EP1578564B1 - Marteau perforateur - Google Patents

Marteau perforateur Download PDF

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Publication number
EP1578564B1
EP1578564B1 EP03814444A EP03814444A EP1578564B1 EP 1578564 B1 EP1578564 B1 EP 1578564B1 EP 03814444 A EP03814444 A EP 03814444A EP 03814444 A EP03814444 A EP 03814444A EP 1578564 B1 EP1578564 B1 EP 1578564B1
Authority
EP
European Patent Office
Prior art keywords
switch
hammer
ring
switch button
spring
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
EP03814444A
Other languages
German (de)
English (en)
Other versions
EP1578564A1 (fr
Inventor
Axel Kuhnle
Willy Braun
Heinz Schnerring
Gerhard Meixner
Karl Frauhammer
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1578564A1 publication Critical patent/EP1578564A1/fr
Application granted granted Critical
Publication of EP1578564B1 publication Critical patent/EP1578564B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0015—Tools having a percussion-only mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0038—Tools having a rotation-only mode

Definitions

  • the invention is based on a hammer drill according to the preamble of claim 1.
  • a hammer drill is in the document US Pat. No. 6,176,321 B1 disclosed.
  • a mode switch is provided, which separates the hammer tube from the gear train in the "chiseling" mode and fixed against rotation in the housing. Thereby the separation between the hammer ear becomes enclosing, rotatably mounted output gear of the gear transmission and the hammer ear made.
  • the hammer drill according to the invention with the features of claim 1, has the advantage that the switching mechanism of the mode selector switch is very flat and the axial extent of the mode selector switch can be kept small in particular by a narrow running switching ring. Due to the flat design of the manually operable switch button receiving housing cover made low and the corner of the hammer drill, which is the distance between the hammer middle and upper edge of the housing to be kept small. For a non-rotatable connection between the rotatable on the hammer tube and axially displaceable fixed switching ring and the output gear of the transmission, a single locking cam is sufficient.
  • a plurality of distributed over the circumference of the switching ring locking cam are provided which are axially inserted into a corresponding plurality of Axialausappel traditions in the driven gear. Due to the large number of locking cams and axial recesses, the metal-made switching ring can transmit a higher torque and, if necessary, can also be made of plastic. In addition, a non-aligned alignment of locking cam and Axialaus traditions a much smaller rotary travel of the hammer tube for engaging the switching ring in the drive wheel is required.
  • the switching ring can be pushed onto the hammer tube in any relative position, which facilitates assembly.
  • the rear derailleur can be made very compact and stable despite Baukliki, so that it ensures a long service life.
  • the switching ring is located on the side facing away from the switching knob side of the driven gear and is fixedly connected under the drive wheel with a pushed onto the other side of the driven gear on the hammer tube coupling ring, which is coupled to the switch knob so that a Switch button switching causes an axial displacement of the switching ring.
  • connection to the preferably made of plastic coupling ring is realized according to an advantageous embodiment of the invention via two cantilevers, which protrude in one piece with the coupling ring axially from this and record the switching ring arranged near its ends recesses.
  • two cantilevers By compressing the two elastically outwardly biased cantilevers of the switching ring can be easily mounted.
  • the circumferential play of the cantilevers is kept larger than that of the switching ring on the hammer tube, so sat the cantilevers no torque must be transmitted.
  • the coupling ring is coupled via a shift fork, which is guided with a nose in an annular groove in the coupling ring on the switch button, wherein the coupling is made via a held on the shift fork synchronization spring and arranged on the switching knob eccentric pin, where the legs of the shift fork abut at diametrical locations non-positively.
  • the large synchronization spring allows a smooth and safe switching of the Operating modes switch.
  • the shift fork and the coupling ring can be inexpensively made of plastic.
  • the size of the switch button facilitates operation and also allows handling with work gloves.
  • the switching knob is assigned a further setting position for the works council "drilling" in which the hammer mechanism is disconnected from its drive with a rotating hammer tube.
  • This decoupling is not caused by the axial displacement of the switching ring on the hammer tube, but by a perpendicular thereto oriented displacement of a switching mechanism part that separates a arranged in the drive chain of the percussion clutch.
  • a switching ramp extending over a rotation angle is formed on the switching knob, preferably on its underside, which rises in the direction of the axis of rotation of the switching knob.
  • the switching mechanism part is advantageously designed as an axially displaceable separating slide, which bears non-positively on the one hand on the switching ramp and on the other hand on a displaceable coupling part of the clutch, by the axial displacement against the force of a clutch spring, the clutch can be solved.
  • the low spring force of the clutch spring and provided on the isolation slide for non-positive application to the switching ramp spring allows a smooth, yet safe switching the mode selector switch.
  • the rotary hammer shown in FIG. 1 in fragmentary form with its rear region in longitudinal section has a housing 10 with a housing opening 11, which is closed by a housing cover 12.
  • a tool holder projects from the housing 10 for the limited axial displacement of a tool.
  • the tool holder is rotatably connected to a rotatably mounted in the housing 10 hammer tube 13.
  • an air cushion impact mechanism 14 is arranged with a piston 15 axially displaceable in the hammer tube 13, which is offset by means of a lying in a drive chain between an electric motor 27 and the piston 15 crank mechanism 16 in a reciprocating stroke movement can be.
  • the air cushion impactor 14 also includes a driven by the piston 15 racket, which acts via an anvil on the end of the tool holder received in the tool.
  • the hammer drill described here agrees with that in the DE 38 26 213 A1 match described hammer drill, the local arrangement and training of tool holder, hammer tube 13 and air cushion impact mechanism 14 with piston 15 also applies to the hammer drill described here.
  • the crank mechanism 16 comprises a crank wheel 18 with a molded bearing socket 181 and a crank pin 19 arranged eccentrically to the rotation axis, on which a push rod 20 rotatably seated, which in turn is pivotally connected to the piston 15 of the air cushion impact mechanism 14.
  • the crank wheel 18 is rotatably mounted with its bearing socket 181 on a housing-fixed axis 17.
  • On the bearing sleeve 181 is rotatably and axially displaceably arranged a gear 21 with external teeth 22.
  • a trained as a helical compression spring clutch spring 23 is supported, which presses the gear 21 frontally against a later described in detail separating slide 24. In this displacement position of the toothed wheel 21 shown in FIG.
  • the gear transmission 30 includes a seated on the hammer tube 13 ring gear 31 which is axially displaceable and rotatably supported on the hammer tube 13, a meshing with the ring gear 31 meshing bevel gear 32 and a bevel gear 32 rotatably connected gear 33 with external teeth 34th bevel gear 32nd and gear 33 are rotatably held in the housing 10, and the external teeth 34 meshes with the drive pinion 28 on the output shaft 26 of the electric motor 27th
  • the hammer drill thus described can be used in three modes.
  • both the hammer tube 13 is set in rotation by the switched-on electric motor 27, and the air cushion striking mechanism 14 is activated, for which purpose the coupling in the drive chain of the air cushion percussion mechanism 14 (as shown in FIG. 1) is closed and the ring gear 31 rotatably connected to the hammer tube 13 is connected.
  • the "chiseling” mode only the air cushion impact mechanism 14 is activated, for which purpose the clutch in the drive chain of the air cushion impact mechanism 14 is closed and the ring gear 31 is decoupled from the hammer tube 13.
  • the air cushion impact mechanism 14 In the "drilling" mode, the air cushion impact mechanism 14 is stopped and the hammer tube 13 is rotated, for which purpose the clutch in the drive chain of the air cushion impact mechanism 14 is opened and the ring gear 31 is non-rotatably connected to the hammer tube 13.
  • a mode switch 35 which includes a single, manually operated switch button 36 and a stable and compact designed switching mechanism 37.
  • the switch button 36 is protected and user friendly in the housing cover 12th
  • the switch button lower part 38 has a switch button lower part 38 and a switch button cap 39, which engages over a housing 12 formed on the collar 12.
  • the switch button lower part 38 is inserted in a collar 21 enclosed by the stepped bore and fixed to the underside of the switch button cap 39.
  • the switch button base 38 has an eccentric pin 40 projecting at right angles from the underside of the switch button base 38, and a shift ramp 41 disposed on the underside of the shift button base 38 extending circumferentially of the shift button base 38 and thereby in the direction of the axis of rotation of the switch knob 36, in Fig. 1 so down, increases.
  • To the switching mechanism 37 also includes the aforementioned slide 24, which is guided vertically displaceably in the housing 10 and with a bent slider end 241 on the underside of the switch button base 38 and rests on the switching ramp 41 and with its other bent slider end 242 the displaceable coupling part of the clutch in the drive chain of the air cushion impact mechanism 14 forming gear 21 overlaps frontally.
  • the upper slide end 241 is pressed by a in Fig.
  • the switching element 43 is composed of a coupling ring 45 made of plastic , of which two with the coupling ring 45 integral, diametrically arranged cantilevers 46 protrude axially.
  • the cantilevers 46 are each provided with a recess 47 at their ring-distal, free end and are biased in the radial direction of the coupling ring 45 to the outside.
  • a switching ring 48 used, which is preferably made of metal.
  • the switching ring 48 carries on its the hammer tube 13 facing the inside two diametrically arranged, radially projecting guide cam 49, the corresponding guide grooves 50 which are incorporated on the outside of the hammer tube 13, eino.
  • the hammer tube 13 two further guide grooves 50 are incorporated, each receiving one of the two cantilevers 46.
  • the dimensions of the cantilever arms 46 and the guide cam 49 are made equal, so that the total of four guide grooves 50 can be made the same.
  • the insertion openings of the Axialausappel strictly undertaken 52 in the ring gear 31 opposite a housing-fixed locking member 53 is arranged, the locking teeth are formed so that the locking cam 51 can be inserted axially into the locking member 53 and eino positively in the direction of rotation.
  • the locking member 53 is disposed in such axial distance from the Axialaus strictly adopted 52 in the ring gear 31 that after pushing out the switching ring 48 from the ring gear 31 of the switching ring 48 is still able to take a position in which its locking cam 51 does not engage in the locking member 53.
  • the hammer tube 13 is neither on the ring gear 31 still fixed to the housing Locking part 53 coupled, so that the hammer tube 13 can rotate freely.
  • the coupling ring 45 has a recess or an annular groove 54 into which a radially oriented nose 45 of the shift fork 44 engages.
  • the synchronization spring 56 is a helical spring with right angles bent to the spring axis, long legs 561, 562 is formed, which is pushed onto a right angle of the shift fork 44 upwardly projecting bolt 57 and with its two long legs 561 and 562 non-positively applied to diametrical positions of the eccentric pin 40, in the direction of the shift fork 44th approximately aligned with each other (Fig. 5 - 8).
  • the eccentric pin 40 is arranged on the switch button lower part 38 at an angle ⁇ relative to the longitudinal axis of the shift fork 44 so that when turning the switch knob 36 by 90 ° four pivot positions of the eccentric pin 40 result, seen in the direction of shift fork 44 each a distance of a / 2 are offset from each other, as shown in Fig. 5.
  • the total displacement of the shift fork 44 is a, after which the shift fork 44 abuts against a housing-fixed stop 59.
  • the upper slide end 241 of the separating slide 24 can still be seen, which engages over the underside of the switching button lower part 38 and rests on the switching ramp 41 over a circumferential angle of approximately 270 °.
  • the switch button cap 39 is shown in plan view. It has a grip web 58 on which a marking tip 581 is formed.
  • the marker tip 581 indicates the setting position of the switch button 36 and in order to set the mode of operation "chiseling" M, "impact drilling” S and “drilling” B, which is set by operating mode selector 35.
  • a "neutral or zero position" 0 is provided, in which only the air cushion impact mechanism 14, but not the rotary drive for the Hammer tube 13 is effective and the hammer tube 13 is free and arbitrary to rotate in the housing 10.
  • mode switch 35 The operation of mode switch 35 is as follows:
  • the switching knob 36 is set so that the marker tip 581 points to the position M, it is - as shown in Fig. 5 - the shift fork 44 furthest in Fig. 1 to the left shifted by the maximum displacement a. Accordingly, the switching member 43 is displaced by the shift fork 44 to the maximum left, whereby the switching ring 48 has penetrated with its locking cam 51 in the housing-fixed locking part 53.
  • cantilevers 46 and grooves 50 rotatable connection of the switching ring 48 to the hammer tube 13, the hammer tube 13 rotatably fixed to the housing 10, and there is no connection between the hammer tube 13 and the ring gear 31.
  • the switching knob 36 is rotated from the position M to the position 0 by 90 ° in Fig. 4 counterclockwise, it is - as shown in Fig. 6 - via the eccentric pin 40 and the synchronization spring 56, the shift fork 44 to the displacement a / 2 in Fig. 1 shifted to the right.
  • the switching member 43 is shifted in Fig. 1 to the right by the same displacement, whereby the locking cam 51 on the switching ring 48 emerge from the locking member 53 and the switching ring 48 - as shown in Fig. 1 - a middle position between the locking member 53 and ring gear 21st occupies.
  • the hammer tube 13 is released for free rotation, but is not offset by the electric motor 27 in rotation.
  • the air cushion impact mechanism 14 remains activated because the separating slide 24 is held in this rotational position of the switch button 36 by the switching ramp 41 in the position shown in Fig. 1.
  • the shift fork 44 is again shifted to the right by the displacement a / 2 in Fig. 1 and abuts the stop 50 fixed to the housing at the half of the pivoting path of the eccentric pin.
  • the further displacing eccentric pin 40 deflects the spring leg 561 of the synchronization spring 56 (FIG. 7).
  • the shifter fork 44 displacing by a / 2 displaces the shift ring 48 in FIG. 1 to the right so that the locking cams 51 insert positively into the axial recesses 52 in the ring gear 31 and thus connect the hammer tube 13 to the ring gear 31 in a rotationally fixed manner.
  • the electric motor 27 now puts the hammer tube 13 and thus the tool holder and the rotatably held in the tool holder tool in rotation.
  • the air cushion impact mechanism 14 remains activated since the upper slide end 241 of the isolating slide 24 has not yet left the switching ramp 41 (see position SB in FIG.

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

Abstract

Marteau perforateur qui possède un mandrin (13) situé dans un boîtier (10) et pouvant être entraîné en rotation, un mécanisme à percussion (14) placé dans le mandrin (13) et pourvu d'un piston (14) pouvant être entraîné pour effectuer une course de va-et-vient, et un commutateur (35) de mode de fonctionnement entre les modes de fonctionnement « forage percutant » et « burinage ». Selon la présente invention, le mandrin (13) est découplé de son entraînement en rotation dans le mode de fonctionnement « forage percutant » et fixé non rotatif dans le boîtier (10) en mode de fonctionnement « burinage ».

Claims (15)

  1. Marteau perforateur comportant un tube de marteau (13) logé tournant dans un boîtier (10) et entraîné en rotation par une roue menée (31) d'un engrenage (30) située sur le tube de marteau (13), un mécanisme de percussion (14) dans le tube de marteau (13) qui présente un piston (15) pouvant être entraîné dans un mouvement linéaire de va-et-vient, et un sélecteur de fonctions (35) pour les fonctions « perforer par percussion » et « buriner » qui présente un bouton de commutation (36) pouvant être actionné manuellement et un mécanisme de commutation (37) relié au bouton de commutation (36) qui accouple le tube de marteau (13) à la roue menée (31) dans la position de réglage du bouton de commutation (36) « perforer par percussion » et le fixe dans le boîtier (10) de façon non pivotante dans la position de réglage « buriner »,
    caractérisé en ce que
    le mécanisme de commutation (37) présente une bague de commutation (48) fixée sur le tube de marteau (13) de façon à résister à la rotation et de façon à pouvoir être déplacée axialement, et qui porte sur sa face externe détournée du tube de marteau (13) au moins une came de verrouillage radialement distante (51) formée d'une part dans au moins un évidement axial (52) solidaire de la roue d'entraînement et d'autre part dans une denture axiale (53) solidaire du boîtier permettant une insertion par complémentarité de forme dans la direction périphérique.
  2. Marteau perforateur selon la revendication 1,
    caractérisé en ce que
    la bague de commutation (48) porte sur sa face interne tournée vers le tube de marteau (13) au moins une came de guidage (49) écartée radialement et permettant de fixer la bague de commutation (48) sur le tube de marteau (13) de façon à résister à la rotation et mobile axialement, de préférence deux cames de guidage (49) diamétralement opposées et le tube de marteau (13) présente sur sa face externe tournée vers la bague de commutation (48) au moins une rainure de guidage axial (50), de préférence deux rainures de guidage diamétralement opposées, dans lesquelles la came de guidage (49) est insérée par complémentarité de forme dans une direction périphérique.
  3. Marteau perforateur selon la revendication 1 ou 2,
    caractérisé en ce que
    la bague de commutation (48) est sur la face de la roue menée (31) détournée du bouton de commutation (36), et reliée sous la roue motrice (31) à une bague d'accouplement (45) poussée sur le tube de marteau (13) de l'autre côté de la roue menée (31), cette bague étant accouplée au bouton de commutation (36) de sorte qu'une commutation du bouton de commutation provoque un déplacement axial de la bague de commutation (48).
  4. Marteau perforateur selon la revendication 3,
    caractérisé en ce que
    la liaison entre la bague de commutation (48) et la bague d'accouplement (45) est établie à l'aide d'au moins deux bras en porte-à-faux (46) axialement écartée de la bague d'accouplement (45).
  5. Marteau perforateur selon la revendication 3 ou 4,
    caractérisé en ce que
    les bras en porte-à-faux (46) sont moulés d'une seule pièce sur la bague d'accouplement (45) et la bague de commutation (48) est logée dans des évidements (47) moulés dans la face externe des bras en porte-à-faux détournée du tube de marteau (13) à proximité de l'extrémité éloignée de la bague d'accouplement des bras en porte-à-faux (46).
  6. Marteau perforateur selon la revendication 4 ou 5,
    caractérisé en ce que
    les bras en porte-à-faux (46) sont logés par complémentarité de forme dans des rainures axiales (50) dans le tube de marteau (13), mobiles axialement et dans la direction périphérique du tube de marteau (13).
  7. Marteau perforateur selon l'une quelconque des revendications 3 à 6,
    caractérisé en ce que
    la face externe de la bague d'accouplement (45), comporte une rainure annulaire (54) dans laquelle un ergot (55) aligné radialement d'une fourchette de commande (44) accouplée au bouton de commutation (36) est guidé de façon coulissante.
  8. Marteau perforateur selon la revendication 7,
    caractérisé en ce que
    le bouton de commutation (36) est fixé de façon pivotante dans le boîtier (10) autour d'un axe de rotation et la fourchette de commande (44) est accouplée par un ressort de synchronisation (56) à un tourillon excentrique (40) écarté du bouton de commutation (36), dans l'intervalle radial à l'axe de rotation.
  9. Marteau perforateur selon la revendication 8,
    caractérisé en ce que
    le ressort de synchronisation (56) est un ressort hélicoïdal comportant des branches (561, 562) longues et pliées de façon perpendiculaire à l'axe du ressort, le ressort à branches (56) est logé sur un boulon (57) formé sur la fourchette de commande (44) et ses deux branches (561, 562) s'appuient par liaison de force sur des emplacements du tourillon d'excentrique (40) diamétralement opposées l'un à l'autre dans la direction de déplacement de la fourchette de commande (44).
  10. Marteau perforateur selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que
    le bouton de commutation (36), à une position de réglage dans une position de déplacement qui règle la bague de commutation (48) du mécanisme de commutation (37) telle que la bague de commutation (48) n'est ni engagé avec la roue menée (31) de façon à résister à la rotation, ni engagé avec le boîtier (10) de façon à résister à la rotation.
  11. Marteau perforateur selon l'une quelconque des revendications 1 à 10,
    caractérisé en ce que
    le bouton de commutation (36) présente une position de réglage pour la fonction « perforer », dans laquelle le mécanisme de percussion (14) est désaccouplé et le désaccouplement du mécanisme de percussion (14) est provoqué par un mouvement de déplacement perpendiculaire d'un élément du mécanisme de commutation (37) déclenché par le bouton de commutation (36), permettant un mouvement de déplacement de la bague de commutation (48) sur le tube de marteau (13).
  12. Marteau perforateur selon la revendication 11,
    caractérisé en ce qu'
    un dispositif d'accouplement comportant deux parties d'accouplement maintenues en engagement l'une avec l'autre par un ressort d'accouplement (23) est agencé dans la chaîne de commande pour le mécanisme de percussion (14), et une partie d'accouplement est mobile contre la force du ressort d'accouplement (23) par l'élément du mécanisme de commutation actionné par le bouton de commutation (36).
  13. Marteau perforateur selon la revendication 12,
    caractérisé en ce que
    le bouton de commutation (36) comporte une rampe de commutation (41) qui s'élève de façon perpendiculaire à la face inférieure du bouton de commutation (36) dans le sens de rotation du bouton de commutation (36), et l'élément du mécanisme de commutation est un coulisseau de séparation (24) axialement mobile qui s'appuie de force d'une part sur la rampe de commutation (41) et d'autre part sur la partie d'accouplement mobile.
  14. Marteau perforateur selon la revendication 13,
    caractérisé en ce que
    la liaison de force entre le coulisseau de séparation (24) et la partie d'accouplement d'une part et le coulisseau de séparation (24) et la rampe de commutation (41) d'autre part est établie par un ressort (42), s'appliquant au coulisseau de séparation (24), dont la tension du ressort est plus grande que celle du ressort d'accouplement (23) et est en sens inverse de la force du ressort d'accouplement.
  15. Marteau perforateur selon l'une quelconque des revendications 12 à 14,
    caractérisé en ce que
    la chaîne de commande pour le mécanisme de percussion (14) présente une roue à manivelle (18) d'une commande à manivelle (16) s'appliquant au piston (15) du mécanisme de percussion (14) et une roue dentée (21), qui engrène avec un pignon de commande (28) entraîné par un moteur électrique (27), la roue à manivelle (18) et la roue dentée (21) forment les parties d'accouplement qui sont en engagement l'une avec l'autre par une denture axiale (25), et le ressort d'accouplement (23) est un ressort de pression qui s'appuie axialement entre la roue à manivelle (18) et la roue dentée (21).
EP03814444A 2002-12-24 2003-07-25 Marteau perforateur Expired - Lifetime EP1578564B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10261030 2002-12-24
DE10261030A DE10261030A1 (de) 2002-12-24 2002-12-24 Bohrhammer
PCT/DE2003/002512 WO2004060616A1 (fr) 2002-12-24 2003-07-25 Marteau perforateur

Publications (2)

Publication Number Publication Date
EP1578564A1 EP1578564A1 (fr) 2005-09-28
EP1578564B1 true EP1578564B1 (fr) 2007-10-10

Family

ID=32477999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03814444A Expired - Lifetime EP1578564B1 (fr) 2002-12-24 2003-07-25 Marteau perforateur

Country Status (6)

Country Link
US (1) US7121359B2 (fr)
EP (1) EP1578564B1 (fr)
JP (1) JP2006512216A (fr)
CN (1) CN100519091C (fr)
DE (2) DE10261030A1 (fr)
WO (1) WO2004060616A1 (fr)

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US11964375B2 (en) 2019-11-27 2024-04-23 Black & Dekcer Inc. Power tool with multispeed transmission

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Publication number Priority date Publication date Assignee Title
GB0311045D0 (en) 2003-05-14 2003-06-18 Black & Decker Inc Rotary hammer
JP4515181B2 (ja) * 2004-07-20 2010-07-28 株式会社マキタ 電動ハンマドリル
DE102004045117A1 (de) * 2004-09-17 2006-03-23 Robert Bosch Gmbh Schaltvorrichtung
US7469752B2 (en) * 2005-12-02 2008-12-30 Makita Corporation Power tool
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DE10261030A1 (de) 2004-07-08
DE50308372D1 (de) 2007-11-22
JP2006512216A (ja) 2006-04-13
WO2004060616A1 (fr) 2004-07-22
EP1578564A1 (fr) 2005-09-28
CN100519091C (zh) 2009-07-29
US7121359B2 (en) 2006-10-17
CN1717300A (zh) 2006-01-04
US20050269116A1 (en) 2005-12-08

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