EP0734814A1 - Hand-held machine tool, in particular impact wrench - Google Patents

Hand-held machine tool, in particular impact wrench Download PDF

Info

Publication number
EP0734814A1
EP0734814A1 EP96102077A EP96102077A EP0734814A1 EP 0734814 A1 EP0734814 A1 EP 0734814A1 EP 96102077 A EP96102077 A EP 96102077A EP 96102077 A EP96102077 A EP 96102077A EP 0734814 A1 EP0734814 A1 EP 0734814A1
Authority
EP
European Patent Office
Prior art keywords
ring
spring
hand tool
tool according
helix
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
EP96102077A
Other languages
German (de)
French (fr)
Other versions
EP0734814B1 (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
Atlas Copco Elektrowerkzeuge 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 Atlas Copco Elektrowerkzeuge GmbH filed Critical Atlas Copco Elektrowerkzeuge GmbH
Publication of EP0734814A1 publication Critical patent/EP0734814A1/en
Application granted granted Critical
Publication of EP0734814B1 publication Critical patent/EP0734814B1/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
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches

Definitions

  • the invention relates to a hand tool, in particular an impact wrench, with a motor, a reduction gear and a rotary pulse generator in a housing, a spring means being provided to dampen vibrations of the housing caused by the rotary pulse generator.
  • Such a hand tool is described in DE 39 37 816 A1.
  • the motor acts via the reduction gear on the rotary pulse generator, which transmits sudden rotary pulses to the screwing tool to increase the tightening torque. These twists and turns cause uncomfortable vibrations in the housing.
  • a torsion spring is provided according to DE 39 37 816 A1.
  • the object of the invention is to propose a hand tool of the type mentioned in the introduction, in which the damping is improved in a structurally simple manner.
  • the above object is achieved in a hand-held power tool of the type mentioned in that the one end of the spring is supported on a ring which on the one hand is displaceably guided on a helix parallel to the axis of rotation and on the other hand axially parallel, and in that the other end of the spring is fixed on a housing Part is supported so that the spring is axially tensioned in the event of a rotary impact.
  • the ring In the event of a rotary impact, the ring is displaced axially parallel due to its storage on the helix. This causes the spring to tension axially. The spring relaxes after the rotary stroke. This ensures that no torsion spring is necessary.
  • a coiled compression spring is preferably used. A tension spring could also be used.
  • the described device effectively dampens the vibrations and reduces noise.
  • a large angle of rotation can be achieved for a desired damping. It is also favorable that a small installation space in the housing is sufficient for the device.
  • the ring is preferably guided with its inner circumference on the helix, which is attached on the outside to a part exposed to the rotary impact.
  • the ring is then guided in an axially displaceable, rotationally fixed manner on its outer circumference on a guide fixed to the housing.
  • the reverse arrangement would also be possible, in which the helix is fixed to the housing and the ring is axially displaceably rotatably guided on a part exposed to the rotary impact.
  • the ring is mounted on the helix by means of balls. Correspondingly low frictional forces occur between the ring and the helix. If higher frictional forces to support the damping and / or a further simplification of the structure are desired, the ring can engage the helix with one or more projections formed on it.
  • the spring mentioned is tensioned in clockwise rotation, i.e. when tightening the screw connection.
  • a further damping element is assigned to the ring on its end face opposite the spring for damping blows in the counterclockwise rotation (loosening the screw connection).
  • This can be a simple elastomer body or, to improve the damping in counterclockwise rotation, another coiled compression spring.
  • An impact wrench has a handle housing part (1) and a drive housing part (2), in which a motor (3) Planetary gear (4) and a rotary pulse generator (5) are arranged.
  • the motor (3) drives the rotary pulse generator (5) via the planetary gear (4) as a reduction gear, which in turn drives a shaft (6) onto which a screwing tool, not shown, can be attached.
  • the common axis of the drive unit is labeled (A).
  • the motor (3) can be operated as an electric motor from a battery pack (7). It could also be mains operated or a compressed air motor.
  • the rotary pulse generator (5) is a known, commercially available unit.
  • the planetary gear (4) has a gear housing (8) which is fastened in the drive housing part (2).
  • a carrier (9), on which the motor (3) is held, is screwed to the gear housing (8).
  • a casing (10) is screwed to the gear housing (8), in which the rotary pulse generator (5) is mounted in the exemplary embodiment according to FIGS. 1 to 4.
  • a pinion (12) of the motor (3) meshes with planet wheels (13) of the planetary gear (4), one of which is shown in FIGS. 2 and 4.
  • the planet gear (13) is mounted on an axle piece (14) which sits in a planetary web (15) for driving the rotary pulse generator (5).
  • the planetary web (15) is mounted on the gear housing (8) by means of a ball bearing (16).
  • the planetary gear (4) has a ring gear (18) provided with internal teeth (17).
  • the planet gears (13) mesh with the internal toothing (17).
  • a further ball bearing (19) is arranged between the ring gear (18) and the carrier (9).
  • the ring gear (18) is provided on the outside with a helix (20) runs parallel to the axis of rotation (A) and is formed by a groove-shaped depression.
  • the coil (20) is assigned a ring (21). This is connected to the helix (20) by means of one or more balls (22).
  • a ball (22) is shown in FIGS. 2 and 4. Three or more balls are preferably provided distributed over the inner circumference of the ring (21). If, for example, three balls (22) are provided, then the helix (20) is provided with three parallel gears. If, for example, several balls (22) are provided, then the helix (20) is provided with several parallel gears.
  • the balls (22) are arranged in a cage (23) so that they maintain their distributed position provided on the outer circumference of the ring gear (18) or the inner circumference of the ring (21). It would also be possible to provide only one single-start helix (20) when using several balls (22).
  • the ball receiving groove (24) of the ring (21) would then have a pitch equal to that of the helix (20).
  • the ring (21) is guided with its outer circumference (25), for example by means of a nose (26), on a longitudinal guide slot (27) of the gear housing (8) parallel to the axis (A), but non-rotatably, but axially displaceable.
  • a compression spring (28) is supported on the ring (21) with one end (29). The other end (30) of the compression spring (28) is supported on the gear housing (8).
  • the functionality of the described device is essentially as follows: In operating phases in which the rotary impact does not act back on the ring gear (18) via the planet web (15) and the planet gears (13), the ring gear (18) is relatively blocked because of the balls (22) with the helix (20 ) connected ring (21) is under the bias of the compression spring (28). This position of the ring (21) and the compression spring (28) is above in Fig. 2 the axis (A).
  • the compression spring (28) relaxes and turns the ring gear (18) back via the ring (21) and the balls (22), the energy stored in the compression spring (28) via the planetary gear (4) and the rotary pulse generator (5) on the screwing tool, whose torque supports.
  • a further compression spring (33) is arranged between the carrier (9) and the ring (21) instead of the elastomer ring (31).
  • the spring (33) acts in the counterclockwise rotation just like the spring (28) in the clockwise rotation.
  • the ring gear (18) rotates and takes the ring (21) with it via the balls (22), tensioning the further compression spring (33).
  • the helix (20) is formed on the casing (11) of the rotary pulse generator (5) and not on the ring gear (18) which is arranged in the housing (8) in a rotationally fixed manner. Parts corresponding to FIGS. 2 and 4 are provided with the same reference symbols in FIG. 5.
  • the rotary shocks described above also act on the jacket (11) of the rotary pulse generator (5). 5, they are damped by the ring (21), which engages the balls (20) via balls (22) and in longitudinal guide slots (27) of an inner part (34) parallel to the axis (A) is slidably guided.
  • the ring (21) is supported on both sides by compression springs (28, 33).
  • the inner part (34) sits on the planetary web (15) in a rotationally fixed manner.
  • the planetary web (15) and the inner part (34) could be formed in one piece.
  • the ring (21) transmits the rotational movement of the planetary web (15) to the casing (11) of the rotary pulse generator (5), the shaft (35) of which is rotatably mounted in the planetary web (15) in FIG. 5. If it is disturbing that the spring (28) is supported on the one hand on the rotating ring (21) and on the other hand on the non-rotating housing (8), a bearing can be provided which ensures that the spring (28) is rotatably or non-rotatably supported at both ends.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Retarders (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

The impact screwdriver head contains a member which vibrates along the axis of the tool and is isolated from the housing by a spring which absorbs the vibration energy. One end (29) of the spring (28) is held against a ring (21) engaged in a spiral groove (20) in the vibrating member (18). The other end (30) is retained in a part of the hand-tool housing (8).

Description

Die Erfindung betrifft eine Handwerkzeugmaschine, insbesondere Schlagschrauber, mit einem Motor, einem Untersetzungsgetriebe und einem Drehpulserzeuger in einem Gehäuse, wobei zur Dämpfung von durch den Drehpulserzeuger hervorgerufenen Vibrationen des Gehäuses ein Federmittel vorgesehen ist.The invention relates to a hand tool, in particular an impact wrench, with a motor, a reduction gear and a rotary pulse generator in a housing, a spring means being provided to dampen vibrations of the housing caused by the rotary pulse generator.

Eine derartige Handwerkzeugmaschine ist in der DE 39 37 816 A1 beschrieben. Der Motor wirkt über das Untersetzungsgetriebe auf den Drehpulserzeuger, der zur Verstärkung des Anzugsmoments schlagartige Drehimpulse auf das Schraubwerkzeug überträgt. Diese Drehschläge haben unangenehme Vibrationen des Gehäuses zur Folge. Um diese Vibrationen zu dämpfen, ist nach der DE 39 37 816 A1 eine Torsionsfeder vorgesehen.Such a hand tool is described in DE 39 37 816 A1. The motor acts via the reduction gear on the rotary pulse generator, which transmits sudden rotary pulses to the screwing tool to increase the tightening torque. These twists and turns cause uncomfortable vibrations in the housing. In order to dampen these vibrations, a torsion spring is provided according to DE 39 37 816 A1.

Die Krafteinleitung auf die Torsionsfeder ist konstruktiv problematisch. Außerdem sind größere Verdrehwinkel der Torsionsfeder nur schwer zu erreichen und es treten Schwingungsprobleme auf. Darüber hinaus wirkt die Torsionsfeder nur beim Anziehen der Schraubverbindung (Rechtslauf), nicht jedoch beim Lösen der Verschraubung (Linkslauf). Sie wird im Linkslauf zerstört.The application of force to the torsion spring is structurally problematic. In addition, larger torsion angles of the torsion spring are difficult to achieve and vibration problems occur. In addition, the torsion spring only works when tightening the screw connection (clockwise rotation), but not when loosening the screw connection (counterclockwise rotation). It is destroyed in left-hand rotation.

Aufgabe der Erfindung ist es, eine Handwerkzeugmaschine der eingangs genannten Art vorzuschlagen, bei der die Dämpfung auf konstruktiv einfache Weise verbessert ist.The object of the invention is to propose a hand tool of the type mentioned in the introduction, in which the damping is improved in a structurally simple manner.

Erfindungsgemäß ist obige Aufgabe bei einer Handwerkzeugmaschine der eingangs genannten Art dadurch gelöst, daß das eine Ende der Feder an einem Ring abgestützt ist, der einerseits an einer drehachsparallelen Wendel und andererseits achsparallel verschieblich geführt ist, und daß das andere Ende der Feder sich an einem gehäusefesten Teil abstützt, so daß die Feder bei einem Drehschlag axial gespannt wird.According to the invention, the above object is achieved in a hand-held power tool of the type mentioned in that the one end of the spring is supported on a ring which on the one hand is displaceably guided on a helix parallel to the axis of rotation and on the other hand axially parallel, and in that the other end of the spring is fixed on a housing Part is supported so that the spring is axially tensioned in the event of a rotary impact.

Bei einem Drehschlag wird der Ring infolge seiner Lagerung an der Wendel achsparallel verschoben. Dadurch spannt sich die Feder axial. Nach dem Drehschlag entspannt sich die Feder. Dadurch ist erreicht, daß keine Torsionsfeder notwendig ist. Vorzugsweise wird eine gewendelte Druckfeder eingesetzt. Es könnte auch eine Zugfeder verwendet werden.In the event of a rotary impact, the ring is displaced axially parallel due to its storage on the helix. This causes the spring to tension axially. The spring relaxes after the rotary stroke. This ensures that no torsion spring is necessary. A coiled compression spring is preferably used. A tension spring could also be used.

Die beschriebene Einrichtung dämpft die Vibrationen wirkungsvoll und verringert die Geräuschentwicklung. Durch die Bemessung der Steigung der Wendel läßt sich ein für eine gewünschte Dämpfung großer Drehwinkel erreichen. Günstig ist auch, daß für die Einrichtung ein kleiner Einbauraum im Gehäuse genügt.The described device effectively dampens the vibrations and reduces noise. By dimensioning the pitch of the helix, a large angle of rotation can be achieved for a desired damping. It is also favorable that a small installation space in the housing is sufficient for the device.

Vorzugsweise ist der Ring mit seinem Innenumfang an der Wendel geführt, die außen an einem dem Drehschlag ausgesetzten Teil angebracht ist. Der Ring ist dann an seinem Außenumfang an einer gehäusefesten Führung axial verschieblich drehfest geführt. Es wäre jedoch auch die umgekehrte Anordnung möglich, bei der die Wendel gehäusefest ausgebildet ist und der Ring an einem dem Drehschlag ausgesetzten Teil axial verschieblich drehfest geführt ist.The ring is preferably guided with its inner circumference on the helix, which is attached on the outside to a part exposed to the rotary impact. The ring is then guided in an axially displaceable, rotationally fixed manner on its outer circumference on a guide fixed to the housing. However, the reverse arrangement would also be possible, in which the helix is fixed to the housing and the ring is axially displaceably rotatably guided on a part exposed to the rotary impact.

In bevorzugter Ausgestaltung der Erfindung ist der Ring mittels Kugeln an der Wendel gelagert. Es treten dabei entsprechend niedrige Reibungskräfte zwischen dem Ring und der Wendel auf. Falls höhere Reibungskräfte zur Unterstützung der Dämpfung und/oder eine weitere Vereinfachung des Aufbaus gewünscht sind, kann der Ring mit einer oder mehreren an ihm ausgebildeten Anformungen in die Wendel eingreifen.In a preferred embodiment of the invention, the ring is mounted on the helix by means of balls. Correspondingly low frictional forces occur between the ring and the helix. If higher frictional forces to support the damping and / or a further simplification of the structure are desired, the ring can engage the helix with one or more projections formed on it.

Die genannte Feder wird im Rechtslauf, also beim Anziehen der Schraubverbindung, gespannt. In Ausgestaltung der Erfindung ist zur Dämpfung von Schlägen im Linkslauf (Lösen der Schraubverbindung) dem Ring an seiner der Feder gegenüberliegenden Stirnseite ein weiteres Dämpfungselement zugeordnet. Dieses kann ein einfacher Elastomerkörper oder zur Verbesserung der Dämpfung im Linkslauf eine weitere gewendelte Druckfeder sein.The spring mentioned is tensioned in clockwise rotation, i.e. when tightening the screw connection. In an embodiment of the invention, a further damping element is assigned to the ring on its end face opposite the spring for damping blows in the counterclockwise rotation (loosening the screw connection). This can be a simple elastomer body or, to improve the damping in counterclockwise rotation, another coiled compression spring.

Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen und der folgenden Beschreibung von Ausführungsbeispielen. In der Zeichnung zeigen:

  • Figur 1 einen Akku-Schlagschrauber im Schnitt,
  • Figur 2 eine gegenüber Fig. 1 vergrößerte Teilansicht,
  • Figur 3 eine Wendel an einem Hohlrad des Getriebes in perspektivischer Teilansicht,
  • Figur 4 ein weiteres Ausführungsbeispiel in einer im wesentlichen Fig. 2 entsprechenden Darstellung und
  • Figur 5 ein weiteres Ausführungsbeispiel.
Further advantageous refinements of the invention result from the subclaims and the following description of exemplary embodiments. The drawing shows:
  • FIG. 1 shows a cordless impact wrench in section,
  • FIG. 2 shows a partial view enlarged compared to FIG. 1,
  • FIG. 3 shows a helix on a ring gear of the transmission in a partial perspective view,
  • Figure 4 shows another embodiment in a representation corresponding essentially to Fig. 2 and
  • Figure 5 shows another embodiment.

Ein Schlagschrauber weist ein Handgriffgehäuseteil(1) und ein Antriebsgehäuseteil(2) auf, in dem ein Motor(3), ein Planetengetriebe(4) und ein Drehpulserzeuger(5) angeordnet sind. Der Motor(3) treibt über das Planetengetriebe(4) als Untersetzungsgetriebe den Drehpulserzeuger(5) an, der seinerseits eine Welle(6) antreibt, auf die ein nicht näher dargestelltes Schraubwerkzeug aufsteckbar ist. Die gemeinsame Achse der Antriebseinheit ist mit (A) bezeichnet.An impact wrench has a handle housing part (1) and a drive housing part (2), in which a motor (3) Planetary gear (4) and a rotary pulse generator (5) are arranged. The motor (3) drives the rotary pulse generator (5) via the planetary gear (4) as a reduction gear, which in turn drives a shaft (6) onto which a screwing tool, not shown, can be attached. The common axis of the drive unit is labeled (A).

Der Motor(3) ist als Elektromotor aus einem Akkupack(7) betreibbar. Er könnte auch netzbetreibbar sein oder auch ein Druckluftmotor sein. Der Drehpulserzeuger(5) ist eine bekannte, handelsübliche Baueinheit.The motor (3) can be operated as an electric motor from a battery pack (7). It could also be mains operated or a compressed air motor. The rotary pulse generator (5) is a known, commercially available unit.

Das Planetengetriebe(4) weist ein Getriebegehäuse(8) auf, das im Antriebsgehäuseteil(2) befestigt ist. Mit dem Getriebegehäuse(8) ist einerseits ein Träger(9) verschraubt, an dem der Motor(3) gehalten ist. Andererseits ist mit dem Getriebegehäuse(8) eine Hülle(10) verschraubt, in der beim Ausführungsbeispiel nach den Figuren 1 bis 4 der Drehpulserzeuger(5) gelagert ist.The planetary gear (4) has a gear housing (8) which is fastened in the drive housing part (2). A carrier (9), on which the motor (3) is held, is screwed to the gear housing (8). On the other hand, a casing (10) is screwed to the gear housing (8), in which the rotary pulse generator (5) is mounted in the exemplary embodiment according to FIGS. 1 to 4.

Ein Ritzel(12) des Motors(3) kämmt mit Planetenrädern(13) des Planetengetriebes(4), von denen in den Figuren 2 und 4 eines gezeigt ist. Das Planetenrad(13) ist an einem Achsstück(14) gelagert, das in einem Plantetensteg(15) zum Antrieb des Drehpulserzeugers(5) sitzt. Der Planetensteg(15) ist mittels eines Kugellagers(16) am Getriebegehäuse(8) gelagert.A pinion (12) of the motor (3) meshes with planet wheels (13) of the planetary gear (4), one of which is shown in FIGS. 2 and 4. The planet gear (13) is mounted on an axle piece (14) which sits in a planetary web (15) for driving the rotary pulse generator (5). The planetary web (15) is mounted on the gear housing (8) by means of a ball bearing (16).

Das Planetengetriebe(4) weist ein mit einer Innenverzahnung(17) versehenes Hohlrad(18) auf. Mit der Innenverzahnung(17) kämmen die Planetenräder(13). Zwischen dem Hohlrad(18) und dem Träger(9) ist ein weiteres Kugellager(19) angeordnet.The planetary gear (4) has a ring gear (18) provided with internal teeth (17). The planet gears (13) mesh with the internal toothing (17). A further ball bearing (19) is arranged between the ring gear (18) and the carrier (9).

Bei der Ausführung nach den Figuren 2 und 4 ist das Hohlrad(18) außen mit einer Wendel(20) versehen, die parallel zur Drehache(A) verläuft und von einer rinnenförmigen Vertiefung gebildet ist. Der Wendel(20) ist ein Ring(21) zugeordnet. Dieser steht mittels einer oder mehreren Kugeln(22) mit der Wendel(20) in Verbindung. In den Figuren 2 und 4 ist jeweils eine Kugel (22) gezeigt. Vorzugsweise sind drei oder mehrere Kugeln am Innenumfang des Ringes(21) verteilt vorgesehen. Sind beispielsweise drei Kugeln(22) vorgesehen, dann ist die Wendel(20) mit drei parallelen Gängen versehen. Sind beispielsweise mehrere Kugeln(22) vorgesehen, dann ist die Wendel(20) mit mehreren parallelen Gängen versehen. Die Kugeln(22) sind in einem Käfig(23) angeordnet, damit sie ihre am Außenumfang des Hohlrades(18) bzw. Innenumfang des Ringes(21) vorgesehene, verteilte Lage beibehalten. Es wäre auch möglich, bei der Verwendung mehrerer Kugeln (22) nur eine eingängige Wendel(20) vorzusehen. Die Kugelaufnahmerinne(24) des Ringes(21) müßte dann eine der Wendel(20) gleiche Steigung aufweisen.In the embodiment according to Figures 2 and 4, the ring gear (18) is provided on the outside with a helix (20) runs parallel to the axis of rotation (A) and is formed by a groove-shaped depression. The coil (20) is assigned a ring (21). This is connected to the helix (20) by means of one or more balls (22). A ball (22) is shown in FIGS. 2 and 4. Three or more balls are preferably provided distributed over the inner circumference of the ring (21). If, for example, three balls (22) are provided, then the helix (20) is provided with three parallel gears. If, for example, several balls (22) are provided, then the helix (20) is provided with several parallel gears. The balls (22) are arranged in a cage (23) so that they maintain their distributed position provided on the outer circumference of the ring gear (18) or the inner circumference of the ring (21). It would also be possible to provide only one single-start helix (20) when using several balls (22). The ball receiving groove (24) of the ring (21) would then have a pitch equal to that of the helix (20).

Der Ring(21) ist mit seinem Außenumfang(25), beispielsweise mittels einer Nase(26), an einem zur Achse (A) parallelen Längsführungsschlitz(27) des Getriebegehäuses(8) drehfest, jedoch axial verschieblich geführt. Am Ring(21) stützt sich eine Druckfeder(28) mit ihrem einen Ende(29) ab. Das andere Ende(30) der Druckfeder(28) stützt sich an dem Getriebegehäuse(8) ab.The ring (21) is guided with its outer circumference (25), for example by means of a nose (26), on a longitudinal guide slot (27) of the gear housing (8) parallel to the axis (A), but non-rotatably, but axially displaceable. A compression spring (28) is supported on the ring (21) with one end (29). The other end (30) of the compression spring (28) is supported on the gear housing (8).

Die Funktionsweise der beschriebenen Einrichtung ist im wesentlichen folgende:
In Betriebsphasen, in denen der Drehschlag nicht über den Planetensteg(15) und die Planetenräder(13) auf das Hohlrad (18) zurückwirkt, ist das Hohlrad(18) relativ blockiert, weil der über die Kugeln(22) mit der Wendel(20) in Verbindung stehende Ring(21) unter der Vorspannung der Druckfeder(28) steht. Diese Stellung des Ringes(21) und der Druckfeder(28) ist in Fig. 2 oberhalb der Achse(A) dargestellt.The functionality of the described device is essentially as follows:
In operating phases in which the rotary impact does not act back on the ring gear (18) via the planet web (15) and the planet gears (13), the ring gear (18) is relatively blocked because of the balls (22) with the helix (20 ) connected ring (21) is under the bias of the compression spring (28). This position of the ring (21) and the compression spring (28) is above in Fig. 2 the axis (A).

Tritt infolge eines kräftigen Drehschlages ein entsprechend höheres Rückschlag-Drehmoment an dem Hohlrad(18) auf, dann dreht sich dieses um die Achse(A) und nimmt dabei über die Kugeln(22) den Ring(21) mit, wobei dieser die Druckfeder(28) spannt. Der sich dabei ergebende Drehwinkel des Hohlrades(18) hängt von der Steigung der Wendel(20) und der Federkennlinie der Druckfeder(28) ab. Dadurch ist erreicht, daß druckschlagbedingte Vibrationen gegenüber dem Getriebegehäuse(8) und damit auch dem Antriebsgehäuseteil (2) und dem Handgriffgehäuseteil(1) gedämpft sind, so daß keine lästigen Vibrationen oder Geräuschentwicklungen auftreten. Da die Wendel(20) sich über wesentlich mehr als 360o erstreckt, sind in Abstimmung mit der Kennlinie der Druckfeder(28) gute Dämpfungswerte erreichbar. Eine Stellung, in der sich der Ring(21) infolge einer Verdrehung des Hohlrades(18) achsparallel verschoben hat und dabei die Druckfeder(28) weiter gespannt hat, ist in Fig. 2 unterhalb der Achse(A) gezeigt.If a correspondingly higher recoil torque occurs on the ring gear (18) as a result of a strong rotary impact, then this rotates about the axis (A) and takes the ring (21) with it via the balls (22), whereby the compression spring ( 28) spans. The resulting angle of rotation of the ring gear (18) depends on the pitch of the helix (20) and the spring characteristic of the compression spring (28). It is thereby achieved that vibrations caused by pressure shock are dampened with respect to the gear housing (8) and thus also the drive housing part (2) and the handle housing part (1), so that no annoying vibrations or noise developments occur. Since the helix (20) extends over more than 360 ° , good damping values can be achieved in coordination with the characteristic of the compression spring (28). A position in which the ring (21) has shifted axially parallel as a result of a rotation of the ring gear (18) and has further tensioned the compression spring (28) is shown in FIG. 2 below the axis (A).

Nach einer Drehschlagspitze entspannt sich die Druckfeder (28) und dreht über den Ring(21) und die Kugeln(22) das Hohlrad(18) zurück, wobei die in der Druckfeder(28) gespeicherte Energie über das Planetengetriebe(4) und den Drehpulserzeuger(5) auf das Schraubwerkzeug, dessen Drehmoment unterstützend, zurückwirkt.After a rotary impact tip, the compression spring (28) relaxes and turns the ring gear (18) back via the ring (21) and the balls (22), the energy stored in the compression spring (28) via the planetary gear (4) and the rotary pulse generator (5) on the screwing tool, whose torque supports.

Die oben anhand von Fig. 2 erläuterte Funktion betrifft den Fall des Anziehens einer Schraube (Rechtslauf). Wird eine Schraube gelöst, dann können ebenfalls kräftige Drehschlagspitzen auftreten, die zu Vibrationen führen können. Um diese zu dämpfen, ist bei der Ausführung nach Fig. 2 im Träger(9) ein federelastischer bzw. gummielastischer Körper, beispielsweise ein Elastomerring (31), angeordnet, der durch eine dem Ring(21) zugewandte Buchse(32) abgedeckt ist. Bei einem Drehschlag im Linkslauf schlägt der Ring(21) auf die Buchse(32) und damit den Elastomerring(31), so daß auch im Linkslauf eine Dämpfung erfolgt.The function explained above with reference to FIG. 2 relates to the case of tightening a screw (clockwise rotation). If a screw is loosened, strong rotary impact tips can also occur, which can lead to vibrations. In order to dampen this, in the embodiment according to FIG. 2 a spring-elastic or rubber-elastic body, for example an elastomer ring (31), is arranged in the carrier (9) and is covered by a bushing (32) facing the ring (21). In the event of a spin in the The ring (21) strikes the bushing (32) counterclockwise and thus the elastomer ring (31), so that damping also takes place in the counterclockwise rotation.

Beim Ausführungsbeispiel nach Fig. 4 ist anstelle des Elastomerrings(31) eine weitere Druckfeder(33) zwischen dem Träger(9) und dem Ring(21) angeordnet. Die Feder(33) wirkt im Linkslauf ebenso wie die Feder(28) im Rechtslauf. Bei einer Drehschlagspitze im Linkslauf dreht sich das Hohlrad(18) und nimmt dabei über die Kugeln(22) den Ring(21) mit, wobei er die weitere Druckfeder(33) spannt.In the embodiment of FIG. 4, a further compression spring (33) is arranged between the carrier (9) and the ring (21) instead of the elastomer ring (31). The spring (33) acts in the counterclockwise rotation just like the spring (28) in the clockwise rotation. In the event of a rotary impact tip rotating counterclockwise, the ring gear (18) rotates and takes the ring (21) with it via the balls (22), tensioning the further compression spring (33).

Beim Ausführungsbeispiel nach Fig. 5 ist die Wendel(20) am Mantel(11) des Drehpulserzeugers(5) und nicht an dem Hohlrad(18) ausgebildet, das drehfest im Gehäuse(8) angeordnet ist. Den Figuren 2 und 4 entsprechende Teile sind in Fig. 5 mit gleichen Bezugszeichen versehen. Die oben beschriebenen Drehschläge wirken auch am Mantel(11) des Drehpulserzeugers(5). Sie sind in ihrer Auswirkung auf das Gehäuse bei der Ausführung nach Fig. 5 durch den Ring (21) gedämpft, der über Kugeln(22) in die Wendel(20) eingreift und in Längsführungsschlitzen(27) eines Innenteils(34) parallel zur Achse(A) verschieblich geführt ist. Der Ring(21) ist wie bei Fig. 4 beidseitig durch Druckfedern(28,33) abgestützt.5, the helix (20) is formed on the casing (11) of the rotary pulse generator (5) and not on the ring gear (18) which is arranged in the housing (8) in a rotationally fixed manner. Parts corresponding to FIGS. 2 and 4 are provided with the same reference symbols in FIG. 5. The rotary shocks described above also act on the jacket (11) of the rotary pulse generator (5). 5, they are damped by the ring (21), which engages the balls (20) via balls (22) and in longitudinal guide slots (27) of an inner part (34) parallel to the axis (A) is slidably guided. As in FIG. 4, the ring (21) is supported on both sides by compression springs (28, 33).

Auf dem Planetensteg(15) sitzt drehfest das Innenteil(34). Der Planetensteg(15) und das Innenteil(34) könnten einstückig ausgebildet sein. Der Ring(21) überträgt die Drehbewegung des Planetenstegs(15) auf den Mantel(11) des Drehpulserzeugers(5), dessen Welle(35) bei Fig. 5 im Planetensteg(15) drehbar gelagert ist. Wenn es stört, daß sich die Feder(28) einerseits am rotierenden Ring(21) und andererseits am nichtrotierenden Gehäuse(8) abstützt, kann ein Lager vorgesehen werden, das gewährleistet, daß die Feder(28) beidendig rotierbar oder nichtrotierbar gelagert ist.The inner part (34) sits on the planetary web (15) in a rotationally fixed manner. The planetary web (15) and the inner part (34) could be formed in one piece. The ring (21) transmits the rotational movement of the planetary web (15) to the casing (11) of the rotary pulse generator (5), the shaft (35) of which is rotatably mounted in the planetary web (15) in FIG. 5. If it is disturbing that the spring (28) is supported on the one hand on the rotating ring (21) and on the other hand on the non-rotating housing (8), a bearing can be provided which ensures that the spring (28) is rotatably or non-rotatably supported at both ends.

Claims (14)

Handwerkzeugmaschine, insbesondere Schlagschrauber, mit einem Motor, einem Untersetzungsgetriebe und einem Drehpulserzeuger in einem Gehäuse, wobei zur Dämpfung von durch den Drehpulserzeuger hervorgerufenen Vibrationen des Gehäuses ein Federmittel vorgesehen ist,
dadurch gekennzeichnet,
daß das eine Ende der Feder(28) an einem Ring(21) abgestützt ist, der einerseits an einer drehachsparallelen Wendel(20) und andererseits achsparallel verschieblich geführt ist und daß das andere Ende der Feder(28) sich am gehäusefesten Teil(8;10) abstützt, so daß die Feder(28) bei einem Drehschlag axial gespannt wird.Hand tool, in particular impact wrench, with a motor, a reduction gear and a rotary pulse generator in a housing, a spring means being provided to dampen vibrations of the housing caused by the rotary pulse generator,
characterized,
that one end of the spring (28) is supported on a ring (21) which is guided on the one hand on a helix (20) parallel to the axis of rotation and on the other hand axially displaceable and that the other end of the spring (28) is attached to the part (8; 10) supports, so that the spring (28) is axially tensioned in the event of a rotary impact. Handwerkzeugmaschine nach Anspruch 1,
dadurch gekennzeichnet,
daß die Feder eine gewendelte Druckfeder(28) oder eine Zugfeder ist.Hand tool according to claim 1,
characterized,
that the spring is a coiled compression spring (28) or a tension spring. Handwerkzeugmaschine nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß der Ring(21) zwischen einem gehäusefesten Teil(8) und einem dem Drehschlag ausgesetzten Teil(18) achsparallel verschieblich geführt ist.Hand tool according to claim 1 or 2,
characterized,
that the ring (21) between a housing-fixed part (8) and a part exposed to the rotary impact (18) is axially displaceably guided. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
daß der Ring(21) mit seinem Innenumfang an der Wendel(20) geführt ist, die außen an einem dem Drehschlag ausgesetzten Teil(18;11) angebracht ist.Hand tool according to one of the preceding claims,
characterized,
that the ring (21) is guided with its inner circumference on the helix (20), the outside on the rotary impact exposed part (18; 11) is attached. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
daß der Ring(21) an seinem Außenumfang an einer gehäusefesten Führung(27) axial verschieblich, drehfest geführt ist.Hand tool according to one of the preceding claims,
characterized,
that the ring (21) is axially displaceably, non-rotatably guided on its outer circumference on a guide (27) fixed to the housing. Handwerkzeugmaschine nach Anspruch 5,
dadurch gekennzeichnet,
daß die Wendel(20) außen am Hohlrad(18) des von einem Planetengetriebe(4) gebildeten Untersetzungsgetriebes vorgesehen ist.Hand tool according to claim 5,
characterized,
that the helix (20) is provided on the outside of the ring gear (18) of the reduction gear formed by a planetary gear (4). Handwerkzeugmaschine nach Anspruch 4,
dadurch gekennzeichnet,
daß die Wendel(20) außen am Mantel(11) des Drehpulserzeugers(5) vorgesehen ist.Hand tool according to claim 4,
characterized,
that the coil (20) is provided on the outside of the jacket (11) of the rotary pulse generator (5). Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
daß der Ring(21) wenigstens mittels einer Kugel(22) an der Wendel(20) gelagert ist.Hand tool according to one of the preceding claims,
characterized,
that the ring (21) is mounted on the helix (20) at least by means of a ball (22). Handwerkzeugmaschine nach Anspruch 8,
dadurch gekennzeichnet,
daß die Kugeln(22) in einem Käfig am Umfang des Ringes(21) beabstandet gehalten sind.Hand tool according to claim 8,
characterized,
that the balls (22) are kept spaced in a cage on the circumference of the ring (21). Handwerkzeugmaschine nach Anspruch 8 oder 9,
dadurch gekennzeichnet,
daß die Wendel(20) entsprechend der Anzahl der Kugeln(22) mehrgängig ist.Hand tool according to claim 8 or 9,
characterized,
that the helix (20) is multi-start according to the number of balls (22). Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
daß die Feder(28) im entspannten Zustand eine Vorspannung hat, die das dem Drehschlag ausgesetzte Teil(18;11) gegenüber dem Teil(8;34), an dem der Ring(21) achsparallel verschieblich geführt ist, relativ blockiert hält, solange kein besonderes Drehschlagmoment auftritt.Hand tool according to one of the preceding claims,
characterized,
that the spring (28) has a pretension in the relaxed state, which holds the part exposed to the rotary shock (18; 11) relative to the part (8; 34) on which the ring (21) is axially displaceably guided, relatively blocked as long as no particular torque occurs. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
daß die Feder(28) im Rechtslauf gespannt wird und daß zur Dämpfung von Drehschlägen im Linkslauf dem Ring(21) an seiner der Feder(28) gegenüberliegenden Stirnseite ein weiteres Dämpfungselement(31;33) zugeordnet ist.Hand tool according to one of the preceding claims,
characterized,
that the spring (28) is tensioned in clockwise rotation and that a further damping element (31; 33) is assigned to the ring (21) on its end face opposite the spring (28) for damping rotary shocks in counterclockwise rotation. Handwerkzeugmaschine nach Anspruch 12,
dadurch gekennzeichnet,
daß das weitere Dämpfungselement ein federelastischer Körper, insbesondere Elastomerkörper(31), ist.Hand tool according to claim 12,
characterized,
that the further damping element is a resilient body, in particular an elastomer body (31). Handwerkzeugmaschine nach Anspruch 12,
dadurch gekennzeichnet,
daß das weitere Dämpfungselement eine weitere gewendelte Druckfeder(33) ist.Hand tool according to claim 12,
characterized,
that the further damping element is a further coiled compression spring (33).
EP96102077A 1995-03-23 1996-02-13 Hand-held machine tool, in particular impact wrench Expired - Lifetime EP0734814B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19510578A DE19510578A1 (en) 1995-03-23 1995-03-23 Hand machine tools, in particular impact wrenches
DE19510578 1995-03-23

Publications (2)

Publication Number Publication Date
EP0734814A1 true EP0734814A1 (en) 1996-10-02
EP0734814B1 EP0734814B1 (en) 1998-07-15

Family

ID=7757476

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96102077A Expired - Lifetime EP0734814B1 (en) 1995-03-23 1996-02-13 Hand-held machine tool, in particular impact wrench

Country Status (4)

Country Link
US (1) US5706902A (en)
EP (1) EP0734814B1 (en)
DE (2) DE19510578A1 (en)
ES (1) ES2120790T3 (en)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29517258U1 (en) * 1995-10-31 1995-12-21 Cooper Industries, Inc., Houston, Tex. Tool
JP3559174B2 (en) * 1998-05-25 2004-08-25 リョービ株式会社 Impact tool impact structure
US6158526A (en) 1999-03-09 2000-12-12 Snap-On Tools Company Reversible impact mechanism with structure limiting hammer travel
US6139359A (en) * 1999-04-08 2000-10-31 Snap-On Tools Company Cordless screwdriver and multi-position battery pack therefor
DE10021355B4 (en) * 2000-05-02 2005-04-28 Hilti Ag Beating electric hand tool with vibration-decoupled assemblies
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US6487940B2 (en) 2001-01-23 2002-12-03 Associated Toolmakers Incorporated Nut driver
JP2002254336A (en) * 2001-03-02 2002-09-10 Hitachi Koki Co Ltd Power tool
GB2383967A (en) * 2002-01-15 2003-07-16 Tranmax Machinery Co Ltd A torque restricting mechanism of a pin hammer-type hammering device
US6729414B2 (en) * 2002-07-16 2004-05-04 Black & Decker Inc. Cordless drill with metal housing
US7326008B2 (en) * 2004-12-10 2008-02-05 Danly Iem, Llc Servo tapping unit with built in shock protection
US20060237205A1 (en) * 2005-04-21 2006-10-26 Eastway Fair Company Limited Mode selector mechanism for an impact driver
JP2006315093A (en) * 2005-05-10 2006-11-24 Hitachi Koki Co Ltd Impact tool
US7806198B2 (en) 2007-06-15 2010-10-05 Black & Decker Inc. Hybrid impact tool
AU2009279632B2 (en) * 2008-08-06 2013-09-26 Milwaukee Electric Tool Corporation Precision torque tool
US9193053B2 (en) 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
DE102009001657A1 (en) * 2009-03-19 2010-09-23 Robert Bosch Gmbh Hand tool
US8631880B2 (en) * 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
US8460153B2 (en) * 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US8584770B2 (en) * 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
JP5463221B2 (en) * 2010-07-02 2014-04-09 株式会社マキタ Oil pulse rotating tool
EP2635410B1 (en) 2010-11-04 2016-10-12 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
EP3636389A1 (en) 2012-02-03 2020-04-15 Milwaukee Electric Tool Corporation Rotary hammer
US9849577B2 (en) 2012-02-03 2017-12-26 Milwaukee Electric Tool Corporation Rotary hammer
JP6050110B2 (en) 2012-12-27 2016-12-21 株式会社マキタ Impact tools
US10328560B2 (en) * 2015-02-23 2019-06-25 Brian Romagnoli Multi-mode drive mechanisms and tools incorporating the same
EP4234168A1 (en) * 2022-02-28 2023-08-30 Hilti Aktiengesellschaft Impact wrench with damper

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2662434A (en) * 1952-02-28 1953-12-15 Millers Falis Company Power-operated rotary impact wrench
US2907239A (en) * 1957-01-08 1959-10-06 Bosch Gmbh Robert Rotary impact tool
DE3937816A1 (en) * 1988-11-14 1990-06-07 Atlas Copco Tools Ab ROTARY BLOW HAND MACHINE
DE9111449U1 (en) * 1991-09-14 1992-01-02 Deprag Schulz Gmbh U. Co, 8450 Amberg Hydraulic impulse wrench with torque cut-off

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2343596A (en) * 1941-12-12 1944-03-07 Cleveland Pneumatic Tool Co Nut setter
DE1163259B (en) * 1951-01-26 1964-02-13 Chicago Pneumatic Tool Co Motor-driven impact wrench

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2662434A (en) * 1952-02-28 1953-12-15 Millers Falis Company Power-operated rotary impact wrench
US2907239A (en) * 1957-01-08 1959-10-06 Bosch Gmbh Robert Rotary impact tool
DE3937816A1 (en) * 1988-11-14 1990-06-07 Atlas Copco Tools Ab ROTARY BLOW HAND MACHINE
DE9111449U1 (en) * 1991-09-14 1992-01-02 Deprag Schulz Gmbh U. Co, 8450 Amberg Hydraulic impulse wrench with torque cut-off

Also Published As

Publication number Publication date
DE19510578A1 (en) 1996-09-26
DE59600329D1 (en) 1998-08-20
ES2120790T3 (en) 1998-11-01
EP0734814B1 (en) 1998-07-15
US5706902A (en) 1998-01-13

Similar Documents

Publication Publication Date Title
EP0734814A1 (en) Hand-held machine tool, in particular impact wrench
DE19512660C2 (en) Pyrotechnic rotary tensioner with mass body drive
DE3937816C2 (en) Rotary impact hand tool
EP1979134B1 (en) Gearing, in particular for portable electric power tools
EP1259744A1 (en) Torsion spring set
EP3149356B1 (en) Rotation damper
DE202006014850U1 (en) Mechanical beater for manual machine tool has impact body mounted axially movable and rotationally secured on drive shaft and an elastomer axial stop as ring-shaped spring element also mounted on drive shaft
DE10201866A1 (en) Joint for power-assisted steering system has elastic body between first and second transmission elements to transfer rotation of first transmission element to second
DE102016224245A1 (en) Hand tool with a spring detent mechanism
DE102009027223B4 (en) Hand-held power tool with ratchet mechanism
EP2097657A1 (en) Torsional vibration damper comprising a sectional primary element
EP2576145A1 (en) Portable power tool with a mechanical percussion mechanism
WO2011124559A1 (en) Shock absorber
DE102012022788B3 (en) Reduction gear unit for adjusting device of motor vehicle, has brake element that is mounted in housing section in axially movable manner in direction of input shaft, where brake element comprises outer thread
DE102009049879B4 (en) Vibration damper for damping torsional vibrations in the drive train of a motor vehicle
DE102007062248A1 (en) Hand tool with a, at least one rotatably mounted intermediate shaft comprehensive gear device
DE3230663C2 (en) Clutch disc with torsional vibration damper and control plate
DE4143218A1 (en) Device for connecting screwdriver bits with drive source - consists of two-part socket linked by torque coupling
DE10251859A1 (en) Spring and damper arrangement for pivotal movement of sprung mounted lever arm(s), e.g. for chain tensioner, has friction element(s) in frictional contact with damping element to damp rotary movement
DE3437344C2 (en) Vibration suppression device for a drive device
DE10330180A1 (en) Cordless drill and driver, comprising shock absorbing element inserted between drive housing and handle
DE10315576A1 (en) Drive for seat adjuster for motor vehicle has flywheel mass provided on flexible shaft arranged between electric motor and flexible shaft and attached to shaft so as to rotate with it
EP1724432A2 (en) Roller for roller blind
DE102010043099A1 (en) Hand tool with a mechanical percussion
EP1391269A2 (en) Hand tool, especially screwdriver

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): DE ES FR GB IT SE

17P Request for examination filed

Effective date: 19961015

17Q First examination report despatched

Effective date: 19970603

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

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

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ATLAS COPCO ELECTRIC TOOLS GMBH

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT SE

REF Corresponds to:

Ref document number: 59600329

Country of ref document: DE

Date of ref document: 19980820

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

Effective date: 19980918

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2120790

Country of ref document: ES

Kind code of ref document: T3

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

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

Ref country code: SE

Payment date: 20060214

Year of fee payment: 11

Ref country code: DE

Payment date: 20060214

Year of fee payment: 11

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

Ref country code: FR

Payment date: 20060216

Year of fee payment: 11

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

Ref country code: GB

Payment date: 20060221

Year of fee payment: 11

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

Ref country code: ES

Payment date: 20060227

Year of fee payment: 11

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

Ref country code: IT

Payment date: 20060228

Year of fee payment: 11

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 NON-PAYMENT OF DUE FEES

Effective date: 20070214

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20070213

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20071030

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: 20070901

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 NON-PAYMENT OF DUE FEES

Effective date: 20070213

Ref country code: FR

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

Effective date: 20070228

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20070214

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

Ref country code: ES

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

Effective date: 20070214

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: 20070213