axiallager für die Bohrspindel eingesetzt werden. Die DT 23 28 462 A1 zeigt eine Schlagbohrmaschine, bei der sich die Bohrspindel im Drehbohrbetrieb mit einer Schulter an einem Axialwälzlager abstützt. Dieses Axialwälzlager ist seinerseits an einer längsverschiebbaren Lagerbuchse abgestützt, welche die Bohrspindel motorseitig radial lagert und ihrerseits in einem Gehäuseabschnitt geführt ist. Auf der von dem Axialwälzlager abgewandten Seite der längsverschiebbaren Lagerbuchse ist ein senkrecht zur Bohrspindel verlaufender Bolzen angeordnet, der einen manuell bedienbaren Drehknopf sowie einen Exzenternocken aufweist. Wird die Schlagbohrmaschine durch Drehen des Drehknopfes in die Drehbohrbetriebsstellung gebracht, drückt der Exzenternocken auf die längsverschiebbare Lagerbuchse und schiebt die Bohrspindel nach vorn, so daS das Schlagwerk abgeschaltet wird. In dieser Drehbohrbetriebsstellung geht der Axialkraftfluß von der Spindel über das Axiallager, die Lagerbuchse, den Exzenternocken auf den Bolzen und von dort auf das Maschinengehäuse. Der Exzenternocken und der Bolzen müssen also für diese Belastungen ausgelegt werden, was jedoch problematisch und teuer ist. Desweiteren weist die bekannte Schlagbohrmaschine das Problem auf, daß die hintere Spindellagerung infolge der axialen Verschiebbarkeit der Lagerbuchse ungenau ist.Impact drills have also become known in which roller bearings are used as axial bearings for the drilling spindle. The DT 23 28 462 A1 shows an impact drill in which the drilling spindle is supported with one shoulder on an axial roller bearing in rotary drilling operation. This Axial roller bearing is in turn supported on a longitudinally displaceable bearing bush which radially supports the drilling spindle on the motor side and is in turn guided in a housing section. On the side of the longitudinally displaceable bearing bush facing away from the axial roller bearing is arranged a bolt running perpendicular to the drilling spindle, which has a manually operated rotary knob and an eccentric cam. If the hammer drill is brought into the rotary drilling operating position by turning the rotary knob, the eccentric cam presses on the longitudinally displaceable bearing bush and pushes the drilling spindle forward so that the hammer mechanism is switched off. In this rotary drilling operating position, the axial force flow goes from the spindle via the axial bearing, the bearing bush, the eccentric cam to the bolt and from there to the machine housing. The eccentric cam and the bolt must therefore be designed for these loads, which is problematic and expensive. Furthermore, the known impact drill has the problem that the rear spindle bearing is imprecise due to the axial displaceability of the bearing bush.

Eine weitere Schlagbohrmaschine ist aus der G 83 19 187 U1 bekannt. Bei dieser Schlagbohrmaschine ist das vordere Spindellager als Schulterlager ausgeführt, dessen eine Schulter mittels eines manuell bedienbaren Verstellrings im vorderen Bereich des Maschinengehäuses axial verschoben werden kann. Diese Ausführung erfordert viele Einzelteile und ist deshalb aufwendig und teuer. Desweiteren geht der Axialkraftfluß über diese vielen Einzelteile, was den Verschleiß und die Störanfälligkeit erhöht.Another impact drill is known from the G 83 19 187 U1. In this hammer drill, the front spindle bearing is designed as a shoulder bearing, one shoulder of which can be axially displaced by means of a manually operated adjusting ring in the front area of the machine housing. This version requires many individual parts and is therefore complex and expensive. Furthermore, the axial force flow over these many individual parts, which increases wear and susceptibility to failure.

Es ist eine Aufgabe der vorliegenden Erfindung, eine Schlagbohrmaschine der eingangs beschriebenen Art zu schaffen, bei der die Nachteile einer Axiallagerung durch bloßes Abstützen der Stirnfläche der Bohrspindel vermieden werden, bei der jedoch die Nachteile von bekannten mit Axialwälzlagern arbeitenden Schlagbohrmaschinen nicht übernommen werden.It is an object of the present invention to provide an impact drill of the type described in the opening paragraph in which the disadvantages of an axial bearing are avoided by merely supporting the end face of the drilling spindle, but in which the disadvantages of known impact drilling machines working with axial roller bearings are not adopted.

Diese Aufgabe wird bei einer Schlagbohrmaschine der eingangs beschriebenen Art erfindungsgemäß dadurch gelöst, daß das Axiallager ein Wälzlager ist und das Verstellorgan über dieses Wälzlager auf die Bohrspindel einwirkt und zwischen der Zwischenwand und einem auf der Bohrspindel angeordneten Antriebsrad vorgesehen ist.This object is achieved according to the invention in a hammer drill of the type described in the introduction in that the axial bearing is a roller bearing and the adjusting element acts on the drill spindle via this roller bearing and is provided between the intermediate wall and a drive wheel arranged on the drill spindle.

Die Erfindung schlägt also vor, eine von dem Verstellorgan gebildete Hubvorrichtung sowie das damit zusammenwirkende Axialwälzlager zwischen der motorseitigen Zwischenwand und dem die Bohrspindel antreibenden Getrieberad anzuordnen. Eine derart ausgebildete Schlagbohrmaschine zeichnet sich durch die Vorteile der Verwendung einer Axialwälzlagerung und durch einen verhältnismäßig kurzen axialen Kraftfluß von der Bohrspindel über das Axialwälzlager und das Verstellorgan auf die Zwischenwand aus, ohne über die hintere Radiallagerung der Bohrspindel zu gehen, wie dies bei der aus der DE 23 28 462 A1 bekannten Schlagbohrmaschine der Fall ist, bei der keine anmeldungsgemäße Zwischenwand für die Lagerung der Bohrspindel vorgesehen ist.The invention therefore proposes to arrange a lifting device formed by the adjusting member and the axial roller bearing cooperating therewith between the motor-side intermediate wall and the gear wheel driving the drilling spindle. A hammer drill designed in this way is distinguished by the advantages of using an axial roller bearing and by a relatively short axial force flow from the drilling spindle via the axial roller bearing and the like Adjusting member on the partition without going over the rear radial bearing of the drilling spindle, as is the case with the impact drill known from DE 23 28 462 A1, in which no partition according to the application is provided for the storage of the drilling spindle.

Durch den Einsatz eines Axialwälzlagers werden die Axialkräfte besser verteilt; es entstehen keine hohen punktuellen Flächenpressungen wie beim Abstützen der Stirnfläche der Bohrspindel, was sich durch eine erhöhte Lebensdauer als vorteilhaft erweist. Die Verwendung der Zwischenwand zur Ableitung der Axialkräfte stellt eine technisch einwandfreie und vorteilhafte Lösung dar, die Axialkräfte gleichmäßig auf das Maschinengehäuse zu übertragen. Die Zwischenwand ist als Stanzteil aus Blech oder als Sinterteil zudem preiswert herstellbar.By using an axial roller bearing, the axial forces are better distributed; there are no high punctiform surface pressures as when supporting the end face of the drilling spindle, which has proven to be advantageous due to the increased service life. The use of the partition for deriving the axial forces represents a technically flawless and advantageous solution to transmit the axial forces evenly to the machine housing. The intermediate wall can also be produced inexpensively as a stamped part made of sheet metal or as a sintered part.

Es wird vorgeschlagen, die Schlagbohrmaschine so auszubilden, daß das Verstellorgan direkt mit der Zwischenwand zusammenwirkt, so daß der Weg des axialen Kraftflusses nur wenige Bauteile erfaßt und die Axialkraft von der Zwischenwand und damit von dem Maschinengehäuse aufgenommen werden kann.It is proposed to design the hammer drill so that the adjusting element cooperates directly with the intermediate wall, so that the path of the axial force flow detects only a few components and the axial force can be absorbed by the intermediate wall and thus by the machine housing.

Bei einer bevorzugten Ausführungsform der Erfindung weist das Verstellorgan oder die Zwischenwand einen in axialer Richtung erstreckten und dem jeweils anderen Bauteil zugewandten Vorsprung auf, der mit einer Vertiefung in dem anderen Bauteil zusammenwirkt. Solchenfalls kann das Verstellorgan von einem quer zur Bohrspindel verschwenkbaren Verstellhebel gebildet sein, so daß durch Verschwenken des Hebels der Vorsprung in Eingriff mit der Vertiefung oder außer Eingriff mit der Vertiefung gebracht und damit eine axiale, auf die Bohrspindel übertragbare Versetzung des Verstellhebels erreicht werden kann.In a preferred embodiment of the invention, the adjusting member or the intermediate wall has one component that extends in the axial direction and the other component facing projection, which cooperates with a recess in the other component. In such a case, the adjusting member can be formed by an adjusting lever which can be pivoted transversely to the drilling spindle, so that the projection can be brought into engagement with the recess or out of engagement with the recess by pivoting the lever and thus an axial displacement of the adjusting lever which can be transferred to the drilling spindle can be achieved.

Bei einer weiteren vorteilhaften Ausführungsform der Schlagbohrmaschine ist eine feststehende Rastenscheibe zwischen der Zwischenwand und dem auf der Bohrspindel angeordneten Antriebsrad vorgesehen und von der Zwischenwand gehalten. Bei dieser Ausführungsform können die in axialer Richtung wirkenden Kraftstöße von der stabilen, vorzugsweise über einen großen Teil ihres Umfangs an dem Maschinengehäuse gelagerten Zwischenwand aufgenommen werden. In Weiterbildung dieses Erfindungsgedankens wird vorgeschlagen, die feststehende Rastenscheibe und die Zwischenwand einstückig auszubilden.In a further advantageous embodiment of the impact drill, a fixed locking disk is provided between the intermediate wall and the drive wheel arranged on the drilling spindle and is held by the intermediate wall. In this embodiment, the force shocks acting in the axial direction can be absorbed by the stable intermediate wall, which is preferably supported over a large part of its circumference on the machine housing. In a development of this inventive idea, it is proposed to form the fixed locking disk and the intermediate wall in one piece.

Die Wirkverbindung zwischen dem Verstellorgan und der Bohrspindel könnte so ausgestaltet sein, daß das Axiallager an einer Schulter oder einem Bund der Bohrspindel abgestützt ist; bevorzugtermaßen stützt sich das Axialwälzlager jedoch gegen das auf der Bohrspindel sitzende Antriebsrad ab, so daß das Verstellorgan über das Axialwälzlager auf das Antriebsrad einwirkt.The operative connection between the adjusting member and the drilling spindle could be designed in such a way that the axial bearing is supported on a shoulder or a collar of the drilling spindle; however, the axial roller bearing is preferably supported against the drive wheel seated on the drilling spindle, so that the adjusting element acts on the drive wheel via the axial roller bearing.

Bei dieser Ausführungsform kann das Axialwälzlager von diesem Antriebsrad, von Wälzkörpern und einer an das Verstellorgan angrenzenden Lagerschale gebildet sein. Es kann sich auch als vorteilhaft erweisen, wenn zwischen dem Antriebsrad und dem Verstellorgan eine Anlaufscheibe vorgesehen ist. Bei einer vorteilhaften Ausführungsform der Erfindung ist ferner vorgesehen, daß das Verstellorgan flächig gegen die Zwischenwand anliegt, so daß bei der Übertragung der in axialer Richtung wirkenden Kraft keine hohe Flächenpressung und damit kein Verschleiß auftritt.In this embodiment, the axial roller bearing can be formed by this drive wheel, by rolling elements and a bearing shell adjacent to the adjusting element. It can also prove to be advantageous if a thrust washer is provided between the drive wheel and the adjusting element. In an advantageous embodiment of the invention, it is further provided that the adjusting member lies flat against the intermediate wall, so that no high surface pressure and thus no wear occurs when the force acting in the axial direction is transmitted.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung ergeben sich aus der beigefügten zeichnerischen Darstellung und der nachfolgenden Beschreibung einer bevorzugten Ausführungsform der erfindungsgemäßen Schlagbohrmaschine. In der Zeichnung zeigt:

Figur 1
eine geschnittene Teilansicht einer erfindungsgemäßen Schlagbohrmaschine, wobei die obere Hälfte der Spindel in der "Drehbohrstellung" und die untere Hälfte in der "Schlagbohrstellung" gezeigt ist;
Figur 2
eine ausschnittsweise Darstellung der Schlagbohrmaschine nach Figur 1 von einer Zwischenwand bis zu einem Antriebsrad der Bohrspindel;
Figur 3
eine Schnittansicht gesehen in Richtung der Pfeile III-III in Figur 1, wobei sich die Schlagbohrmaschine in der Schlagbohrbetriebsstellung befindet;
Figur 4
eine Rastenscheibe der Schlagbohrmaschine nach Figur 1;
Figur 5
eine der Figur 3 entsprechende Schnittansicht, wobei sich die Schlagbohrmaschine in der Drehbohrbetriebsstellung befindet; und
Figur 6
eine weitere Ausführungsform, bei der eine Zwischenwand und die Rastenscheibe einstückig ausgebildet sind.
Further features, details and advantages of the invention result from the attached drawing and the following description of a preferred embodiment of the impact drill according to the invention. The drawing shows:
Figure 1
a partial sectional view of an impact drill according to the invention, the upper half of the spindle being shown in the "rotary drilling position" and the lower half in the "impact drilling position";
Figure 2
a partial representation of the impact drill according to Figure 1 from an intermediate wall to a drive wheel of the drilling spindle;
Figure 3
a sectional view seen in the direction of arrows III-III in Figure 1, wherein the hammer drill is in the hammer drilling operating position;
Figure 4
a locking disc of the impact drill according to Figure 1;
Figure 5
a sectional view corresponding to Figure 3, wherein the impact drill is in the rotary drilling operating position; and
Figure 6
a further embodiment in which an intermediate wall and the locking disk are integrally formed.

Figur 1 zeigt eine insgesamt mit dem Bezugszeichen 2 bezeichnete Schlagbohrmaschine, wobei der von der Erfindung nicht betroffene Teil der Schlagbohrmaschine weggelassen ist. Die Schlagbohrmaschine 2 umfaßt eine Bohrspindel 4, die an ihrem hinteren Ende von einer in zwei Gehäuseschalen eingesetzten Zwischenwand 6 durch ein Nadellager 8 radial gelagert ist. Im vorderen Bereich der Bohrmaschine ist die Spindel 4 zusätzlich durch ein Rillenkugellager 10 radial gelagert.FIG. 1 shows an impact drill marked overall with reference number 2, the part of the impact drill not affected by the invention being omitted. The hammer drill 2 comprises a drill spindle 4, the is supported radially at its rear end by an intermediate wall 6 inserted in two housing shells by a needle bearing 8. In the front area of the drilling machine, the spindle 4 is additionally supported radially by a deep groove ball bearing 10.

Wie sich auch aus der Figur 2 ersehen läßt, ist in der Zwischenwand 6 desweiteren ein Radialkugellager 12 gehalten, durch welches eine Ankerwelle 14 geführt und gelagert ist. Die Ankerwelle 14 erstreckt sich durch die Zwischenwand 6 hindurch und weist an ihrem vorderen Ende ein Ritzel 16 auf, welches mit einem drehfest auf der Bohrspindel 4 sitzenden, von einem Stirnrad gebildeten Antriebsrad 18 kämmt.As can also be seen from FIG. 2, a radial ball bearing 12 is also held in the intermediate wall 6, through which an armature shaft 14 is guided and supported. The armature shaft 14 extends through the intermediate wall 6 and has at its front end a pinion 16 which meshes with a drive wheel 18 which is seated on the drilling spindle 4 and is fixed in terms of rotation.

Zwischen der Zwischenwand 6 und dem Antriebsrad 18 ist ein Schlagwerk 20 der Schlagbohrmaschine 2 untergebracht. Das Schlagwerk 20 umfaßt eine feststehende Rastenscheibe 22, die sich gegen die Zwischenwand 6 abstützt und an dieser gehalten ist. Die Rastenscheibe 22 weist an ihrer dem Antriebsrad 18 zugewandten Stirnseite Rastenzähne 24 auf, die im Schlagbohrbetrieb der Maschine mit Rastenzähnen 26 an der Stirnseite des Antriebsrads 18 in an sich bekannter Weise zusammenwirken.An impact mechanism 20 of the impact drill 2 is accommodated between the intermediate wall 6 and the drive wheel 18. The striking mechanism 20 comprises a fixed locking disk 22 which is supported against the intermediate wall 6 and is held thereon. The detent disk 22 has on its end face facing the drive wheel 18 detent teeth 24 which, in percussion drilling operation of the machine, cooperate with detent teeth 26 on the end face of the drive wheel 18 in a manner known per se.

In dem Bereich zwischen der Zwischenwand 6 und dem Antriebsrad 18 ist desweiteren ein Verstellorgan 30 in der Form eines in einer senkrecht zur Bohrspindel 4 verlaufenden Ebene schwenkbaren Verstellhebels 32 untergebracht. Der Verstellhebel 32 weist einen der Zwischenwand 6 zugewandten Vorsprung 34 auf, der in eine in der Zwischenwand 6 ausgebildete Vertiefung 36 einrastbar ist. In diesem eingerasteten Zustand befindet sich die Schlagbohrmaschine 2 in der Schlagbohrbetriebsstellung, bei der die Rastenzähne 24 und 26 in Eingriff sind. Wird der Verstellhebel 32 senkrecht zur Zeichnungsebene der Figuren 1 und 2 in eine zweite Stellung verschwenkt, so gleitet der Vorsprung 34 aus der Vertiefung 36 heraus und versetzt dadurch den Verstellhebel 32 nach vorn. Der Verstellhebel 32 drückt dabei auf eine Anlaufscheibe 38. Die Anlaufscheibe 38 bildet die hintere Lagerschale 40 eines Axialwälzlagers 42. Das Axialwälzlager 42 ist in dem dargestellten Fall von der Anlaufscheibe 38, von kugelförmigen Wälzkörpern 44 und von dem eine vordere Lagerschale bildenden Antriebsrad 18 gebildet. Der axiale Versatz des Verstellhebels 32 bei Verschwenkung aus der Schlagbohrbetriebsstellung in die Drehbohrbetriebsstellung wird also direkt über das Axialwälzlager 42 auf das Antriebsrad 18 und somit auf die Bohrspindel 4 übertragen, wodurch diese ebenfalls nach vorn verschoben wird und die Rastenzähne 24 der Rastenscheibe 22 und die Rastenzähne 26 des Antriebsrads 18 außer Eingriff gebracht werden. In dieser Drehbohrbetriebsstellung wird die beim Bohrbetrieb auftretende axiale Belastung von der Bohrspindel 4 bzw. dem Antriebsrad 18 über das Axialwälzlager 42, über den Verstellhebel 32 auf die Zwischenwand 6 übertragen. Desweiteren ist eine Feder 46 zwischen dem Verstellhebel 32 und dem Axialwälzlager 42 angeordnet, welche den Verstellhebel 32 in die Vertiefung 36 in der Zwischenwand 6 drückt, aber auch das Antriebsrad 18 und damit die Bohrspindel 4 in der Schlagbohrbetriebsstellung derart nach vorn drückt, daß die Rastenzähne 24 und 26 so lange außer Eingriff bleiben bis die Bohrspindel gegen ein Werkstück gedrückt wird.In the area between the intermediate wall 6 and the drive wheel 18 there is also an adjusting member 30 in the Form of a pivotable in a plane perpendicular to the drilling spindle 4 adjusting lever 32 housed. The adjusting lever 32 has a projection 34 which faces the intermediate wall 6 and which can be latched into a recess 36 formed in the intermediate wall 6. In this locked state, the impact drill 2 is in the impact drilling operating position, in which the ratchet teeth 24 and 26 are engaged. If the adjusting lever 32 is pivoted into a second position perpendicular to the plane of the drawing in FIGS. 1 and 2, the projection 34 slides out of the recess 36 and thereby displaces the adjusting lever 32 to the front. The adjusting lever 32 presses on a thrust washer 38. The thrust washer 38 forms the rear bearing shell 40 of an axial roller bearing 42. The axial roller bearing 42 is formed in the illustrated case by the thrust washer 38, by spherical rolling elements 44 and by the drive wheel 18 forming a front bearing shell. The axial offset of the adjusting lever 32 when pivoting from the percussion drilling operating position into the rotary drilling operating position is thus transmitted directly via the axial roller bearing 42 to the drive wheel 18 and thus to the drilling spindle 4, whereby this is also shifted forward and the locking teeth 24 of the locking disk 22 and the locking teeth 26 of the drive wheel 18 are disengaged. In this rotary drilling operating position, the axial load occurring during drilling operation from the drilling spindle 4 or the drive wheel 18 is via the Axial roller bearing 42, transmitted to the intermediate wall 6 via the adjusting lever 32. Furthermore, a spring 46 is arranged between the adjusting lever 32 and the thrust roller bearing 42, which presses the adjusting lever 32 into the recess 36 in the intermediate wall 6, but also presses the drive wheel 18 and thus the drilling spindle 4 forward in the percussion drilling operating position in such a way that the ratchet teeth 24 and 26 remain out of engagement until the drill spindle is pressed against a workpiece.

Die Figuren 3 und 5 zeigen eine senkrecht zur Längsachse der Bohrspindel 4 und durch das Axialwälzlager 42 hindurch verlaufenden Schnitt. In der Darstellung nach Figur 3 befindet sich die Schlagbohrmaschine in der Schlagbohrbetriebsstellung; die Vorsprünge 34 des Verstellhebels 32 sind in die Vertiefungen 34 in der Zwischenwand 6 eingerastet, und die Anordnung aus Verstellhebel 32, Axialwälzlager 42 und Antriebsrad 18 bzw. Bohrspindel 4 befindet sich in der in Figur 1 dargestellten unteren Position.FIGS. 3 and 5 show a section running perpendicular to the longitudinal axis of the drilling spindle 4 and through the axial roller bearing 42. In the illustration according to FIG. 3, the impact drill is in the impact drilling operating position; the projections 34 of the adjusting lever 32 are snapped into the recesses 34 in the intermediate wall 6, and the arrangement of adjusting lever 32, axial roller bearing 42 and drive wheel 18 or drilling spindle 4 is in the lower position shown in FIG. 1.

Die in den Figuren 3 und 5 erkennbare Rastenscheibe 22 ist in der Figur 4 als Einzelteil dargestellt. Sie weist zwei Füße 48 auf, mit denen sie in Aussparungen der Zwischenwand 6 zentriert und gehalten ist. Dabei stützt sich die Rastenscheibe 22 mit ihrer Fläche 50 an der Zwischenwand 6 ab. An der gegenüberliegenden Seite befinden sich die Rastenzähne 24.The locking disk 22 which can be seen in FIGS. 3 and 5 is shown as an individual part in FIG. It has two feet 48 with which it is centered and held in recesses in the intermediate wall 6. In this case, the catch disk 22 is supported with its surface 50 on the intermediate wall 6 from. The ratchet teeth 24 are located on the opposite side.

Figur 5 zeigt den Verstellhebel 32 in seiner anderen Schwenkstellung, in der sich die Bohrmaschine in der Drehbohrbetriebsstellung befindet. In dieser Stellung sind die der Zwischenwand 6 zugewandten Vorsprünge 34 des Verstellhebels 32 außer Eingriff mit den Vertiefungen 36 der Zwischenwand 6, und der Verstellhebel 32 ist in der in der Figur 1 oberen Stellung und drückt über das Axialwälzlager 42 das Antriebsrad 18 und damit die Bohrspindel 4 nach vorn. Wenn die Bohrspindel 4 gegen ein Werkstück gedrückt wird, wird die dabei auftretende axiale Belastung über das Axialwälzlager 42 auf den Verstellhebel 32 und von dort über die drei Vorsprünge 34 an die Zwischenwand 6 übertragen.FIG. 5 shows the adjusting lever 32 in its other swivel position, in which the drilling machine is in the rotary drilling operating position. In this position, the projections 34 of the adjusting lever 32 facing the intermediate wall 6 are out of engagement with the recesses 36 of the intermediate wall 6, and the adjusting lever 32 is in the upper position in FIG. 1 and presses the drive wheel 18 and thus the drilling spindle via the axial roller bearing 42 4 forward. When the drilling spindle 4 is pressed against a workpiece, the axial load occurring is transmitted via the axial roller bearing 42 to the adjusting lever 32 and from there via the three projections 34 to the intermediate wall 6.

Schließlich zeigt die Figur 6 eine weitere Ausführungsform der erfindungsgemäßen Schlagbohrmaschine, die sich von der vorausgehend beschriebenen Ausführungsform dadurch unterscheidet, daß eine Zwischenwand 6' und eine Rastenscheibe 22' als einstückiges Bauteil ausgeführt sind.Finally, FIG. 6 shows a further embodiment of the impact drill according to the invention, which differs from the previously described embodiment in that an intermediate wall 6 'and a detent disk 22' are designed as a one-piece component.

Claims (10)

Schlagbohrmaschine mit einer motorseitigen Zwischenwand, insbesondere nur radialen Lagerung einer Bohrspindel, und mit einem Verstellorgan zum axialen Verstellen der Bohrspindel zwischen einer Schlagbohrbetriebsstellung und einer Drehbohrbetriebsstellung und mit einem die Bohrspindel in der Drehbohrbetriebsstellung abstützenden Axiallager, dadurch gekennzeichnet, daß das Axiallager ein Wälzlager (42) ist und das Verstellorgan (30) über dieses Wälzlager (42) auf die Bohrspindel (4) einwirkt und zwischen der Zwischenwand (6) und einem auf der Bohrspindel (4) angeordneten Antriebsrad (18) vorgesehen ist.Impact drill with an intermediate wall on the motor side, in particular only radial mounting of a drilling spindle, and with an adjusting member for axially adjusting the drilling spindle between an impact drilling operating position and a rotary drilling operating position and with an axial bearing supporting the drilling spindle in the rotary drilling operating position, characterized in that the axial bearing is a roller bearing (42) and the adjusting element (30) acts on the drilling spindle (4) via this roller bearing (42) and is provided between the intermediate wall (6) and a drive wheel (18) arranged on the drilling spindle (4). Schlagbohrmaschine nach Anspruch 1, dadurch gekennzeichnet, daß das Verstellorgan (30) direkt mit der Zwischenwand (6) zusammenwirkt.Impact drill according to claim 1, characterized in that the adjusting member (30) interacts directly with the intermediate wall (6). Schlagbohrmaschine nach Anspruch 2, dadurch gekennzeichnet, daß das Verstellorgan (30) oder die Zwischenwand (6) einen in axialer Richtung erstreckten und dem jeweils anderen Bauteil zugewandten Vorsprung (34) aufweist, der mit einer Vertiefung (36) in dem anderen Bauteil (6, 30) zusammenwirkt.Impact drill according to claim 2, characterized in that the adjusting member (30) or the intermediate wall (6) has a projection (34) which extends in the axial direction and faces the other component and which has a recess (36) in the other component (6 , 30) cooperates. Schlagbohrmaschine nach einem oder mehreren der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Verstellorgan (30) einen schwenkbaren Verstellhebel (32) umfaßt, dessen Schwenkebene senkrecht zur Umdrehungsachse der Bohrspindel (84) verläuft.Impact drill according to one or more of the preceding claims, characterized in that the adjusting member (30) comprises a pivotable adjusting lever (32), the pivot plane of which extends perpendicular to the axis of rotation of the drilling spindle (84). Schlagbohrmaschine nach einem oder mehreren der vorstehenden Ansprüche, gekennzeichnet durch eine feststehende Rastenscheibe (22), die zwischen der Zwischenwand (6) und dem auf der Bohrspindel (4) angeordneten Antriebsrad (18) vorgesehen und von der Zwischenwand (6) gehalten ist.Impact drill according to one or more of the preceding claims, characterized by a fixed locking disk (22) which is provided between the intermediate wall (6) and the drive wheel (18) arranged on the drilling spindle (4) and is held by the intermediate wall (6). Schlagbohrmaschine nach Anspruch 5, dadurch gekennzeichnet, daß die feststehende Rastenscheibe (22) und die Zwischenwand (6) einstückig ausgebildet sind.Impact drill according to claim 5, characterized in that the fixed detent disc (22) and the intermediate wall (6) are integrally formed. Schlagbohrmaschine nach einem oder mehreren der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Verstellorgan (30) über das Axialwälzlager (42) auf das Antriebsrad (18) einwirkt.Impact drill according to one or more of the preceding claims, characterized in that the adjusting member (30) acts on the drive wheel (18) via the axial roller bearing (42). Schlagbohrmaschine nach Anspruch 7, dadurch gekennzeichnet, daß das Axialwälzlager (42) von dem auf der Bohrspindel (4) angeordneten Antriebsrad (18) von Wälzkörpern (44) und einer an das Verstellorgan (30) angrenzenden Lagerschale (40) gebildet ist.Impact drill according to claim 7, characterized in that the axial roller bearing (42) is formed by the drive wheel (18) arranged on the drilling spindle (4), by rolling elements (44) and a bearing shell (40) adjoining the adjusting element (30). Schlagbohrmaschine nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß zwischen dem Antriebsrad (18) und dem Verstellorgan (30) eine Anlaufscheibe (38) vorgesehen ist.Impact drill according to claim 7 or 8, characterized in that a thrust washer (38) is provided between the drive wheel (18) and the adjusting member (30). Schlagbohrmaschine nach einem oder mehreren der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Verstellorgan (30) flächig gegen die Zwischenwand (6) anliegt.Impact drill according to one or more of the preceding claims, characterized in that the adjusting member (30) lies flat against the intermediate wall (6).
EP96109456A 1995-07-25 1996-06-13 Hand-hold drilling machine with device for switching between operating modes "drilling" and "percussive drilling" Expired - Lifetime EP0755756B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19527117 1995-07-25
DE19527117A DE19527117C2 (en) 1995-07-25 1995-07-25 Hand drill with device for switching the operating modes "drilling" and "hammer drilling"

Publications (3)

Publication Number Publication Date
EP0755756A2 true EP0755756A2 (en) 1997-01-29
EP0755756A3 EP0755756A3 (en) 1998-01-28
EP0755756B1 EP0755756B1 (en) 2000-01-05

Family

ID=7767719

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96109456A Expired - Lifetime EP0755756B1 (en) 1995-07-25 1996-06-13 Hand-hold drilling machine with device for switching between operating modes "drilling" and "percussive drilling"

Country Status (2)

Country Link
EP (1) EP0755756B1 (en)
DE (2) DE19527117C2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1834736A1 (en) * 2006-03-18 2007-09-19 Metabowerke GmbH Hand power tool

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2555533A1 (en) * 2006-08-08 2008-02-08 Fern Beauchamp Hammer drill bit chuck attachment

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1346537A (en) * 1971-08-09 1974-02-13 Metabowerke Kg Electrically-powered multi-purpose tools usable as rotary-percussive drills
FR2192894A1 (en) * 1972-07-13 1974-02-15 Black & Decker Mfg Co
DE2715682A1 (en) * 1977-04-07 1978-10-19 Metabowerke Kg IMPACT DRILL WITH NOTES FIXED TO THE HOUSING
EP0399714A2 (en) * 1989-05-25 1990-11-28 Black & Decker Inc. Improvements in or relating to power tools

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2328462C2 (en) * 1973-06-05 1985-08-29 Robert Bosch Gmbh, 7000 Stuttgart Impact drill

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1346537A (en) * 1971-08-09 1974-02-13 Metabowerke Kg Electrically-powered multi-purpose tools usable as rotary-percussive drills
FR2192894A1 (en) * 1972-07-13 1974-02-15 Black & Decker Mfg Co
DE2715682A1 (en) * 1977-04-07 1978-10-19 Metabowerke Kg IMPACT DRILL WITH NOTES FIXED TO THE HOUSING
EP0399714A2 (en) * 1989-05-25 1990-11-28 Black & Decker Inc. Improvements in or relating to power tools

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1834736A1 (en) * 2006-03-18 2007-09-19 Metabowerke GmbH Hand power tool

Also Published As

Publication number Publication date
DE59604090D1 (en) 2000-02-10
DE19527117A1 (en) 1997-01-30
EP0755756A3 (en) 1998-01-28
DE19527117C2 (en) 2000-05-31
EP0755756B1 (en) 2000-01-05

Similar Documents

Publication Publication Date Title
DE4236819C2 (en) Motorized turning tool device
EP0050192B2 (en) Drill hammer
DE3205141C2 (en)
DE2323268C3 (en) Impact drill
DE3429140A1 (en) DRILLING HAMMER WITH A PNEUMATIC STRIKE
DE102007001494B3 (en) Hand-held hammer drill
DE4021037C2 (en) Electric drill with speed and torque adjustment option
CH666216A5 (en) HAND MACHINE TOOL, ESPECIALLY DRILLING OR HAMMER.
CH655273A5 (en) TOOL HOLDER FOR DRILLING AND IMPACT DRILLING DEVICES.
WO2002020224A1 (en) Tool mounting for a hand machine tool
WO2018224248A1 (en) Floating bearing, steering gear, and steering system
DE4302083A1 (en) Power tool, in particular power tool
DE102004058686A1 (en) Power tool with a drive that can be switched over between the operating modes drilling, impact drilling, and chiseling
DE102004008224A1 (en) differential device
DE2522446B2 (en) Safety slip clutch for hand drill
EP0876881B1 (en) Drill- and/or percussion apparatus
EP2206572B1 (en) Electric tool with switchable gear
DE4300612A1 (en) Centering device, in particular for steering valves
DE3004991A1 (en) OVERLOAD CLUTCH FOR TRANSMITTING A LIMITED TORQUE
EP0768151A1 (en) Tool holder
DE4441820B4 (en) Hammer and / or percussion hammer
EP0755756B1 (en) Hand-hold drilling machine with device for switching between operating modes "drilling" and "percussive drilling"
DE10023983B4 (en) Hydrodynamic coupling device
EP1834736A1 (en) Hand power tool
DE19722798C2 (en) clutch

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: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19980220

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19990203

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ITF It: translation for a ep patent filed

Owner name: BUZZI, NOTARO&ANTONIELLI D'OULX

REF Corresponds to:

Ref document number: 59604090

Country of ref document: DE

Date of ref document: 20000210

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20000517

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

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20070228

REG Reference to a national code

Ref country code: FR

Ref legal event code: D3

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

Ref country code: IT

Payment date: 20090626

Year of fee payment: 14

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 NON-PAYMENT OF DUE FEES

Effective date: 20100613

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59604090

Country of ref document: DE

Representative=s name: LORENZ & KOLLEGEN PATENTANWAELTE PARTNERSCHAFT, DE

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

Ref country code: GB

Payment date: 20150623

Year of fee payment: 20

Ref country code: DE

Payment date: 20150623

Year of fee payment: 20

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

Ref country code: FR

Payment date: 20150623

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59604090

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20160612

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20160612