EP2646198B1 - Mécanisme de percussion à marteau - Google Patents

Mécanisme de percussion à marteau Download PDF

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Publication number
EP2646198B1
EP2646198B1 EP11770108.6A EP11770108A EP2646198B1 EP 2646198 B1 EP2646198 B1 EP 2646198B1 EP 11770108 A EP11770108 A EP 11770108A EP 2646198 B1 EP2646198 B1 EP 2646198B1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
tool chuck
hammer
chuck drive
tool
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.)
Active
Application number
EP11770108.6A
Other languages
German (de)
English (en)
Other versions
EP2646198A1 (fr
Inventor
Joachim Hecht
Martin Kraus
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 EP2646198A1 publication Critical patent/EP2646198A1/fr
Application granted granted Critical
Publication of EP2646198B1 publication Critical patent/EP2646198B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • B25B21/023—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 for imparting an axial impact, e.g. for self-tapping screws
    • 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
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • 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
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • 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
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B25D2216/003—Tools having a percussion-and-rotation mode comprising de-phasing of percussion and rotation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0015—Anvils
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/131—Idling mode of tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/301—Torque transmission means

Definitions

  • a "impact generation unit” is to be understood in particular as meaning a unit which is intended to translate a rotational movement into a, in particular translational, striking movement of the racquet suitable for drilling and percussion drilling operation.
  • the impact generation unit is designed as a impact generation unit that appears appropriate to the person skilled in the art, but preferably as a pneumatic impact generation unit and / or particularly preferably as a impact generation unit with a rocker arm.
  • a "rocker arm” should in particular be understood to mean a device which is mounted so as to be movable about a pivot axis and which is provided to deliver a power absorbed at a first coupling region to a second coupling region.
  • the term “bat” is to be understood as a means of the hammer impact mechanism, which is intended to be accelerated in particular translationally during operation by the impact generating unit and to deliver a recorded during the acceleration pulse as a shock pulse in the direction of an insert tool.
  • the racket is accelerated by an air pressure or advantageously by a rocker arm in the direction of impact.
  • the racket is unaccelerated immediately prior to a strike.
  • the racket is preferably in a stroke from a shock pulse in the direction of an insert tool, in particular via an anvil, to the insert tool.
  • a "tool chuck drive shaft” is to be understood, in particular, as a shaft which transmits rotational movement from a gear, in particular a planetary gear, in the direction of a tool chuck in a drilling and / or percussion drilling operation.
  • the shaft is at least partially formed as a solid shaft.
  • the tool chuck drive shaft extends in the direction of impact over at least 40 mm.
  • the tool chuck drive shaft and the tool chuck in a drilling and / or percussion drilling operation in particular always, a same speed, that is, in particular a drive train between the chuck drive shaft and the tool chuck is free of a transmission.
  • the term "tool chuck” is to be understood to mean a device which is intended to fix an insert tool detachably, at least non-rotatably, directly from an operator, in particular without tools.
  • a "direction of impact” is to be understood in particular as meaning a direction which runs parallel to an axis of rotation of the tool chuck and which is directed by the racket in the direction of the tool chuck.
  • the direction of impact is aligned parallel to a rotational axis of the tool chuck drive shaft.
  • the phrase "movably support” is to be understood to mean that the tool chuck drive shaft has a bearing surface which, in at least one operating state, transmits bearing forces perpendicular to the direction of impact to the racquet.
  • a “coupling means” is to be understood in particular as meaning a means which is intended to transmit a movement from one component to another component at least by means of a positive connection.
  • the form-fitting is detachably formed by the operator in at least one operating state.
  • the positive connection for switching an operating mode is releasable, and advantageously between a screw, a drill a chisel and / or a percussion drilling operation.
  • the coupling agent is advantageous as a coupling that appears appropriate to a person skilled in the art
  • a jaw clutch and / or a toothing formed.
  • the coupling means has a plurality of positive locking elements and a region connecting the interlocking elements.
  • the term "rotationally fixed" should be understood that the coupling means and the tool chuck drive shaft are firmly connected to each other at least in the circumferential direction, preferably in each direction, and in particular in each operating state.
  • the coupling means transmits a kinetic energy, in particular a rotational energy, to at least one region of the impact generation unit.
  • the beat generation unit drives the bat with this energy. Due to the inventive design, a particularly compact and powerful hammer impact mechanism can be provided structurally simple.
  • the coupling means is formed integrally with the tool chuck drive shaft, whereby an inexpensive production can be achieved.
  • the coupling means could be in another, the skilled person seems appropriate with the tool chuck drive shaft, but advantageously pressed, bolted and / or circumferentially positively and axially connected via a snap ring or a band.
  • one piece should be understood in particular at least materially connected connected, for example, by a welding process, a gluing process, a Anspritzrind and / or another, the skilled person appear useful process, and / or advantageously formed in one piece, such as by a Manufacture from a cast and / or advantageously from a single blank.
  • the coupling means is provided to immerse in activating at least one beat mode in a coupling means of the beat generation unit, whereby advantageously little space is needed.
  • activating a beat mode is meant, in particular, a setting process in which, in particular, the operator sets the hammer impact mechanism in such a way that, during operation, the beat generation unit drives the beater in a striking manner.
  • the operator preferably switches from a drilling and / or screwing mode to a percussion drilling and / or chisel mode.
  • the phrase "immersing in a coupling agent” should be understood to mean that the coupling means is arranged in an operating state outside a recess of the impact generation unit and is moved into the recess when the impact mode is activated.
  • a “recess” should in particular be understood to mean a region delimited by the impact generation unit, by more than 180 degrees, advantageously by 360, the coupling means on at least one plane, which is advantageously aligned perpendicular to the direction of impact Degrees, encloses.
  • the tool chuck drive shaft at least partially penetrates the racket, whereby a chuck drive shaft with a particularly low mass and a small space requirement can be provided.
  • a chuck drive shaft with a particularly low mass and a small space requirement can be provided.
  • the phrase "at least partially penetrate” that the racket the tool chuck drive shaft on at least one plane, which is advantageously aligned perpendicular to the direction of impact, by more than 270 degrees, preferably 360 degrees encloses.
  • the racket is positively secured to the tool chuck drive shaft in a direction perpendicular to the axis of rotation of the chuck drive shaft, that is, movably supported in the direction of the axis of rotation.
  • the hammer impact mechanism comprises at least one bearing which is provided to support the tool chuck drive shaft axially displaceable, whereby a structurally simple impact mechanism shutdown is possible.
  • a “bearing” is to be understood, in particular, as meaning a device which fixes the tool chuck drive shaft, in particular, so as to be movable and axially displaceable, at least about the axis of rotation, relative to a housing.
  • the term "axially displaceable" should be understood to mean that the bearing movably fixes the tool chuck drive shaft, in particular relative to a housing, parallel to the direction of impact.
  • a connection of the coupling means of the tool chuck drive shaft driving the impact generating unit can be released by an axial displacement of the chuck drive shaft.
  • the hammer impact mechanism has a planetary gear that drives the tool chuck drive shaft in at least one operating state, whereby an advantageous translation can be achieved in a small space. Furthermore, structurally simple torque limitation and several gear stages can be realized.
  • a "planetary gear” is to be understood in particular as a unit having at least one planetary gear set.
  • a planetary gear set preferably has a sun gear, a ring gear, a planet carrier and at least one of the planet tenradisme on a circular path around the sun gear guided planet.
  • the planetary gear has at least two selectable by the operator gear ratios between an input and an output of the planetary gear.
  • the tool chuck drive shaft has a further coupling means which is provided to produce an axially displaceable rotationally fixed connection to the planetary gear, whereby a structurally simple structure can be achieved.
  • An "axially displaceable rotationally fixed connection” is to be understood in particular as meaning a connection which is intended to transmit a force in the circumferential direction and to permit a movement of the tool chuck drive shaft relative to the planetary gear in the axial direction.
  • the hammer impact mechanism comprise a torque limiting device, which is intended to limit a maximum transmissible via the tool chuck drive shaft torque, whereby the operator is advantageously protected and the hand tool can be comfortably and efficiently used for screwing.
  • limit is to be understood in this context, in particular, that the torque limiting device prevents exceeding the particular adjustable by an operator maximum torque.
  • the torque limiting device opens a rotationally fixed connection between a drive motor and the tool chuck during operation.
  • the torque limiting device can act on an energy supply of the drive motor.
  • the hammer impact tool has a tool chuck and a striker with a coupling means which is provided for transmitting a rotational movement to the tool chuck, whereby a particularly compact hammer impact mechanism can be provided.
  • the striker transmits a rotational movement of the tool chuck drive shaft to the tool chuck.
  • a "striker" is to be understood in particular an element of the hammer impact mechanism, which transmits the impact pulse of the racket in the direction of the insert tool in a striking operation.
  • the striker strikes in at least one operating condition directly on the insert tool.
  • the striker prevents ingress of dust through the tool chuck in the hammer impact mechanism.
  • the impact generation unit has a spur gear stage which translates a rotational speed of the tool chuck drive shaft into a higher rotational speed for impact generation, whereby a particularly advantageous ratio between rotational speed and impact rate of an insertion tool can be achieved in a structurally simple and space-saving manner.
  • a "spur gear stage” is to be understood in particular as an arrangement of, in particular, two intermeshing toothed wheels, which are rotatably mounted about parallel axes.
  • the gears have a toothing on a surface facing away from its axis.
  • a rotational speed of a drive means of the impact generating unit that appears to be suitable to a person skilled in the art is to be understood as a “rotational speed for impact generation” which translates a rotational movement into a linear movement.
  • the drive means of the impact generation unit is designed as a swash bearing or particularly preferably as an eccentric element.
  • translate is meant to be understood here that the speed of the tool chuck drive shaft and the speed to beat production differ.
  • the speed for the impact generation is greater, advantageously at least twice as large as the rotational speed of the tool chuck drive shaft.
  • a gear ratio of the rotational speed to the impact generation to the rotational speed of the tool chuck drive shaft is non-uniform.
  • the hammer impact mechanism comprises a Schlager Wegungsabschalte unit with a blocking element, at least in a drilling operation and in particular in a screw parallel to at least a force of the tool chuck drive shaft acts on the striker, whereby an advantageous arrangement of an operating element of the Schlager Wegungsabschaltech is structurally simple.
  • an annular operating element which encloses the striker or the tool chuck drive shaft, can be easily realized.
  • a "impact generation disconnection unit” is to be understood as meaning, in particular, a unit which is provided for enabling an operator to switch off the impact generation unit for a drilling and / or screwing operation.
  • the impact generation shut-off unit prevents in particular automatic switching on of the impact generation unit when an insertion tool is pressed against a workpiece in a drilling and / or screwing mode.
  • Pressing in a chisel and / or percussion drilling mode preferably causes an axial displacement of the chuck drive shaft.
  • the blocking element is provided to prevent axial displacement of the chuck drive shaft, the tool chuck and / or advantageously the striker in the drilling and / or screwing mode:
  • the phrase "parallel to a force” that the chuck drive shaft and the Locking effect in at least one operating state at two different locations a force on the striker.
  • the tool chuck drive shaft and the blocking element could exert a force on the tool chuck in two different places in at least one operating state.
  • the forces preferably have a component oriented in the same direction, preferably parallel to the axis of rotation of the tool chuck drive shaft, from the tool chuck drive shaft in the direction of the tool chuck.
  • the blocking element acts directly on the striker, but particularly preferably at least via a tool chuck bearing.
  • the tool chuck drive shaft acts directly on the striker.
  • the striker transmits a rotational movement from the chuck drive shaft to the tool chuck.
  • a hand tool with a hammer impact mechanism is proposed.
  • a "hand tool” is to be understood as meaning, in particular, a hand tool that appears appropriate to a person skilled in the art, but preferably a drill, a rotary hammer, a drill, a drill bit and / or a percussion hammer.
  • the hand tool is designed as a battery hand tool, That is to say, in particular, the hand tool has a coupling means which is provided to supply a drive motor of the hand tool with electrical power to a hand tool battery connected to the coupling means.
  • FIG. 1 shows a hand tool 10a, which is designed as a percussion drill.
  • the hand tool 10a has a pistol-shaped housing 12a.
  • a drive motor 14a of the hand tool 10a is arranged in the housing 12a.
  • the housing 12a has a handle region 16a and a battery coupling means 18a, which is arranged on an end of the handle region 16a facing away from the drive motor 14a.
  • the battery coupler 18a electrically and mechanically disconnectable by an operator, couples a hand tool battery 20a.
  • the hand tool battery 20a has an operating voltage of 10.8 volts, but could also have a different, in particular higher, operating voltage.
  • the hand tool 10a has a hammer hammer mechanism 22a according to the invention with a tool chuck 24a arranged on the outside and operating elements 26a, 28a.
  • FIG. 2 shows the hammer blower 22a in a sectional view.
  • the hammer blower 22a further comprises a planetary gear 30a and a chuck drive shaft 32a.
  • the planetary gear 30a in operation, rotates the tool chuck drive shaft 32a about an axis of rotation.
  • the planetary gear 30a has three planetary gear stages 34a, 36a, 38a.
  • a gear ratio of the planetary gear 30a between a rotor 40a of the drive motor 14a and the chuck drive shaft 32a is adjustable by an operator in at least two stages. Alternatively, a gear ratio between the drive motor 14a and the tool chuck drive shaft 32a could be unadjustable.
  • the hammer blower 22a has a torque limiting device 42a.
  • the torque limiting device 42a holds a ring gear 44a of the planetary gear 30a fixed in one operation.
  • the torque limiting device 42a fixation balls 46a, which engage in recesses of the ring gear 44a.
  • a spring 48a of the torque limiting device 42a exerts a force on the fixing balls 46a in the direction of the ring gear 44a.
  • An end of the spring 48a facing the fixing balls 46a is movable in the direction of the fixing balls 46a by the operator by means of one of the operating elements 26a.
  • the operating element 26a has an eccentric element.
  • the force acting on the fixing balls 46a force is adjustable.
  • the torque limiting device 42a is provided to limit a maximum torque transmittable via the tool chuck drive shaft 32a.
  • the hammer blower 22a has a beat generation unit 50a and a first coupling means 52a.
  • the first coupling means 52a is rotatably connected to the chuck drive shaft 32a, namely, the first coupling means 52a and the chuck drive shaft 32a are integrally formed.
  • the impact generating unit 50a has a second coupling means 54a, which in a drilling and / or a percussion drilling mode is non-rotatably connected to the first coupling means 52a.
  • the first coupling means 52a is formed as projections and the second coupling means 54a as recesses. Upon activation of the drilling mode, the first coupling means 52a dives into the second coupling means 54a, completely.
  • the coupling between the first coupling means 52a and the second coupling means 54a by an axial displacement of the tool chuck drive shaft 32a in the direction of the tool chuck 24a solvable.
  • a spring 56a of the hammer mechanism 22a is arranged between the first coupling means 52a and the second coupling means 54a.
  • the spring 56a urges the tool chuck drive shaft 32a toward the tool chuck 24a.
  • the beat generation unit 50a is switched off, it opens the coupling between the first coupling means 52a and the second coupling means 54a.
  • the hammer blower 22a has a first bearing 58a which fixes the second coupling means 54a relative to the housing 12a in the axial direction and rotatably supports coaxially with the tool chuck drive shaft 32a. Furthermore, the hammer mechanism 22a has a second bearing 60a, which rotatably supports the tool chuck drive shaft 32a on a side facing the drive motor 14a about the rotation axis. The second bearing 60a is integrally formed with one of the three planetary gear stages 38a.
  • the tool chuck drive shaft 32a has a coupling means 62a which connects it axially displaceably and non-rotatably with a planet carrier 64a of this planetary gear stage 38a.
  • this planetary gear stage 38a is provided for axially displaceably supporting the chuck drive shaft 32a.
  • the chuck drive shaft 32a is rotatably supported by a tool chuck bearing 70a together with the chuck 24a.
  • the tool chuck bearing 70a has a rear bearing element, which is pressed axially fixed on the tool chuck 24a.
  • the tool chuck bearing 70a has a front bearing member which axially supports the tool chuck 24a in the housing 12a.
  • the impact generation unit 50a includes a spur gear stage 72a that translates a rotational speed of the tool chuck drive shaft 32a to a higher rotational speed for impact generation.
  • a first gear 74a of the spur gear 72a is integrally formed with the second coupling means 54a. It is driven in a percussion drilling operation by the chuck drive shaft 32a.
  • a second gear 76a of the spur gear 72a is formed integrally with a hammer shaft 78a.
  • An axis of rotation of the percussion shaft 78a is disposed in the radial direction adjacent to the axis of rotation of the chuck drive shaft 32a.
  • the impact generating unit 50a has two bearings 80a which rotatably support the impactor shaft 78a in an axially fixed manner.
  • the impact generating unit 50a has a drive means 82a, which translates a rotational movement of the striking mechanism shaft 78a into a linear movement.
  • An eccentric element 84a of the drive means 82a is formed integrally with the striking mechanism shaft 78a.
  • An eccentric sleeve 86a of the drive means 82a is rotatably mounted relative to the eccentric member 84a on the eccentric member 84a, by means of a needle ring.
  • the eccentric sleeve 86a has a recess 88a, which surrounds a rocker arm 90a of the impact generating unit 50a.
  • the rocker arm 90a is pivotally supported on a tilting axis 92a of the impact generating unit 50a, pivotable about an axis perpendicular to the rotational axis of the tool chuck driving shaft 32a.
  • An end of the rocker arm 90a facing away from the drive means 82a partially encloses a racket 94a of the hammer impact mechanism 22a.
  • the rocker arm engages in a recess 96a of the racket 94a.
  • the recess 96a is annular.
  • the rocker arm 90a causes a force on the racket 94a to accelerate it.
  • the rocker arm 90a is moved sinusoidally during operation.
  • the rocker arm 90a is resilient.
  • the rocker arm 90a has a spring constant of about 30 N / mm.
  • the chuck drive shaft 32a supports the racket 94a movably in the direction of impact 98a.
  • the racket 94a defines a recess 100a.
  • the chuck drive shaft 32a penetrates the racket 94a through the recess 100a.
  • the racket 94a surrounds the recess 100a on a plane perpendicular to the recess 100a to 360 degrees.
  • the striker 94a strikes an anvil 102a of the hammer impactor 22a.
  • the striker 102a is disposed between an insert tool 104a and the racket 94a.
  • the insert tool 104a is fixed in an operative state in the tool chuck 24a.
  • the tool chuck 24a supports the striker 102a movably parallel to the impact direction 98a.
  • the striker 102a passes impact pulses coming from the striker 94a to the insert tool 104a during a percussion drilling operation.
  • the tool chuck drive shaft 32a is axially movable and rotatably connected to the striker 102a.
  • the striker 102a defines a recess 106a.
  • the tool chuck drive shaft 32a is partially disposed in the recess 106a of the striker 102a in an operative condition.
  • the tool chuck drive shaft 32a is rotatably supported via the striker 102a, the tool chuck 24a and the tool chuck bearing 70a.
  • the tool chuck 24a is driven in rotation via the anvil 102a.
  • the tool chuck 24a and the striker 102a each have a coupling means 108a, 110a, wherein the coupling means for transmitting the rotational movement to the tool chuck 24a are provided.
  • the coupling means 108a of the striker 102a is formed as a groove whose main extension is arranged parallel to the direction of impact 98a.
  • the coupling means 108a extends along a radially outer circumferential surface of the striker 102a.
  • the coupling means 110a of the tool chuck 24a is formed as a matching to the groove survey.
  • the tool chuck 24a has an insert tool coupling region 112a in which, during a drilling or screwing operation, the insert tool 104a is fixed in the direction of impact 98a or is movably fastened in the impact direction 98a during a percussion drilling operation.
  • the tool chuck has a taper 114a, which limits a movement range of the striker 102a in the direction of impact 98a.
  • the tool chuck 24a has a fastening ring 116a which delimits a movement region of the striker 102a against the impact direction 98a.
  • an operator presses the insert tool 104a against a workpiece not shown in detail. Thereby, the operator shifts the insertion tool 104a, the beatpiece 102a, and the tool chuck drive shaft 32a relative to the housing 12a in a direction opposite to the impact direction 98a, that is, toward the drive motor 14a. At this time, the operator presses the spring 56a of the hammer hammer 22a together.
  • the first coupling means 52a dips into the second coupling means 54a, whereby the tool chuck drive shaft 32a starts to drive the impact generation unit 50a.
  • the spring 56a pushes the tool chuck drive shaft 32a, the striker 102a and the insert tool 104a in the direction of impact 98a. Thereby, a rotationally fixed connection between the first coupling means 52a and the second coupling means 54a is opened, whereby the impact generating unit 50a is turned off.
  • the hammer mechanism 22a has a Schlager Wegungsabschalte unit 118a with a blocking element 120a, with a slotted guide 122a and with the control element 28a.
  • the locking member 120a causes a force on the striker 102a that acts on the striker 102a in parallel with at least one force of the tool chuck drive shaft 32a.
  • the force of the locking element 120a acts on the tool chuck bearing 70a via the tool chuck 24a and via the fastening ring 116a on the striker 102a.
  • the force of the blocking element 120a prevents axial displacement of the striker 102a and the tool chuck drive shaft 32a in a drilling or screwing mode and thus activation of the impact generating unit 50a.
  • the force of the chuck drive shaft 32a has an operatively parallel portion that rotationally drives the striker 102a during operation.
  • the force has a functionally and directionally parallel portion, which causes the spring 56a via the tool chuck drive shaft 32a on the striker 102a.
  • FIG. 4 is a perpendicular to the cut of the FIG. 2 and aligned parallel to the direction of impact 98a aligned section, wherein the operating element 28a in the sections of the Figures 2 and 4 is arranged in two different positions.
  • the operating element 28a is annular. It encloses the axis of rotation of the chuck drive shaft 32a, namely coaxially.
  • the operating element 28a is rotatably mounted. It is rotatably connected to the slide guide 122a.
  • the slide guide 122a is also annular.
  • the slide guide 122a has a bevel 124a.
  • the slope 124a connects two surfaces 126a, 128a of the slotted guide 122a.
  • the surfaces 126a, 128a are aligned perpendicular to the direction of impact 98a.
  • the surfaces 126a, 128a are arranged on different planes in the direction of impact 98a.
  • the blocking element 120a is disposed in a recess 130a bounded inter alia by the slope 124a and one of the surfaces 126a. This surface 126a is located closer to the drive motor 14a than the other surface 128a.
  • the housing 12a has a housing element 132a which rotatably supports the blocking element and displaceably supports it in the direction of impact 98a.
  • the locking member 120a can be pressed together with the tool chuck 24a at a start of a percussion drilling operation in a direction opposite to the striking direction 98a.
  • the blocking element 120a does not effect a locking force on the tool chuck 24a.
  • the blocking element 120a Upon rotation of the operating element 28a of the impact generation shut-off unit 118a, the blocking element 120a is moved by the slope 124a in the direction of impact 98a. The blocking element 120a is held in this forward position in the drilling or screwing mode. This prevents the blocking element 120a in the drilling or screwing mode, an axial displacement of the chuck drive shaft 32a.
  • FIGS. 5 to 11 Further embodiments of the invention are shown. The following descriptions and the drawings are essentially limited to the differences between the exemplary embodiments, with reference in principle to the same reference components, in particular with respect to components with the same reference numerals, to the drawings and / or the description of the other embodiments, in particular FIGS. 1 to 4 , can be referenced.
  • To distinguish the embodiments of the letter a is the reference numerals of the embodiment in the FIGS. 1 to 4 readjusted.
  • the letter a is replaced by the letters b to e.
  • FIG. 5 shows a part of a hammer blower 22b.
  • a beater 94b of a beating unit 50b of the hammer blower 22b is movably supported on a tool chuck drive shaft 32b of the hammer blower 22b.
  • the tool chuck drive shaft 32b is axially displaceable and non-rotatably connected to an anvil 102b of the hammer impact mechanism 22b.
  • the striker 102b has a coupling means 108b which, in at least one operating state, forms a rotationally fixed connection to a tool chuck 24b of the hammer impact mechanism 22b.
  • the coupling means 108b is disposed on a side facing a taper 114b of the tool chuck 24b.
  • the coupling means 108b is formed as a toothing.
  • a seal portion 134b of the striker tapers against the tool chuck 24b and advantageously prevents dust from entering the impact generation unit 50b.
  • FIG. 6 shows how FIG. 5 schematically a part of a hammer impact mechanism 22c.
  • a beater 94c of a beating unit 50c of the hammer blower 22c is movably supported on a tool chuck drive shaft 32c of the hammer blower 22c.
  • the chuck drive shaft 32c is axially displaceable and non-rotatably connected to an anvil 102c of the hammer impactor 22c.
  • the striker 102c has a coupling means 108c which, in at least one operating state, forms a rotationally fixed connection to a tool chuck 24c of the hammer impact mechanism 22c.
  • the tool chuck 24c has an insert tool coupling region 112c into which the coupling means 108c of the striker 102c at least partially intervenes.
  • the one insert tool coupling region 112c is intended to cause circumferentially forces on an insert tool during operation.
  • the coupling means 108c is disposed in an operative state at least partially within a taper 114c of the tool chuck 24c.
  • the coupling means 108c is formed as an external hexagon. The dimensions of the external hexagon correspond to those which usually has one bit for a screwing operation.
  • a sealing area 134c of the anvil 102c rests against the tool chuck 24c without teeth, and prevents inexpensively and advantageously the penetration of dust into the impact generating unit 50c. In particular, fat loss can be minimized.
  • FIGS. 7 to 10 also show in section and in perspective a part of a hammer impact mechanism 22d.
  • a beater 94d of a beating unit 50d of the hammer blower 22d is movably supported on a tool chuck drive shaft 32d of the hammer blower 22d.
  • the tool chuck drive shaft 32d is axially displaceable and rotatably connected to an anvil 102d of the hammer impact mechanism 22d.
  • the striker 102d has a coupling means 108d, which forms a rotationally fixed connection to a tool chuck 24d of the hammer impact mechanism 22d in at least one operating state.
  • the coupling means 108d is disposed in an operative state at least partially within a taper 114d of the tool chuck 24d.
  • the coupling means 108d is designed as a toothing with two coupling ribs lying opposite one another with respect to a rotation axis.
  • the coupling means 108d has a same shape and dimensions as a coupling means for coupling with an insertion tool. The shape and dimensions correspond to the standard SDS-Quick.
  • a sealing area 134d of the striker 102d rests on the tool chuck 24d without teeth.
  • FIG. 11 shows how FIG. 5 schematically a part of a hammer impact mechanism 22e.
  • a beater 94e of a beating unit 50e of the hammer impactor 22e is movably supported on a tool chuck drive shaft 32e of the hammer impactor 22e.
  • the chuck drive shaft 32e is axially fixed and non-rotatably connected to an anvil 102e of the hammer impactor 22e.
  • the chuck drive shaft 32e and the anvil 102e are integrally formed.
  • the striker 94e moves the tool chuck drive shaft 32e and the striker 102e together in the direction of impact 98e.
  • the Tool chuck drive shaft 32e is axially displaceable by means of a coupling means 62e and rotationally fixed with a in the embodiment of FIGS. 1 to 4 connected planetary gear stage connected.

Landscapes

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

Claims (12)

  1. Mécanisme de percussion à marteau comprenant au moins une unité de génération de percussion (50a-e) qui comprend un percuteur (94a-e), caractérisé par un arbre d'entraînement de mandrin d'outil (32a-e) qui, dans au moins un état de fonctionnement, supporte de manière mobile le percuteur (94a-e) dans la direction de percussion (98a ; 98e), et un moyen d'accouplement (52a) qui est relié de manière solidaire en rotation à l'arbre d'entraînement de mandrin d'outil (32a-e) et est prévu pour entraîner l'unité de génération de percussion (50a,e).
  2. Mécanisme de percussion à marteau selon la revendication 1, caractérisé en ce que le moyen d'accouplement (52a) est réalité d'une seule pièce avec l'arbre d'entraînement de mandrin d'outil (32a-e).
  3. Mécanisme de percussion à marteau selon la revendication 1 ou 2, caractérisé en ce que le moyen d'accouplement (52a) est prévu pour s'enfoncer dans un moyen d'accouplement (54a) de l'unité de génération de percussion (50a-e) lors d'une activation d'au moins un mode de percussion.
  4. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé en ce que l'arbre d'entraînement de mandrin d'outil (32a-e) traverse au moins partiellement le percuteur (94a-e).
  5. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé par au moins un palier (60a) qui est prévu pour supporter de manière axialement déplaçable l'arbre d'entraînement de mandrin d'outil (32a-e).
  6. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé par une transmission planétaire (30a) qui entraîne l'arbre d'entraînement de mandrin d'outil (32a-e) dans au moins un état de fonctionnement.
  7. Mécanisme de percussion à marteau selon les revendications 5 et 6, caractérisé en ce que l'arbre d'entraînement de mandrin d'outil (32a-e) comprend un moyen d'accouplement (62a ; 62e) supplémentaire qui est prévu pour réaliser une liaison solidaire en rotation axialement déplaçable par rapport à la transmission planétaire (30a).
  8. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé par un dispositif de limitation de couple (42a) qui est prévu pour limiter un couple maximal pouvant être transmis par le biais de l'arbre d'entraînement de mandrin d'outil (32a).
  9. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé par un mandrin d'outil (24a) et une bouterolle (102a) comprenant un moyen d'accouplement (108a) qui est prévu pour la transmission d'un mouvement de rotation au mandrin d'outil (24a).
  10. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de génération de percussion (50a) comprend un étage de transmission à pignons droits (72a) qui multiplie une vitesse de rotation de l'arbre d'entraînement de mandrin d'outil (32a) en une vitesse de rotation plus élevée pour la génération de percussion.
  11. Mécanisme de percussion à marteau au moins selon la revendication 9, caractérisé par une unité de désactivation de génération de percussion (118a) comprenant un élément de blocage (120a) qui, au moins lors d'un fonctionnement de perçage, agit sur la bouterolle (102a) parallèlement à une force de l'arbre d'entraînement de mandrin d'outil (32a).
  12. Outil à main comprenant un mécanisme de percussion à marteau (22a) selon l'une quelconque des revendications précédentes.
EP11770108.6A 2010-11-29 2011-10-14 Mécanisme de percussion à marteau Active EP2646198B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010062106 2010-11-29
DE102011007691A DE102011007691A1 (de) 2010-11-29 2011-04-19 Hammerschlagwerk
PCT/EP2011/067974 WO2012072328A1 (fr) 2010-11-29 2011-10-14 Mécanisme de percussion à marteau

Publications (2)

Publication Number Publication Date
EP2646198A1 EP2646198A1 (fr) 2013-10-09
EP2646198B1 true EP2646198B1 (fr) 2014-07-30

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US (1) US9434059B2 (fr)
EP (1) EP2646198B1 (fr)
CN (1) CN103221183A (fr)
DE (1) DE102011007691A1 (fr)
WO (1) WO2012072328A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011078628A1 (de) * 2011-07-05 2013-01-10 Robert Bosch Gmbh chlagwerkvorrichtung
DE102017211772A1 (de) * 2016-07-11 2018-01-11 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
DE102019220153A1 (de) * 2019-12-19 2021-06-24 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung für eine Handwerkzeugmaschine

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Publication number Priority date Publication date Assignee Title
DE1834737U (de) * 1961-04-29 1961-07-13 Hombak Maschinenfab Kg Verstellbares widerlager an holzzerspanungsmaschinen.
NL8304043A (nl) * 1983-11-24 1985-06-17 Skil Nederland Nv Inrichting voor het aandrijven van een boor- en/of slaggereedschap.
DE3611890A1 (de) * 1985-12-17 1987-10-15 Licentia Gmbh Antrieb fuer das schlagwerk eines elektropneumatisch arbeitenden drehschlagbohrhammers
EP1834737A1 (fr) * 2006-03-18 2007-09-19 Metabowerke GmbH Outil à main électrique
CN101342693B (zh) * 2007-07-12 2011-08-03 苏州宝时得电动工具有限公司 动力工具
DE102007062248A1 (de) * 2007-12-21 2009-06-25 Robert Bosch Gmbh Handwerkzeugmaschine mit einer, mindestens eine drehbar gelagerte Zwischenwelle umfassenden Getriebevorrichtung
ATE554883T1 (de) * 2008-07-01 2012-05-15 Metabowerke Gmbh Schlagschrauber

Also Published As

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WO2012072328A1 (fr) 2012-06-07
CN103221183A (zh) 2013-07-24
US20130319708A1 (en) 2013-12-05
US9434059B2 (en) 2016-09-06
DE102011007691A1 (de) 2012-05-31
EP2646198A1 (fr) 2013-10-09

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