EP1281483B1 - Marteau rotatif - Google Patents

Marteau rotatif Download PDF

Info

Publication number
EP1281483B1
EP1281483B1 EP20010118236 EP01118236A EP1281483B1 EP 1281483 B1 EP1281483 B1 EP 1281483B1 EP 20010118236 EP20010118236 EP 20010118236 EP 01118236 A EP01118236 A EP 01118236A EP 1281483 B1 EP1281483 B1 EP 1281483B1
Authority
EP
European Patent Office
Prior art keywords
crank
gear
hammer drill
drill according
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20010118236
Other languages
German (de)
English (en)
Other versions
EP1281483A3 (fr
EP1281483A2 (fr
Inventor
Roland Vögele
Rainer Kumpf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Techtronic Industries GmbH
Original Assignee
AEG Electric Tools GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by AEG Electric Tools GmbH filed Critical AEG Electric Tools GmbH
Priority to DE50113888T priority Critical patent/DE50113888D1/de
Priority to EP20010118236 priority patent/EP1281483B1/fr
Publication of EP1281483A2 publication Critical patent/EP1281483A2/fr
Publication of EP1281483A3 publication Critical patent/EP1281483A3/fr
Application granted granted Critical
Publication of EP1281483B1 publication Critical patent/EP1281483B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • 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
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism

Definitions

  • the invention relates to a rotary hammer or chisel hammer with the features according to the preamble of claim 1.
  • a hammer drill is, for example US-A-2 638 325 known.
  • Rotary hammers or chisels for drilling in stone or concrete and for performing chiselling have a tool spindle for receiving a drill, a chisel or similar tools.
  • the longitudinally displaceable tool is acted upon by a percussion with blows in its longitudinal direction, whereby a chisel effect is achieved with the tool used.
  • a usually switched on or switched off executed rotary drive is provided for the generation of a rotational movement of the tool spindle in combination with the percussion to perform drilling.
  • the striking mechanism and the rotary drive are typically driven by a common drive motor.
  • the percussion includes a crank mechanism with a crankshaft and a connecting rod.
  • the connecting rod acts, for example via a spring and in particular by means of a piston on pneumatic way on the tool spindle.
  • the crank mechanism is driven by a spur gear, which requires a complex bearing of the crank mechanism because of the high mechanical load of the hammer mechanism.
  • a combination of radial and thrust bearings is provided for receiving the forces occurring and for fixing the individual parts in their predetermined position.
  • Corresponding bearing seats and / or bearing blocks hold the individual bearings.
  • the high number of items is costly. The assembly is expensive, the items are not fixed before the completion of the full installation and can fall out, for example, during maintenance.
  • the invention has for its object to provide a rotary hammer, which requires a reduced installation and maintenance in the field of its transmission.
  • the drive for the impact mechanism in the form of a gear pair, which consists of a bevel gear fixed to the crank and a bevel gear engaging in the bevel gear whose axes of rotation are at an angle, in particular at an approximately right angle to each other.
  • the crank wheel is mounted so as to be longitudinally displaceable by means of a radial shaft bearing.
  • the longitudinal displaceability of the crank wheel is limited in one direction by a thrust bearing and in the opposite direction by the bevel pinion.
  • the flying storage leads to a simple mountability by attaching the crank wheel to the storage.
  • the final determination of the crank wheel by mounting the drive motor.
  • Its bevel pinion acts as a thrust bearing and as a safeguard against axial slipping out of the crank wheel.
  • On the additional cost of a further axial storage or anti-skid can be dispensed with.
  • the bevel gear and the Kurbelradnabe are designed as two separate components to reduce the manufacturing costs, wherein the bevel gear is fixed to the Kurbelradnabe and in particular festgelötet.
  • the bevel pinion is appropriate directly on the drive shaft of the drive motor and engages directly into the bevel gear.
  • the bevel pinion is integrally formed with the drive shaft for ease of manufacture. As a result, the number of gear parts is kept small.
  • the above design contributes to the compact and lightweight design of the hammer drill.
  • the radial shaft bearing suitably comprises a needle bearing and is in particular designed as a pair of needle bearings.
  • a high bearing capacity is given low volume, especially for absorbing the impact loads from the percussion.
  • Under load needle bearings have a low elastic deformation, whereby repercussions on the mutual alignment of the gears in the drive are avoided. Due to the paired arrangement of two needle bearings in addition to a high radial stiffness and high rigidity in tilt direction is given.
  • the crank wheel is rotatably supported by means of the radial shaft bearing about a particular hollow executed, fixed housing stud bolts.
  • the shaft bearing can be arranged on the inside of the crank wheel in the region of the drive, the output and the crank mechanism.
  • the bearing has at least approximately no eccentricity compared to the forces acting, whereby the bearing forces and the deformations occurring are minimized.
  • a hollow design of the stud bolt a favorable ratio of weight to strength and rigidity is achieved.
  • a cast-in steel bushing for receiving the stud bolt is advantageously provided.
  • the Textilmetallguß of the gear housing leads to a high rigidity and insensitivity to shocks, wherein the cast-steel bushing initiates the concentrated bearing force in the stud bolt flat while avoiding voltage spikes in the light metal housing.
  • the pouring of the steel bushing leads in addition to a simple production and reliable power and heat transfer.
  • the stud bolt can be fixed with little effort, for example by pressing in the steel bushing.
  • the diameter of the housing-fixed stud in the region of the radial shaft bearing is smaller than the outer diameter of the cast-in socket.
  • the cast-in socket forms a shoulder, which can serve as Axialgleitlager or to support a separate thrust bearing.
  • the stud is pressed directly into the gear housing, wherein the diameter of the stud in the region of the radial shaft bearing is smaller than in the gear housing area. The thicker area of the stud for pressing into the gear housing takes in one-piece training, the function of the steel bushing was. In addition, a reduction of the items is given and a simplification of the assembly allows.
  • the drive motor via the crank mechanism of the striking mechanism in the rotary drive.
  • an output is provided in the region of the crank hub, via which the Kurbelradnabe acts on the tool spindle for generating the rotational movement.
  • the Kurbelradnabe is characterized a multifunction part in which branches the power flow in the direction of the impact mechanism and the rotary drive. This multifunctional part can be manufactured and assembled as a unit.
  • the crank mechanism of the impact mechanism and the rotary drive of the tool spindle can be mounted independently of the drive motor and brought into operative connection with each other. During maintenance work, the drive motor dismantled as a unit. In the case of the crank drive, which is still in engagement with the rotary drive, a functional check can be carried out manually.
  • the output is based on the crank pin of the crank mechanism in the direction of its axis of rotation on the same side of the Kurbelradnabe arranged as the drive. This allows a simply configured, based on the connecting rod unilateral bearing the Kurbelradnabe, the Kurbelradnabe can be mounted together with the storage without consideration of a connecting rod or a link control. On the additional design effort on both sides of the connecting rod arranged storage with an additional bearing block is omitted.
  • the drive motor acts directly on the Kurbelradnabe only, the required tolerances in the corresponding drive with little effort can be maintained.
  • the tolerance insensitivity leads not only to cost-effective manufacturability but also to a corresponding longevity.
  • the output in the region of the crank hub is expediently formed by a further pair of gears with two gears designed in particular as spur gears.
  • the gear pair has a high load capacity and low tolerance insensitivity.
  • the lying on the crank gear of the second gear pair is expediently formed integrally with the Kurbelradnabe, which in addition to reduced manufacturing costs, a high power transmission from the Kurbelradnabe on the gear even with small dimensions is possible.
  • an intermediate shaft is provided between the output and the tool spindle, on which the second gear of the gear pair is provided by the output.
  • a strong speed reduction of the tool spindle can be structurally predetermined, whereby relative to the spindle speed, a high impact frequency of the striking mechanism is adjustable. This allows a high drilling performance with low tool wear.
  • the arrangement of an intermediate shaft in conjunction with a strong reduction allows the choice of tooth pairings in a geometrically favorable range.
  • the intermediate shaft expediently comprises a torque-limiting safety clutch, via which the corresponding gearwheel is connected. The safety coupling in the intermediate shaft area requires no additional space. Inadvertent seizure of the drilling tool, only the rotary drive is interrupted.
  • the drilling tool can be worked out.
  • the power transmission from the intermediate shaft to the tool spindle is advantageously carried out via a bevel pinion on the intermediate shaft, which engages in a bevel gear on the tool spindle.
  • the rotary drive can be interrupted in a simple manner to use the hammer drill, for example, for chiselling.
  • the drive motor and the tool spindle are expediently arranged axially parallel to one another, resulting in an overall slim design of the hammer drill. Working even in confined spaces is relieved.
  • the center of gravity of the hammer drill is close to the axis of the tool spindle, whereby the hammer drill can be performed in impact operation with improved accuracy.
  • Fig. 1 shows a longitudinal sectional view of an overview of a 10kg hammer drill 1.
  • the hammer drill 1 has at the rear a drive motor 4, which is designed in the illustrated embodiment as an electric motor. It may also be provided a combustion, hydraulic or pneumatic motor.
  • a rotatable tool spindle 2 is mounted in a gear housing 5 in which an indicated tool 3, for example a drill, chisel or the like, is held. It is provided on the tool 3 acting percussion 6.
  • a crank mechanism 7 is mounted as part of the hammer mechanism 6, which is driven by the drive motor 4.
  • the crank mechanism 7 comprises a crank wheel 8, which is rotatable about a rotation axis 17.
  • the crank 8 Eccentric to the axis of rotation 17, the crank 8 has a crank pin 11 which is in engagement with a connecting rod 9.
  • a piston 32 is connected to the crank mechanism 7 and longitudinally displaceable oscillating drivable.
  • the piston 32 is guided in the hollow tool spindle 2 and generates by means of its oscillating movement an oscillating air pressure in the tool spindle 2.
  • the oscillating air pressure is pneumatically transmitted to a striker 33, which in turn strikes a striker 34 and thus over the striker 34 impact energy on the tool 3 applies.
  • Fig. 2 shows an enlarged view of the hammer drill 1 after Fig. 1 in the region of the crank mechanism 7 and the drive motor 4.
  • a transmission element 45 is provided between the crank wheel 8 and the piston 32.
  • the transmission element 45 is shown in FIG Embodiment, the connecting rod 9, but can also be designed, for example, as a linearly longitudinally displaceable link or the like.
  • the connecting rod 9 has a connecting rod 46, through which the crank pin 11 is guided.
  • the crank pin may be integrally formed with the crank hub 10 or another component of the crank wheel 8. In the illustrated embodiment, it is a separate item and engages with press-fit in an end-side retaining opening 47 of the crank hub 10th
  • a drive shaft 19 with an armature 35 is rotatably mounted in a rear ball bearing 36 and a front ball bearing 37 about a rotation axis 18.
  • the axis of rotation 18 of the drive shaft 19 is substantially perpendicular to the axis of rotation 17 of the crank wheel 8.
  • an arrangement in a different angle and, for example, an axially parallel arrangement may be appropriate.
  • the crank wheel 8 has a Kurbelradnabe 10, wherein between the Kurbelradnabe 10 and the drive motor 4, a drive 12 is provided, via which the drive motor 4 acts on the crank mechanism 7.
  • the drive 12 may be an intermediate gear, a worm gear, a belt drive or the like. Be and is formed in the embodiment shown by a gear pair 14. From the angular arrangement of the two axes of rotation 17, 18 to each other results in a conical configuration of the gear pair 14. In an axis-parallel arrangement are advantageously provided spur gears.
  • the gear pair 14 consists of a bevel gear 10 fixed to the bevel gear 15 and a bevel gear 15 engaging bevel gear 16.
  • the bevel gear 15 can be pressed with the bevel gear 10, screwed or the like. Be and is in the illustrated embodiment on the Kurbelradnabe 10th soldered.
  • the bevel pinion 16 may be mounted on an intermediate shaft or the like and is fixed in the illustrated embodiment to the drive shaft 19 of the drive motor, as a result, the drive motor 4 with his Drive shaft 19 engages over the bevel pinion 16 directly into the bevel gear 15.
  • the front ball bearing 37 of the drive shaft 19 is arranged in the immediate vicinity of the bevel pinion 16.
  • the crank wheel 8 is mounted by means of a radial shaft bearing 20 in the direction of its axis of rotation 17 longitudinally displaceable flying.
  • a thrust bearing 21 is provided on the conrod 9 side facing away from the radial shaft bearing 20 .
  • the longitudinal displacement of the crank wheel 8 is limited in one direction by this thrust bearing 21 and in the opposite direction by the bevel pinion 16.
  • the radial shaft bearing 20 is formed as a pair of needle bearings 22.
  • a housing-fixed hollow running stud 23 is provided, around which the crank wheel 8 is rotatably supported by means of the needle bearing 22.
  • crank wheel 8 with a pivot pin which engages in a bearing bush or the like.
  • the stud bolt 23 can be screwed into the gear housing 5, pressed or cast directly. In the illustrated embodiment, it is pressed into a steel bushing 24.
  • the steel bushing 24 in turn is cast in the gear housing 5 made of cast aluminum. It may also be expedient to press the steel bush 24 into the transmission housing 5.
  • materials for the transmission housing 5 other light metals such as magnesium or injection-molded plastic are suitable.
  • an output 13 is provided, via which the crank wheel hub 10 acts on the tool spindle 2 to produce a rotational movement.
  • the output 13 based on the connecting rod 9 in the direction of the axis of rotation 17, on the same side of the Kurbelradnabe 10 as the drive 12.
  • the output 13 may be a worm drive or the like.
  • a another gear pair 25 is in the illustrated embodiment a another gear pair 25.
  • the output 13 can act directly on the tool spindle 2.
  • an intermediate shaft 28 is provided, which is rotatably mounted about a substantially parallel to the axis of rotation 17 of the crank wheel 8 shaft shaft 42.
  • the gear pair 25 is formed in this embodiment of two gears designed as spur gears 26, 27. In an angular arrangement of the shaft axis 42 to the rotation axis 17, the gears 26, 27 are preferably formed as bevel gears.
  • the crank wheel side gear 26 of the gear pair 25 is integrally formed with the Kurbelradnabe 10.
  • the gear 27 on the side of the intermediate shaft 28 is designed as a separate component and fixed by a torque limiting safety clutch 29 on the intermediate shaft 28.
  • a bevel pinion 30 is formed, which engages in a bevel gear 31 on the tool spindle 2.
  • the tool spindle 2 has on the outside a toothing 38 on which the bevel gear 31 is rotatably mounted.
  • the intermediate shaft 28 has on its side facing away from the bevel pinion 30 a stub axle 44 which engages in a blind hole 43 in the gear housing 5 and is mounted there by means of needle bearings 40. It can also be a storage about a stud bolts comparable to the storage of the crank wheel 8 appropriate.
  • the spindle axis 41 of the tool spindle 2 and the axis of rotation 18 of the drive shaft 19 are arranged substantially parallel to each other. Perpendicular to this are the axis of rotation 17 of the crank wheel 8 and the shaft axis 42 of the intermediate shaft 28. Depending on the application, any other angular arrangements may be appropriate.
  • Fig. 3 shows a longitudinal sectional view of another embodiment of a hammer drill 1 with a rotatably mounted tool spindle 2, through which a tool 3 is rotatably driven.
  • an electric motor 4 is provided which drives a striking mechanism 6 and the bevel pinion 30 and the bevel gear 31, the tool spindle 2 rotationally.
  • the bevel gear 16 is formed integrally with the drive shaft 19 on the drive shaft 19 of the drive motor 4.
  • the stud bolt 23 is pressed into a ribbed, cast-in in the gear housing 5 steel bushing 24.
  • the steel bushing 24 may also be pressed into the transmission housing 5.
  • the steel bush 24 has a larger diameter than the stud bolt 23 in the region of the radial shaft bearing 20 for the Kurbelradnabe 10.
  • a thrust bearing 21 for the Kurbelradnabe 10 is designed as a sliding bearing and supported on the steel bushing 24 frontally.
  • the stud bolt 23 has a coaxial downwardly open bore 48 in the form of a blind hole.
  • the transmission housing 5 is suitably a Weinmetallguß- or plastic injection molding.
  • Fig. 4 shows in an enlarged detail the arrangement Fig. 3 In the region of the crank hub 10.
  • a variant of the stud 23 is provided, which has a radially enlarged paragraph 49 in the region of the gear housing 5, whose diameter is greater than the diameter of the stud 23 in the region of the radial shaft bearing 20.
  • the stud and the paragraph 49 are integrally formed, wherein the stud bolt 23 is pressed with the paragraph 49 in the transmission housing 5 directly.

Landscapes

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

Claims (14)

  1. Marteau perforateur (1) ou marteau-burineur comportant une broche d'outil (2) permettant de recevoir un outil (3), un moteur d'entraînement (4) et un mécanisme de percussion (6), logé dans un carter d'engrenage (5) et agissant sur l'outil (3), qui comprend une transmission à manivelle (7) avec une roue à manivelle (8) pouvant tourner autour d'un axe de rotation (17), la roue à manivelle (8) présentant un moyeu de roue à manivelle (10) et un maneton de manivelle (11) et un entraînement (12) étant prévu entre le moyeu de roue à manivelle (10) et le moteur d'entraînement (4), par le biais duquel le moteur d'entraînement (4) agit sur la transmission à manivelle (7), caractérisé en ce que l'entraînement (12) se compose d'une roue conique (15) fixée au niveau du moyeu de roue à manivelle (10) et d'un pignon conique (16) s'engrenant dans la roue conique (15), dont les axes de rotation (17, 18) sont disposés en angle les uns par rapport aux autres, et en ce que la roue à manivelle (8) est disposée en porte-à-faux de manière à se déplacer longitudinalement au moyen d'un palier d'arbre radial (20), la possibilité de déplacement longitudinal dans une direction par un palier axial (21) et dans la direction opposée par le pignon conique (16) est limitée.
  2. Marteau perforateur selon la revendication 1,
    caractérisé en ce que le palier d'arbre radial (20) comprend au moins un roulement à aiguilles (22) et est réalisé en particulier sous forme de paire de roulements à aiguilles (22).
  3. Marteau perforateur selon la revendication 1 ou 2,
    caractérisé en ce que la roue à manivelle (8) est logée de manière rotative autour d'un goujon (23) fixé au carter, en particulier creux, au moyen du palier d'arbre radial (20)
  4. Marteau perforateur selon la revendication 3,
    caractérisé en ce que le carter d'engrenage (5) est en métal léger, en particulier en aluminium ou en magnésium ou en plastique, dans lequel est coulé un coussinet en acier (24) pour la réception du goujon (23).
  5. Marteau perforateur selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que le diamètre du goujon (23) fixé au carter dans la zone du palier d'arbre radial (20) est inférieur au diamètre extérieur du coussinet coulé ou emmanché (24) .
  6. Marteau perforateur selon la revendication 3,
    caractérisé en ce que le goujon (23) est emmanché directement dans le carter d'engrenage (5), le diamètre du goujon (23) dans la zone du palier d'arbre radial (20) étant inférieur à celui dans la zone du carter d'engrenage.
  7. Marteau perforateur selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que le pignon conique (16) se trouve sur un arbre d'entraînement (19) du moteur d'entraînement (4) et s'engrène directement dans la roue conique (15), le pignon conique (16) étant réalisé en particulier d'un seul tenant avec l'arbre d'entraînement (19).
  8. Marteau perforateur selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que la roue conique (15) est reliée de manière solidaire en rotation au moyeu de roue à manivelle (10) et est en particulier brasée.
  9. Marteau perforateur selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce qu'une sortie (13) est prévue dans la zone du moyeu de roue à manivelle (10) par le biais de laquelle le moyeu de roue à manivelle (10) agit sur la broche d'outil (2) pour générer le mouvement de rotation, la sortie (13) en direction de l'axe de rotation (17) se trouvant par rapport au maneton de manivelle (11) du même côté du moyeu de roue à manivelle (10) que la sortie (12).
  10. Marteau perforateur selon la revendication 9,
    caractérisé en ce que la sortie (13) est formée par une deuxième paire de roues dentées (25) avec deux roues dentées (26, 27) réalisées en particulier sous forme de roues droites.
  11. Marteau perforateur selon la revendication 10,
    caractérisé en ce que la roue dentée (26) est réalisée d'un seul tenant avec le moyeu de roue à manivelle (10).
  12. Marteau perforateur selon l'une quelconque des revendications 1 à 11,
    caractérisé en ce qu'un arbre intermédiaire (28) qui comprend en particulier un accouplement de sûreté (29) limitant le couple est prévu avec la roue dentée (27) entre la sortie (13) et la broche d'outil (2).
  13. Marteau perforateur selon la revendication 12,
    caractérisé en ce qu'une roue conique (30), qui s'engrène dans une roue conique (31) au niveau de la broche d'outil (2) est prévue au niveau de l'arbre intermédiaire (28).
  14. Marteau perforateur selon l'une quelconque des revendications 1 à 13,
    caractérisé en ce que le moteur d'entraînement (4) et la broche d'outil (3) sont axialement parallèles l'un par rapport à l'autre.
EP20010118236 2001-07-30 2001-07-30 Marteau rotatif Expired - Lifetime EP1281483B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE50113888T DE50113888D1 (de) 2001-07-30 2001-07-30 Bohrhammer
EP20010118236 EP1281483B1 (fr) 2001-07-30 2001-07-30 Marteau rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20010118236 EP1281483B1 (fr) 2001-07-30 2001-07-30 Marteau rotatif

Publications (3)

Publication Number Publication Date
EP1281483A2 EP1281483A2 (fr) 2003-02-05
EP1281483A3 EP1281483A3 (fr) 2003-03-05
EP1281483B1 true EP1281483B1 (fr) 2008-04-23

Family

ID=8178162

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20010118236 Expired - Lifetime EP1281483B1 (fr) 2001-07-30 2001-07-30 Marteau rotatif

Country Status (2)

Country Link
EP (1) EP1281483B1 (fr)
DE (1) DE50113888D1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007062248A1 (de) 2007-12-21 2009-06-25 Robert Bosch Gmbh Handwerkzeugmaschine mit einer, mindestens eine drehbar gelagerte Zwischenwelle umfassenden Getriebevorrichtung
EP4319944A1 (fr) * 2021-04-07 2024-02-14 Milwaukee Electric Tool Corporation Outil électrique à percussion

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2638325A (en) * 1947-12-29 1953-05-12 Joy Mfg Co Drilling apparatus
DE2335924A1 (de) * 1973-07-14 1975-02-06 Bosch Gmbh Robert Handwerkzeugmaschine mit betriebszeitanzeigevorrichtung
DE2743153A1 (de) * 1977-09-24 1979-04-05 Impex Essen Vertrieb Kurbeltrieb fuer elektromotorisch angetriebene handschlaggeraete
EP0042010B1 (fr) * 1980-06-12 1984-08-08 Black & Decker Inc. Outil à force motrice comportant un mécanisme pour convertir un mouvement rotatif en un mouvement alternatif
US4712625A (en) * 1986-01-14 1987-12-15 Willy Kress Drilling and percussion hammer
DE3621183A1 (de) * 1986-06-25 1988-01-07 Bosch Gmbh Robert Handwerkzeugmaschine, insbesondere bohr- und/oder schlaghammer
DE3936849A1 (de) * 1989-11-06 1991-05-08 Bosch Gmbh Robert Elektrisch angetriebene handwerkzeugmaschine
JP3609626B2 (ja) * 1998-09-16 2005-01-12 株式会社マキタ ハンマードリル

Also Published As

Publication number Publication date
DE50113888D1 (de) 2008-06-05
EP1281483A3 (fr) 2003-03-05
EP1281483A2 (fr) 2003-02-05

Similar Documents

Publication Publication Date Title
EP1940593B1 (fr) Machine-outil electrique
DE3405922C2 (fr)
EP1923176B1 (fr) Marteau perforateur
EP1716980B1 (fr) Outil portatif avec entraînement à basculement
EP0771618B1 (fr) Outil pour forer et/ou ciseler
DE2252951B2 (de) Bohrhammer
EP3638457B1 (fr) Machine-outil portative
WO2008071489A1 (fr) Dispositif de percussion d'une machine-outil électrique à main
DE102005000199A1 (de) Handwerkzeuggerät mit Ratschenschlagwerk
DE102004058686A1 (de) Elektrowerkzeug mit einem zwischen den Betriebsarten Bohren, Schlagbohren, Meißeln umschaltbaren Antrieb
DE102015201573A1 (de) Schlagwerkvorrichtung, insbesondere für einen Schlagschrauber
EP2700477B1 (fr) Agencement d'engrenage pour une machine-outil et machine-outil
EP0771620B1 (fr) Outil de forage et de burinage
EP3456479B1 (fr) Dispositif d'entraînement pour une machine-outil motorisée
DE102004052329A1 (de) Synchronisations- und Schalteinheit für Einknopf-Wahlschalter sowie Elektrowerkzeug mit Synchronisations- und Schalteinheit
EP1281483B1 (fr) Marteau rotatif
EP1420921B1 (fr) Machine-outil, en particulier marteau perforateur et/ou burineur
EP1677950B1 (fr) Outil de percussion pour une machine-outil a main
EP3461594B1 (fr) Dispositif d'entraînement pour une machine-outil entraînée
DE3215198C2 (fr)
DE102006027116A1 (de) Bohr- und/oder Schlaghammer
DE102012005864A1 (de) Taumelwelle mit integrierter Sicherheitskupplung und Verriegelung
DE3213671A1 (de) Bohrhammer
DE3402728A1 (de) Bohr- oder schlaghammer
DE102006031745A1 (de) Handwerkzeugmaschine, insbesondere Bohr- und/oder Meißelhammer

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20030329

AKX Designation fees paid

Designated state(s): DE FR GB IT

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

Owner name: A & M ELECTRIC TOOLS GMBH

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Owner name: AEG ELECTRIC TOOLS GMBH

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

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

Effective date: 20080423

REF Corresponds to:

Ref document number: 50113888

Country of ref document: DE

Date of ref document: 20080605

Kind code of ref document: P

ET Fr: translation filed
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

Effective date: 20090126

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

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

Ref country code: ES

Payment date: 20180903

Year of fee payment: 18

Ref country code: FR

Payment date: 20180725

Year of fee payment: 18

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

Ref country code: GB

Payment date: 20180719

Year of fee payment: 18

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

Ref country code: DE

Payment date: 20190719

Year of fee payment: 19

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

Effective date: 20190730

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: 20190730

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

Ref country code: FR

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

Effective date: 20190731

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: 20190730

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50113888

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20210202