EP2132005A1 - Rotary percussion mechanism - Google Patents

Rotary percussion mechanism

Info

Publication number
EP2132005A1
EP2132005A1 EP08708789A EP08708789A EP2132005A1 EP 2132005 A1 EP2132005 A1 EP 2132005A1 EP 08708789 A EP08708789 A EP 08708789A EP 08708789 A EP08708789 A EP 08708789A EP 2132005 A1 EP2132005 A1 EP 2132005A1
Authority
EP
European Patent Office
Prior art keywords
anvil
rotary impact
tool shaft
mechanism according
hammer
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
EP08708789A
Other languages
German (de)
French (fr)
Other versions
EP2132005B1 (en
Inventor
Aldo Di Nicolantonio
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2132005A1 publication Critical patent/EP2132005A1/en
Application granted granted Critical
Publication of EP2132005B1 publication Critical patent/EP2132005B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
    • B25D11/106—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool cam member and cam follower having the same shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode

Definitions

  • the invention relates to a rotary impact mechanism for an electric tool, in particular an electric hand tool according to the preamble of claim 1.
  • Such rotary impact devices are used exclusively in helicopters and rotary impact wrenches (impact wrenches).
  • An example of a rotary impact wrench with a rotary impact mechanism is disclosed in DE 147 88 09.
  • rotary impact drives a distinction is made between three basic types, namely cam followers, V-groove impactors and hydraulic pulse impactors.
  • Rotary tappets enable the release of high torques with relatively low power input in almost torque-free manner.
  • Impact drills usually use detent impact devices, which in contrast to the rotary impact mechanism do not produce any angular momentum in the circumferential direction on the tool shaft. conditions, but only an adjustment pulse in the axial direction.
  • Rastenschlagwerke have the advantage that they are extremely simple and inexpensive to produce. In practice, however, these prove to be less effective (low impact). More powerful mechanical percussion for impact drills, for example, so-called mass impact, the structure of which is very complex and they are therefore expensive to produce and assemble.
  • the invention is therefore based on the object to modify a rotary striking mechanism for use in a percussion drill.
  • the invention is based on the idea of aligning or shaping the at least one hammer surface and / or the at least one anvil surface in such a way that a force component acting on the tool shaft in the axial direction is generated by the impact of the hammer surface on the anvil surface in addition to the angular momentum in the circumferential direction will, which ensures that the adjustable in the axial direction stored tool shaft, which preferably carries a drill chuck with drilling tool, is accelerated in the direction of the workpiece to be machined.
  • the rotary impact mechanism according to the invention can be used to produce a striking drill driver.
  • the rotational energy of the rotational impact weight is used, inter alia, for generating the axial force component.
  • the preferred oblique or curved alignment or shaping of the hammer surface and / or the anvil surface thereby ensures a division of the angular momentum into an axial and a peripheral component.
  • the rotary impact mechanism according to the invention is extremely powerful and requires little space.
  • the rotary impact is inexpensive to produce.
  • the claimed Drehtschwerk can cover even without a gear ratio to cover a large speed range with high torque and works efficiently and kickback, even in hard building materials such as concrete or rock.
  • the drilling action is supported in addition to the axial impact of the impact component acting in the circumferential direction.
  • the rotary impact mechanism can be formed with all known adjustment mechanisms, such as a cam mechanism, a Schrägnuten mechanism, in particular a V-groove mechanism, or a particular hydraulic pulse mechanism.
  • An advantage is an embodiment in which, with an increased torque requirement by the tool or by the tool shaft and an associated reduction in rotational speed of the tool shaft by means of an adjustment mechanism, a relative movement between the rotary shaft impact weight and the anvil, which is preferably permanently coupled torque-transmitting with the tool shaft, in particular rotatably connected thereto, effected in the axial and circumferential direction, whereby from the rotational movement of the rotational impact weight out a collision between the hammer surface and the anvil surface is provoked.
  • the tool shaft is axially adjustable in such a way, in particular between two axial stops, that an axial displacement of the tool results by at least two, preferably at least three, in particular at least five millimeters, or more.
  • the axial force component is achieved on the tool shaft by the fact that the hammer surface with an imaginary, orthogonal to the axis of rotation of the tool shaft and the rotary impact weight, in particular by the anvil, extending plane an angle ⁇ ⁇ 90th ° is clamped.
  • the angle ⁇ the ratio between the angular momentum and the axial momentum can be set.
  • the anvil surface is inclined relative to the orthogonal to the axis of rotation plane at an angle ß ⁇ 90 °, ie with this plane an angle ß ⁇ 90 °.
  • the hammer surface and the corresponding anvil surface are curved in the same direction and with the same radius of curvature, that are at least approximately formed congruent.
  • the angle ⁇ at least approximately from an angular range between 5 ° and 85 °, in particular at least approximately between 15 ° and 75 °, preferably at least approximately between 25 ° and 65 °, preferably between 35 ° and 55 ° is selected, or more preferably about 45 °.
  • the angle ⁇ is preferably 180 ° - ⁇ .
  • the anvil has a plurality of anvil surfaces inclined in the same direction and / or the rotational impact weight has a plurality of hammer surfaces inclined in the same direction.
  • both mutually oppositely inclined anvil surfaces and both mutually oppositely inclined hammer surfaces are each at an axial projection of the anvil and the rotational impact weight.
  • At least one adjusting mechanism is provided for varying the angle ⁇ or the angle ⁇ .
  • this adjustment mechanism is designed such that an angle ⁇ and / or an angle ß of at least approximately 90 ° is adjustable, so that no axial impact pulse results on the tool shaft and equipped with the rotary percussion power tool can be used as a rotary impact wrench.
  • rotary impact mechanism in which the adjusting mechanism can be blocked or bridged, preferably such that at an increased torque request by the tool shaft no impact pulse is triggered.
  • a construction in which the tool shaft, in particular together with the anvil by means of a spring, in particular designed as a helical spring in the direction of an axial stop is subjected to spring force, wherein the axial stop is preferably arranged at the opposite end of the free end of the tool shaft.
  • the spring serves as a return spring for adjusting the tool shaft to its starting position after full axial movement.
  • Fig. 1 is a solely for the clockwise rotation configurable tes rotary impact mechanism with a trained as Nockenmechanis ⁇ adjusting mechanism in a position at the beginning of an increased torque demand by a tool shaft,
  • Fig. 3 is a schematic representation of essential components of a rotary impact mechanism, which can perform both a left and a right direction of rotation rotational shocks with an axial force component.
  • the rotary impact mechanism can also be designed as Schrägnuten-, in particular V-Nutenschlagwerk, or as a pulse impact mechanism. Further control or adjustment mechanisms are also conceivable.
  • the formation of the rotary impact mechanism as a V-groove impact mechanism would have the advantage that the energy stored in the rotational impact weight can accelerate quasi-free from the drive motor by a spring in the wire direction. In a cam follower described by way of example below, part of the stored energy is used to accelerate the drive motor.
  • the rotary impact mechanism 1 shown in FIG. 1 comprises a tool shaft 2, at the upper, free end of the drawing plane, for example, a drill chuck with a drill tool is arranged.
  • a rotary impact weight 3 is arranged which is provided with an outer longitudinal toothing 4.
  • a drive motor not shown, whose motor shaft is formed with a longitudinal toothing 4 conforming to the longitudinal toothing, which is engaged with the longitudinal teeth 4 of the rotary impact weight 3 (not shown), the rotational impact weight 3 in the direction of arrow 5 (left-handed) driven.
  • a cam disc 6 with cam 7 sits on the camshaft 18 in a rotationally fixed manner.
  • the rotational impact weight 3 is supported on the cam disc 6 by a ball 8, the rotational impact weight 3 being actuated by means of a restoring spring 9, which is rotationally fixed on the tool shaft 2 arranged anvil 10 (anvil disk) and the other end at one Ring shoulder 11 of the rotary impact weight 3 is supported in the axial direction on the cam 6 spring force.
  • the driven, further rotating rotational impact weight 3 is pressed by rolling the ball 8 via the cam 7 against the spring force of the return spring 9 on the camshaft 18 forward in the direction of arrow 19.
  • an oblique hammer surface 15 of the rotary impact weight 3 strikes an anvil surface 16 of the anvil 10.
  • the hammer surface 15 is approximately 45 ° relative to a plane E orthogonal to the axis of rotation 13 and through the anvil 10 ° inclined.
  • the positive connection between the camshaft 18 and the tool shaft 2 is preferably formed such that the positive engagement in the axial movement of the tool shaft 2 and the axially differently mounted camshaft 18 does not solve.
  • Fig. 2 it is shown how the inclined at an angle ⁇ of about 45 ° to the plane E hammer surface 15 and the plane E at an angle ß of about 135 ° inclined anvil surface 16 abut each other.
  • Fig. 3 only a section of the tool shaft 2 with anvil 10 and a section of the rotary impact weight 3 is shown.
  • the rotational impact weight 3 has two mutually oppositely inclined hammer surfaces 15, both of which enclose with the plane E an angle ⁇ of about 65 °.
  • the anvil 10 is provided with two mutually oppositely inclined hammer surfaces 16 which each span with the plane E an angle ß of about 115 °.
  • the angular relationship ⁇ 180 ° - ß applies here.
  • the rotary impact mechanism 1 shown can both left and also an anti-clockwise axial impact pulse to the tool shaft 2 generating operated.

Landscapes

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

Abstract

The invention relates to a rotary percussion mechanism (1) for an electric tool, having a drivable rotary percussion weight (3) with at least one hammer surface (15), and having an anvil (16) that can be rotated with the rotary percussion weight (3) about a common rotational axis (13) and is operatively connected to a tool shaft (2) to transmit torque, said anvil having at least one anvil surface (16). Said rotary percussion mechanism also has a displacement mechanism comprising a return spring (9), said mechanism being designed to cause a combined relative motion in the axial and circumferential directions under tension of the return spring (9) between the rotary percussion weight (3) and the anvil (10), resulting in a percussion effect of the hammer surface (15) on the anvil surface (16) in the circumferential direction, when the tool shaft (2) demands increased torque. According to the invention, the tool shaft (2) is axially displaceably supported, and the anvil surface (16) and/or the hammer surface (15) is/are aligned and/or designed such that a percussion of the hammer surface (15) on the anvil surface (16) results in a displacement of the tool shaft (2) in the axial direction, in addition to a rotary impulse on the tool shaft (2) in the circumferential direction.

Description

Beschreibungdescription
DrehschlagwerkRotary percussion
Stand der TechnikState of the art
Die Erfindung betrifft ein Drehschlagwerk für ein Elektro- werkzeug, insbesondere ein Elektrohandwerkzeug gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a rotary impact mechanism for an electric tool, in particular an electric hand tool according to the preamble of claim 1.
Derartige Drehschlagwerke werden ausschließlich in Im- pulsschraubern und Drehschlagschraubern (Schlagschraubern) eingesetzt. Ein Beispiel für einen Drehschlagschrauber mit einem Drehschlagwerk ist in der DE 147 88 09 offenbart. Bei Drehschlagantrieben wird zwischen drei Grundtypen, nämlich Nockenschlagwerken, V-Nutenschlagwerken und hydraulischen Impulsschlagwerken unterschieden. Drehschlagwerke ermöglichen die Freisetzung hoher Drehmomente bei relativ geringem Leistungseinsatz auf nahezu rückdrehmomentsfreie Weise. Weiterhin zeichnen sie sich dadurch aus, dass sie die kontinuierliche Leistungsabgabe des Antriebsmotors in einen schlagförmigen Drehimpuls umwandeln, wobei die Energieabgabe des Motors in einem Drehschlaggewicht zwischengespeichert wird und schlagartig mittels eines Impulses hoher Leistungsintensität an einem drehfest auf einer ein Schraubwerkzeug tragenden Werkzeugwelle angeordneten Amboss weitergegeben wird. Ein weiterer Vorteil von Drehschlagwerken ist, dass diese kompakt zu bauen und kostengünstig herstellbar sind.Such rotary impact devices are used exclusively in helicopters and rotary impact wrenches (impact wrenches). An example of a rotary impact wrench with a rotary impact mechanism is disclosed in DE 147 88 09. With rotary impact drives, a distinction is made between three basic types, namely cam followers, V-groove impactors and hydraulic pulse impactors. Rotary tappets enable the release of high torques with relatively low power input in almost torque-free manner. Furthermore, they are characterized by the fact that they convert the continuous power output of the drive motor in a punch-shaped angular momentum, the energy output of the engine is stored in a rotational impact weight and abruptly transmitted by means of a pulse of high power intensity on a non-rotatably mounted on a tool shaft supporting a screwing anvil , Another advantage of rotary impact is that they are compact and inexpensive to produce.
In Schlagbohrmaschinen werden meist Rastenschlagwerke eingesetzt, die im Gegensatz zum Drehschlagwerk keinen Drehimpuls in Umfangsrichtung auf die Werkzeugwelle erzeu- gen, sondern ausschließlich einen Verstellimpuls in axialer Richtung. Rastenschlagwerke haben den Vorteil, dass sie äußerst einfach aufgebaut und kostengünstig herstellbar sind. In der Praxis erweisen sich diese jedoch als wenig effektiv (geringe Schlagkraft) . Leistungsfähigere mechanische Schlagwerke für Schlagbohrmaschinen sind beispielsweise sogenannte Massenschlagwerke, deren Aufbau jedoch sehr komplex ist und diese daher nur kostenintensiv herstellbar und montierbar sind.Impact drills usually use detent impact devices, which in contrast to the rotary impact mechanism do not produce any angular momentum in the circumferential direction on the tool shaft. conditions, but only an adjustment pulse in the axial direction. Rastenschlagwerke have the advantage that they are extremely simple and inexpensive to produce. In practice, however, these prove to be less effective (low impact). More powerful mechanical percussion for impact drills, for example, so-called mass impact, the structure of which is very complex and they are therefore expensive to produce and assemble.
Offenbarung der Erfindung Technische AufgabeDISCLOSURE OF THE INVENTION Technical Problem
Der Erfindung liegt daher die Aufgabe zugrunde, ein Dreh- Schlagwerk für den Einsatz in einer Schlagbohrmaschine zu modifizieren .The invention is therefore based on the object to modify a rotary striking mechanism for use in a percussion drill.
Technische LösungTechnical solution
Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen auch sämtliche Kombinationen aus zumindest zwei der in der Beschreibung, den Ansprüchen und/oder den Figuren angegebenen Merkmalen.This object is achieved with the features of claim 1. Advantageous developments of the invention are specified in the subclaims. All combinations of at least two of the features specified in the description, the claims and / or the figures also fall within the scope of the invention.
Der Erfindung liegt der Gedanke zugrunde, die mindestens eine Hammerfläche und/oder die mindestens eine Ambossfläche derart auszurichten bzw. zu formen, dass durch den Schlag der Hammerfläche auf die Ambossfläche zusätzlich zu dem Drehimpuls in Umfangsrichtung eine in axialer Richtung auf die Werkzeugwelle wirkende Kraftkomponente erzeugt wird, die dafür sorgt, dass die in axialer Richtung verstellbar gelagerte Werkzeugwelle, die bevorzugt ein Bohrfutter mit Bohrwerkzeug trägt, in Richtung des zu bearbeitenden Werkstückes beschleunigt wird. Durch diese Modifikation gegenüber bekannten Drehschlagwerken kann das erfindungsgemäße Drehschlagwerk zum Erzeugen eines schlagenden Bohrervortriebs eingesetzt werden. Die Drehenergie des Drehschlaggewichtes wird dabei u.a. zur Erzeugung der axialen Kraftkomponente ausgenutzt. Die bevorzugt schräge oder gebogene Ausrichtung bzw. Ausformung der Hammerfläche und/oder der Ambossfläche sorgt dabei für eine Aufteilung des Drehimpulses in eine Axial- sowie in eine Umfangskomponente . Das erfindungsgemäße Drehschlagwerk ist äußerst leistungsstark und benötigt wenig Bauraum. Darüber hinaus ist das Drehschlagwerk kostengünstig herstellbar. Das beanspruchte Drehschlagwerk kann selbst ohne eine Getriebeübersetzung vorsehen zu müssen einen großen Drehzahlbereich bei gleichzeitig hohen Drehmomenten abdecken und arbeitet dabei effizient und rückschlagsarm, selbst in harten Baustoffen wie Beton oder Gestein. Die Bohrwirkung wird dabei zusätzlich zu dem Axialschlag von der in Umfangsrichtung wirkenden Schlagkomponente unterstützt.The invention is based on the idea of aligning or shaping the at least one hammer surface and / or the at least one anvil surface in such a way that a force component acting on the tool shaft in the axial direction is generated by the impact of the hammer surface on the anvil surface in addition to the angular momentum in the circumferential direction will, which ensures that the adjustable in the axial direction stored tool shaft, which preferably carries a drill chuck with drilling tool, is accelerated in the direction of the workpiece to be machined. As a result of this modification compared with known rotary impact devices, the rotary impact mechanism according to the invention can be used to produce a striking drill driver. The rotational energy of the rotational impact weight is used, inter alia, for generating the axial force component. The preferred oblique or curved alignment or shaping of the hammer surface and / or the anvil surface thereby ensures a division of the angular momentum into an axial and a peripheral component. The rotary impact mechanism according to the invention is extremely powerful and requires little space. In addition, the rotary impact is inexpensive to produce. The claimed Drehschlagwerk can cover even without a gear ratio to cover a large speed range with high torque and works efficiently and kickback, even in hard building materials such as concrete or rock. The drilling action is supported in addition to the axial impact of the impact component acting in the circumferential direction.
Das Drehschlagwerk lässt sich mit allen bekannten Verstellmechanismen, wie beispielsweise einem Nocken-Mechanismus, einem Schrägnuten-Mechanismus, insbesondere einem V-Nuten- Mechanismus, oder einem insbesondere hydraulischen Impulsmechanismus, ausbilden.The rotary impact mechanism can be formed with all known adjustment mechanisms, such as a cam mechanism, a Schrägnuten mechanism, in particular a V-groove mechanism, or a particular hydraulic pulse mechanism.
Von Vorteil ist eine Ausführungsform, bei der bei einer er- höhten Drehmomentanforderung durch das Werkzeug bzw. durch die Werkzeugwelle und einer damit verbundenen Drehgeschwindigkeitsreduzierung der Werkzeugwelle mittels eines Verstellmechanismus eine Relativbewegung zwischen dem Dreh- schlaggewicht und dem Amboss, der bevorzugt dauerhaft drehmomentübertragend mit der Werkzeugwelle gekoppelt ist, insbesondere drehfest mit dieser verbunden ist, in axialer sowie in Umfangsrichtung bewirkt, wodurch aus der Drehbewe- gung des Drehschlaggewichtes heraus eine Kollision zwischen der Hammerfläche und der Ambossfläche provoziert wird. Bevorzugt ist die Werkzeugwelle derart, insbesondere zwischen zwei Axialanschlägen, axial verstellbar, dass durch einen Drehschlag eine Axialverstellung des Werkzeugs um mindes- tens zwei, vorzugsweise mindestens drei, insbesondere mindestens fünf Millimeter, oder mehr resultiert.An advantage is an embodiment in which, with an increased torque requirement by the tool or by the tool shaft and an associated reduction in rotational speed of the tool shaft by means of an adjustment mechanism, a relative movement between the rotary shaft impact weight and the anvil, which is preferably permanently coupled torque-transmitting with the tool shaft, in particular rotatably connected thereto, effected in the axial and circumferential direction, whereby from the rotational movement of the rotational impact weight out a collision between the hammer surface and the anvil surface is provoked. Preferably, the tool shaft is axially adjustable in such a way, in particular between two axial stops, that an axial displacement of the tool results by at least two, preferably at least three, in particular at least five millimeters, or more.
In Ausgestaltung der Erfindung ist mit Vorteil vorgesehen, dass die axiale Kraftkomponente auf die Werkzeugwelle da- durch erzielt wird, dass die Hammerfläche mit einer gedachten, orthogonal zur Drehachse der Werkzeugwelle und des Drehschlaggewichtes, insbesondere durch den Amboss, verlaufenden Ebene ein Winkel α ≠ 90° aufgespannt wird. Durch die Wahl des Winkels α kann dabei das Verhältnis zwischen Dreh- impuls und Axialimpuls eingestellt werden.In an embodiment of the invention is advantageously provided that the axial force component is achieved on the tool shaft by the fact that the hammer surface with an imaginary, orthogonal to the axis of rotation of the tool shaft and the rotary impact weight, in particular by the anvil, extending plane an angle α ≠ 90th ° is clamped. By selecting the angle α, the ratio between the angular momentum and the axial momentum can be set.
Zusätzlich oder alternativ ist in Weiterbildung der Erfindung vorgesehen, dass die Ambossfläche gegenüber der orthogonal zur Drehachse verlaufenden Ebene unter einem Winkel ß ≠ 90° geneigt ist, also mit dieser Ebene einen Winkel ß ≠ 90° einschließt.Additionally or alternatively, it is provided in a development of the invention that the anvil surface is inclined relative to the orthogonal to the axis of rotation plane at an angle ß ≠ 90 °, ie with this plane an angle ß ≠ 90 °.
Zur Minimierung des Verschleißes von Hammerfläche und Ambossfläche ist es von Vorteil, wenn die WinkelbeziehungTo minimize the wear of the hammer surface and the anvil surface, it is advantageous if the angular relationship
α = 180°-ßα = 180 ° -β
gilt. Neben einer ebenen Ausbildung der Ambossfläche und/oder der Hammerfläche ist auch eine gekrümmte Ausbildung denkbar, wobei bevorzugt die Hammerfläche und die korrespondierende Ambossfläche in die gleiche Richtung und mit dem gleichen Krümmungsradius gekrümmt sind, also zumindest näherungsweise formkongruent ausgebildet sind.applies. In addition to a planar design of the anvil surface and / or the hammer surface and a curved training is conceivable, preferably the hammer surface and the corresponding anvil surface are curved in the same direction and with the same radius of curvature, that are at least approximately formed congruent.
Es hat sich als vorteilhaft herausgestellt, wenn der Winkel α zumindest näherungsweise aus einem Winkelbereich zwischen 5° und 85°, insbesondere zumindest näherungsweise zwischen 15° und 75°, vorzugsweise zumindest näherungsweise zwischen 25° und 65°, bevorzugt zwischen 35° und 55°, gewählt wird, oder besonders bevorzugt etwa 45° beträgt. Bei einem Winkel α von 45° wird dabei die Schlagenergie zumindest näherungsweise hälftig aufgeteilt zur Erzeugung eines Schlagimpulses in axialer Richtung sowie zur Erzeugung eines Schlagimpulses in Umfangsrichtung. Der Winkel ß beträgt dabei bevorzugt 180° - α.It has proven to be advantageous if the angle α at least approximately from an angular range between 5 ° and 85 °, in particular at least approximately between 15 ° and 75 °, preferably at least approximately between 25 ° and 65 °, preferably between 35 ° and 55 ° is selected, or more preferably about 45 °. At an angle α of 45 ° while the impact energy is at least approximately split in half to generate a shock pulse in the axial direction and to generate a shock pulse in the circumferential direction. The angle β is preferably 180 ° - α.
Zur Erhöhung der Schlagfrequenz ist mit Vorteil vorgesehen, dass der Amboss mehrere in die gleiche Richtung geneigte Ambossflächen und/oder das Drehschlaggewicht mehrere in die gleiche Richtung geneigte Hammerflächen aufweist.In order to increase the impact frequency, it is advantageously provided that the anvil has a plurality of anvil surfaces inclined in the same direction and / or the rotational impact weight has a plurality of hammer surfaces inclined in the same direction.
Um sowohl bei einem in eine linke Drehrichtung angetriebenen Drehschlaggewicht als auch bei einem in eine rechte Drehrichtung angetriebenen Drehschlaggewicht eine Schlagwirkung in axialer Richtung, d.h. einen Schlagimpuls auf die Werkzeugwelle in axialer Richtung, zu realisieren, ist es von Vorteil, wenn der Amboss zumindest zwei in einander entgegengesetzte Richtungen geneigte Ambossflächen und/oder das Drehschlaggewicht zumindest zwei in einander entgegen- gesetzte Richtungen geneigte Hammerflächen aufweist. Bevorzugt befinden sich beide einander entgegengesetzt geneigte Ambossflächen sowie beide einander entgegengesetzt geneigte Hammerflächen an jeweils einem Axialvorsprung des Ambosses bzw. des Drehschlaggewichts.In order to realize a hammering action in the axial direction, ie a shock pulse on the tool shaft in the axial direction, both in a rotational speed driven in a left direction of rotation as well as a driven in a right direction of rotation rotational impact, it is advantageous if the anvil at least two in opposing directions inclined anvil surfaces and / or the rotational impact weight at least two in opposite set directions has inclined hammer surfaces. Preferably, both mutually oppositely inclined anvil surfaces and both mutually oppositely inclined hammer surfaces are each at an axial projection of the anvil and the rotational impact weight.
Um das Verhältnis zwischen Axialschlagimpuls und Umfangs- schlagimpuls variieren zu können, ist es von Vorteil, wenn mindestens ein Verstellmechanismus zur Variation des Win- kels α oder des Winkels ß vorgesehen ist. Bevorzugt ist dieser Verstellmechanismus derart ausgebildet, dass auch ein Winkel α und/oder ein Winkel ß von zumindest näherungsweise 90° einstellbar ist, so dass kein axialer Schlagimpuls auf die Werkzeugwelle resultiert und das mit dem Dreh- Schlagwerk ausgestattete Elektrowerkzeug als Drehschlagschrauber einsetzbar ist.In order to be able to vary the ratio between the axial impact pulse and the peripheral impact pulse, it is advantageous if at least one adjusting mechanism is provided for varying the angle α or the angle β. Preferably, this adjustment mechanism is designed such that an angle α and / or an angle ß of at least approximately 90 ° is adjustable, so that no axial impact pulse results on the tool shaft and equipped with the rotary percussion power tool can be used as a rotary impact wrench.
Mit Vorteil ist eine weitere Ausgestaltungsform des Drehschlagwerks, bei der der Verstellmechanismus blockierbar bzw. überbrückbar ist, bevorzugt derart, dass bei einer erhöhten Drehmomentanforderung durch die Werkzeugwelle kein Schlagimpuls ausgelöst wird. Durch diese Weiterbildung ist es möglich, ein mit dem Drehschlagwerk ausgestattetes Elektrowerkzeug im reinen Bohrbetrieb (reiner Drehbetrieb) ohne Hammerbetätigung einzusetzen.Advantageously, another embodiment of the rotary impact mechanism, in which the adjusting mechanism can be blocked or bridged, preferably such that at an increased torque request by the tool shaft no impact pulse is triggered. With this development, it is possible to use a power tool equipped with the rotary impact mechanism in the pure drilling operation (pure rotary operation) without hammer operation.
Von Vorteil ist eine Konstruktion, bei der die Werkzeugwelle, insbesondere zusammen mit dem Amboss mittels einer, insbesondere als Schraubenfeder ausgebildeten, Feder in Richtung auf einen Axialanschlag federkraftbeaufschlagt ist, wobei der Axialanschlag bevorzugt an dem dem freien Ende der Werkzeugwelle gegenüberliegenden Ende angeordnet ist. Die Feder dient dabei als Rückstellfeder zum Verstel- len der Werkzeugwelle in ihre Ausgangsposition nach voll- führter Axialbewegung.Advantageous is a construction in which the tool shaft, in particular together with the anvil by means of a spring, in particular designed as a helical spring in the direction of an axial stop is subjected to spring force, wherein the axial stop is preferably arranged at the opposite end of the free end of the tool shaft. The spring serves as a return spring for adjusting the tool shaft to its starting position after full axial movement.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen; diese zeigen in:Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings; these show in:
Fig. 1 ein ausschließlich für den Linkslauf konfigurier- tes Drehschlagwerk mit einem als Nockenmechanis¬ mus ausgebildeten Verstellmechanismus in einer Position zu Beginn einer erhöhten Drehmomentanforderung durch eine Werkzeugwelle,Fig. 1 is a solely for the clockwise rotation configurable tes rotary impact mechanism with a trained as Nockenmechanis ¬ adjusting mechanism in a position at the beginning of an increased torque demand by a tool shaft,
Fig. 2 das Drehschlagwerk gemäß Fig. 1 in einer Position, in der das Drehschlaggewicht mit seiner Hammerfläche einen Schlag in Umfangsrichtung gegen eine Ambossfläche des drehfest mit der Werk¬ zeugwelle verbundenen Ambosses ausübt, und1 in a position in which the rotational impact weight with its hammer surface a stroke in the circumferential direction against an anvil surface of rotatably connected to the work ¬ generating shaft anvil exerts, and
Fig. 3 eine schematische Darstellung wesentlicher Komponenten eines Drehschlagwerkes, welches sowohl bei einer linken als auch bei einer rechten Drehrichtung Drehschläge mit einer Axialkraftkomponente ausführen kann.Fig. 3 is a schematic representation of essential components of a rotary impact mechanism, which can perform both a left and a right direction of rotation rotational shocks with an axial force component.
Ausführungsformen der ErfindungEmbodiments of the invention
In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet . In den Figuren ist ein als Nockenschlagwerk ausgebildetes Drehschlagwerk gezeigt. Alternativ kann das Drehschlagwerk auch als Schrägnuten-, insbesondere V-Nutenschlagwerk, oder als Impulsschlagwerk ausgebildet werden. Weitere Steuer- bzw. Verstellmechanismen sind ebenfalls denkbar. Die Ausbildung des Drehschlagwerks als V-Nuten-Schlagwerk hätte den Vorteil, dass die in dem Drehschlaggewicht gespeicherte Energie quasi frei vom Antriebsmotor von einer Feder in Drahtrichtung beschleunigen kann. Bei einem im Folgenden exemplarisch beschriebenen Nockenschlagwerk wird ein Teil der gespeicherten Energie zur Beschleunigung des Antriebsmotors verwendet.In the figures, the same components and components with the same function with the same reference numerals. In the figures, designed as a cam impact turning device is shown. Alternatively, the rotary impact mechanism can also be designed as Schrägnuten-, in particular V-Nutenschlagwerk, or as a pulse impact mechanism. Further control or adjustment mechanisms are also conceivable. The formation of the rotary impact mechanism as a V-groove impact mechanism would have the advantage that the energy stored in the rotational impact weight can accelerate quasi-free from the drive motor by a spring in the wire direction. In a cam follower described by way of example below, part of the stored energy is used to accelerate the drive motor.
Das in Fig. 1 gezeigte Drehschlagwerk 1 umfasst eine Werk- zeugwelle 2, an deren in der Zeichnungsebene oberen, freien Ende beispielsweise ein Bohrfutter mit einem Bohrerwerkzeug angeordnet ist. Koaxial zu einer mit der Werkzeugwelle 2 fluchtenden und mit der Werkzeugwelle 2 formschlüssig verbundenen Nockenwelle 19 ist ein Drehschlaggewicht 3 ange- ordnet, das mit einer äußeren Längsverzahnung 4 versehen ist. Mittels eines nicht gezeigten Antriebsmotors, dessen Motorwelle mit einer zur Längsverzahnung 4 formkongruenten Längsverzahnung ausgebildet ist, die mit der Längsverzahnung 4 des Drehschlaggewichts 3 in Eingriff steht (nicht gezeigt) , wird das Drehschlaggewicht 3 in Pfeilrichtung 5 (linksdrehend) angetrieben.The rotary impact mechanism 1 shown in FIG. 1 comprises a tool shaft 2, at the upper, free end of the drawing plane, for example, a drill chuck with a drill tool is arranged. Coaxially with a camshaft 19 which is aligned with the tool shaft 2 and is positively connected with the tool shaft 2, a rotary impact weight 3 is arranged which is provided with an outer longitudinal toothing 4. By means of a drive motor, not shown, whose motor shaft is formed with a longitudinal toothing 4 conforming to the longitudinal toothing, which is engaged with the longitudinal teeth 4 of the rotary impact weight 3 (not shown), the rotational impact weight 3 in the direction of arrow 5 (left-handed) driven.
Auf der Nockenwelle 18 sitzt drehfest eine Nockenscheibe 6 mit Nocken 7. Über eine Kugel 8 stützt sich das Drehschlag- gewicht 3 an der Nockenscheibe 6 ab, wobei das Drehschlaggewicht 3 mittels einer Rückstellfeder 9, die sich eine- nends an einem drehfest auf der Werkzeugwelle 2 angeordneten Amboss 10 (Ambossscheibe) und anderenends an einer Ringschulter 11 des Drehschlaggewichtes 3 abstützt in axialer Richtung auf die Nockenscheibe 6 federkraftbeaufschlagt .A cam disc 6 with cam 7 sits on the camshaft 18 in a rotationally fixed manner. The rotational impact weight 3 is supported on the cam disc 6 by a ball 8, the rotational impact weight 3 being actuated by means of a restoring spring 9, which is rotationally fixed on the tool shaft 2 arranged anvil 10 (anvil disk) and the other end at one Ring shoulder 11 of the rotary impact weight 3 is supported in the axial direction on the cam 6 spring force.
Solange die Werkzeugwelle 2 (mit Bohrwerkzeug) keinen größeren Widerstand bietet, reicht die Vorspannkraft der Rückstellfeder 9 aus, dass das Drehschlaggewicht 3 über die Kugel 8 die Nockenscheibe 6 und damit die Nockenwelle 18 und somit die Werkzeugwelle 2 in Pfeilrichtung 12 dreht (Links- drehrichtung) . Dabei drehen Drehschlaggewicht 3, Werkzeugwelle 2 und Nockenwelle 18 um eine gemeinsame Drehachse 13.As long as the tool shaft 2 (with drilling tool) offers no major resistance, the biasing force of the return spring 9 is sufficient that the rotary impact weight 3 on the ball 8, the cam 6 and thus the camshaft 18 and thus the tool shaft 2 rotates in the direction of arrow 12 (left-hand rotation ). Rotational impact weight 3, tool shaft 2 and camshaft 18 rotate about a common axis of rotation 13.
Steigt der Widerstand beim Bohren an, erhöht sich also die Drehmomentanforderung der Werkzeugwelle 2, dann reduziert sich die Rotationsgeschwindigkeit der Werkzeugwelle 2 und aufgrund des Formschlusses mit der Nockenwelle 18, auch die Rotationsgeschwindigkeit der Nockenwelle 18, wodurch diese ggf. sogar zum Stillstand kommen. Das angetriebene, weiterdrehende Drehschlaggewicht 3 wird durch Abwälzen der Kugel 8 über die Nocke 7 gegen die Federkraft der Rückstellfeder 9 auf der Nockenwelle 18 nach vorne in Pfeilrichtung 19 gedrückt. Erreicht dabei die Kugel 8 die vordere Kante 14 des Nockens 7, schlägt eine schräge Hammerfläche 15 des Drehschlaggewichtes 3 auf eine Ambossfläche 16 des Ambosses 10. Die Hammerfläche 15 ist gegenüber einer orthogonal zur Drehachse 13 und durch den Amboss 10 verlaufenden Ebene E um etwa 45° geneigt. Die Ambosflache schließt mit der Ebene E ein Winkel ß = 180°- 45° = 135° ein. Durch die Neigung der Flächen 15, 16 erfährt der Amboss 10 und damit die Werkzeugwelle 2 nicht nur einen Drehimpuls in Umfangsrich- tung (Pfeilrichtungen 5, 12), sondern auch in axialer Richtung 17, wodurch die Werkzeugwelle 2 in axialer Richtung 17 verstellt wird und somit auf das zu bearbeitende Werkstück ein Axialschlag ausgeübt wird.Increases the resistance during drilling, so increases the torque requirement of the tool shaft 2, then reduces the rotational speed of the tool shaft 2 and due to the positive connection with the camshaft 18, and the rotational speed of the camshaft 18, thereby possibly even come to a standstill. The driven, further rotating rotational impact weight 3 is pressed by rolling the ball 8 via the cam 7 against the spring force of the return spring 9 on the camshaft 18 forward in the direction of arrow 19. When the ball 8 reaches the front edge 14 of the cam 7, an oblique hammer surface 15 of the rotary impact weight 3 strikes an anvil surface 16 of the anvil 10. The hammer surface 15 is approximately 45 ° relative to a plane E orthogonal to the axis of rotation 13 and through the anvil 10 ° inclined. The anvil surface encloses with the plane E an angle ß = 180 ° - 45 ° = 135 °. Due to the inclination of the surfaces 15, 16, the anvil 10 and thus the tool shaft 2 undergoes not only an angular momentum in the circumferential direction (arrows 5, 12), but also in the axial direction 17, whereby the tool shaft 2 in the axial direction 17 is adjusted and thus an axial impact is exerted on the workpiece to be machined.
Der Formschluss zwischen Nockenwelle 18 und Werkzeugwelle 2 ist dabei bevorzugt derart ausgebildet, dass sich der Formschluss bei der Axialbewegung der Werkzeugwelle 2 und der axial unterschiedlich gelagerten Nockenwelle 18 nicht löst.The positive connection between the camshaft 18 and the tool shaft 2 is preferably formed such that the positive engagement in the axial movement of the tool shaft 2 and the axially differently mounted camshaft 18 does not solve.
Nach vollführtem Schlag werden das Drehschlaggewicht 3 und die Kugel 8 durch die Rückstellfeder 9 an der Rückseite 20 des Nockens 7 auf der Nockenscheibe 6 der Nockenwelle 18 wieder zurückgedrückt, so dass die Hammerfläche 15 sich an der Ambossfläche 16 vorbei drehen kann. Nach einer Umdrehung (bei einem Ein-Nocken-Schlagwerk) trifft das Dreh- schlaggewicht 3 wieder mittels seiner Kugel 8 auf die Nocke 7 der Nockenwelle 18, wodurch sich die beschriebene Folgesequenz wiederholt.After a completed blow the rotational impact weight 3 and the ball 8 are pushed back by the return spring 9 on the back 20 of the cam 7 on the cam 6 of the camshaft 18, so that the hammer surface 15 can rotate past the anvil surface 16 past. After one revolution (in the case of a single-cam impact mechanism), the rotary impact weight 3 hits the cam 7 of the camshaft 18 again by means of its ball 8, as a result of which the sequence described is repeated.
In Fig. 2 ist gezeigt, wie die unter einem Winkel α von etwa 45° zur Ebene E geneigte Hammerfläche 15 und die zur Ebene E unter einem Winkel ß von etwa 135° geneigte Ambossfläche 16 aneinander schlagen.In Fig. 2 it is shown how the inclined at an angle α of about 45 ° to the plane E hammer surface 15 and the plane E at an angle ß of about 135 ° inclined anvil surface 16 abut each other.
In Fig. 3 ist lediglich ein Ausschnitt der Werkzeugwelle 2 mit Amboss 10 sowie ein Ausschnitt des Drehschlaggewichtes 3 gezeigt. Zu erkennen ist, dass das Drehschlaggewicht 3 zwei einander entgegengesetzt geneigte Hammerflächen 15 aufweist, die beide mit der Ebene E einen Winkel α von etwa 65° einschließen. Entsprechend ist der Amboss 10 mit zwei einander entgegengesetzt geneigten Hammerflächen 16 versehen, die mit der Ebene E jeweils einen Winkel ß von etwa 115° aufspannen. Dabei gilt die Winkelbeziehung α = 180° - ß. Das gezeigte Drehschlagwerk 1 kann sowohl links- als auch rechtsdrehend einen axialen Schlagimpuls auf die Werkzeugwelle 2 erzeugend betrieben werden. In Fig. 3, only a section of the tool shaft 2 with anvil 10 and a section of the rotary impact weight 3 is shown. It can be seen that the rotational impact weight 3 has two mutually oppositely inclined hammer surfaces 15, both of which enclose with the plane E an angle α of about 65 °. Accordingly, the anvil 10 is provided with two mutually oppositely inclined hammer surfaces 16 which each span with the plane E an angle ß of about 115 °. The angular relationship α = 180 ° - ß applies here. The rotary impact mechanism 1 shown can both left and also an anti-clockwise axial impact pulse to the tool shaft 2 generating operated.

Claims

Ansprüche claims
1. Drehschlagwerk für ein Elektrowerkzeug, mit einem antreibbaren Drehschlaggewicht (3) mit mindestens einer Hammerfläche (15), und mit einem mit dem Drehschlaggewicht (3) um eine gemeinsame Drehachse (13) rotierbaren sowie mit einer Werkzeugwelle (2) drehmo- mentübertagend wirkverbundenen Amboss (10) mit mindes- tens einer Ambossfläche (16), auf die die Hammerfläche (15) in Umfangsrichtung schlagend einwirkend angeordnet ist, dadurch gekennzeichnet, dass die Werkzeugwelle (2) axial verstellbar gelagert ist, und dass die Ambossfläche (15) und/oder die Hammerfläche (16) derart ausgerichtet und/oder ausgebildet sind/ist, dass durch einen Schlag der Hammerfläche (15) auf die Ambossfläche (16) neben einem Drehimpuls auf die Werkzeugwelle (2) in Umfangsrichtung eine Ver- Stellung der Werkzeugwelle (2) in Axialrichtung (17) resultiert .1. Rotary impact mechanism for a power tool, with a drivable rotary impact weight (3) with at least one hammer surface (15), and with the Drehschlaggewicht (3) about a common axis of rotation (13) rotatable and with a tool shaft (2) operatively operatively connected torque Anvil (10) having at least one anvil surface (16) on which the hammer surface (15) is arranged to act in the circumferential direction, characterized in that the tool shaft (2) is mounted axially adjustable, and that the anvil surface (15) and / or the hammer surface (16) are aligned and / or formed such that a displacement of the hammer surface (15) on the anvil surface (16) in addition to an angular momentum on the tool shaft (2) in the circumferential direction a displacement of the tool shaft ( 2) in the axial direction (17) results.
2. Drehschlagwerk nach Anspruch 1, dadurch gekennzeichnet, dass das Drehschlagwerk (1) mit einem eine Rückstellfeder (9) aufweisenden Verstellmechanismus versehen ist, der bei einer erhöhten Drehmomentanforderung der Werkzeugwelle (2) unter Spannung der Rückstellfeder (9) zwischen dem Drehschlaggewicht (3) und dem Amboss (10) eine kombinierte Relativbewegung in axialer sowie in Umfangsrichtung und in der Folge die Schlagwirkung der Hammerfläche (15) in Umfangsrichtung auf die Ambossfläche (16) bewirkend ausgebildet ist. 2. Rotary impact mechanism according to claim 1, characterized in that the rotary impact mechanism (1) having a return spring (9) having adjusting mechanism is provided at an increased torque requirement of the tool shaft (2) under tension of the return spring (9) between the rotational impact weight (3 ) and the anvil (10) a combined relative movement in the axial and in the circumferential direction and in consequence the impact of the hammer surface (15) in the circumferential direction on the anvil surface (16) is formed effecting.
3. Drehschlagwerk nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass die Ambossfläche (15) gegenüber einer orthogonal zur Drehachse (13) verlaufenden Ebene (E) unter einem Winkel (α) von ungleich 90° geneigt ist.3. Rotary impact mechanism according to one of claims 1 or 2, characterized in that the anvil surface (15) relative to a plane orthogonal to the rotation axis (13) extending plane (E) at an angle (α) of not equal to 90 ° inclined.
4. Drehschlagwerk nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Ambossfläche (16) gegenüber der orthogonal zur Drehachse (13) verlaufenden Ebene (E) unter einem Winkel (ß) von ungleich 90° geneigt ist.4. Rotary impact mechanism according to one of claims 1 to 3, characterized in that the anvil surface (16) with respect to the orthogonal to the axis of rotation (13) extending plane (E) at an angle (ß) of not equal to 90 ° inclined.
5. Drehschlagwerk nach Anspruch 4, dadurch gekennzeichnet, dass zumindest näherungsweise gilt α = 180° - ß.5. Rotary impact mechanism according to claim 4, characterized in that at least approximately α = 180 ° - ß.
6. Drehschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Winkel α zwischen der Hammerfläche (15) und der orthogonal zur Drehachse (13) verlaufenden Ebene (E) zumindest näherungsweise zwischen 5° und 85°, insbesondere zumindest näherungsweise zwischen 15° und 75°, vorzugsweise zumindest näherungsweise zwischen 25° und 65°, bevorzugt zwischen 35° und 55°, besonders bevorzugt etwa 45° beträgt.6. Rotary impact mechanism according to one of the preceding claims, characterized in that the angle α between the hammer surface (15) and the orthogonal to the axis of rotation (13) extending plane (E) at least approximately between 5 ° and 85 °, in particular at least approximately between 15 ° and 75 °, preferably at least approximately between 25 ° and 65 °, preferably between 35 ° and 55 °, more preferably about 45 °.
7. Drehschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Winkel (ß) zwischen der Ambossfläche (16) und der orthogonal zur Drehachse (13) verlaufenden Ebene (E) zumindest näherungsweise zwischen 95° und 175°, insbesondere zumindest näherungsweise zwischen 105° und 165°, vorzugsweise zumindest näherungsweise zwischen 115° und 155°, bevorzugt zwischen 125° und 145°, besonders bevorzugt etwa 135° beträgt.7. Rotary impact mechanism according to one of the preceding claims, characterized in that the angle (ß) between the anvil surface (16) and the orthogonal to the rotation axis (13) extending plane (E) at least approximately between 95 ° and 175 °, in particular at least approximately between 105 ° and 165 °, preferably at least approximately between 115 ° and 155 °, preferably between 125 ° and 145 °, particularly preferably about 135 °.
8. Drehschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Amboss (10) mehrere in die gleiche Richtung geneigte Ambossflächen (16) und/oder das Drehschlaggewicht (3) mehrere in die gleiche Richtung geneigte Hammerflächen (15) aufweist.8. Rotary impact mechanism according to one of the preceding claims, characterized in that the anvil (10) has a plurality of inclined in the same direction anvil surfaces (16) and / or the rotary impact weight (3) a plurality of inclined in the same direction hammer surfaces (15).
9. Drehschlagwerk nach einem der vorhergehenden Ansprü- che, dadurch gekennzeichnet, dass der Amboss (10) zumindest zwei in einander entgegengesetzte Richtungen geneigte Ambossflächen (16) und/oder das Drehschlaggewicht (3) zumindest zwei in einander entgegengesetzte Richtungen geneigte Hammerflächen (15) aufweist.9. Rotary impact mechanism according to one of the preceding claims, characterized in that the anvil (10) at least two inclined in opposite directions anvil surfaces (16) and / or the rotary impact weight (3) at least two in opposite directions inclined hammer surfaces (15) having.
10. Drehschlagwerk nach einem der Ansprüche 3 bis 9, dadurch gekennzeichnet, dass der Winkel (α) und/oder der Winkel (ß) mittels eines Verstellmechanismus verstellbar sind/ist.10. rotary impact mechanism according to one of claims 3 to 9, characterized in that the angle (α) and / or the angle (ß) are adjustable by means of an adjusting / is.
11. Drehschlagwerk nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, dass eine Blockiereinrichtung zum Ausserkraftsetzen und/oder eine Überbrückungseinrichtung zum Überbrücken des Verstellmechanismus vorgesehen ist. 11. Rotary impact mechanism according to one of claims 2 to 10, characterized in that a blocking device for override and / or a bridging device is provided for bridging the adjusting mechanism.
12. Drehschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Werkzeugwelle (2) mittels einer Feder in Richtung einer Nockenwelle (18) federkraftbeaufschlagt ist . 12. Rotary impact mechanism according to one of the preceding claims, characterized in that the tool shaft (2) by means of a spring in the direction of a camshaft (18) is spring-loaded.
EP08708789A 2007-03-28 2008-02-07 Rotary percussion mechanism Not-in-force EP2132005B1 (en)

Applications Claiming Priority (2)

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DE102007014757A DE102007014757A1 (en) 2007-03-28 2007-03-28 Rotary percussion
PCT/EP2008/051509 WO2008116691A1 (en) 2007-03-28 2008-02-07 Rotary percussion mechanism

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EP2132005B1 EP2132005B1 (en) 2012-05-02

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DE (1) DE102007014757A1 (en)
ES (1) ES2382497T3 (en)
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CN103213103B (en) * 2012-01-19 2015-07-15 南京德朔实业有限公司 Fastener tool
US9272400B2 (en) * 2012-12-12 2016-03-01 Ingersoll-Rand Company Torque-limited impact tool
EP2759378B1 (en) * 2013-01-28 2015-11-04 Chervon (HK) Limited A multi-tool for fasteners
JP2015024474A (en) * 2013-07-26 2015-02-05 日立工機株式会社 Impact tool
DE102016203389A1 (en) * 2016-03-02 2017-09-07 Robert Bosch Gmbh Mechanical rotary impact mechanism for a hand tool machine

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US2049273A (en) 1932-10-06 1936-07-28 Robert H Pott Impact tool
FR1057422A (en) * 1952-05-27 1954-03-08 Tightening wrench
US2940565A (en) * 1956-05-14 1960-06-14 Schodeberg Carl Theodore Power driven impact tool
DE1478809A1 (en) 1962-09-15 1969-02-20 Bosch Gmbh Robert Motor-driven impact wrench
US20060024141A1 (en) 2004-07-30 2006-02-02 Hilti Aktiengesellschaft Power tool with an intermittent angular torque pulse

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EP2132005B1 (en) 2012-05-02

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