EP2646198A1 - Mécanisme de percussion à marteau - Google Patents

Mécanisme de percussion à marteau

Info

Publication number
EP2646198A1
EP2646198A1 EP11770108.6A EP11770108A EP2646198A1 EP 2646198 A1 EP2646198 A1 EP 2646198A1 EP 11770108 A EP11770108 A EP 11770108A EP 2646198 A1 EP2646198 A1 EP 2646198A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
tool chuck
impact
tool
hammer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11770108.6A
Other languages
German (de)
English (en)
Other versions
EP2646198B1 (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

Links

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 hammer blower with at least one impact generating unit comprising a racket with a chuck drive shaft which movably supports the racket in at least one operating state, and with a coupling means which is rotatably connected to the chuck drive shaft and which is provided to the impact generating unit to propose, proposed.
  • a "impact generation unit” is to be understood in particular as meaning a unit which is intended to translate a rotational movement into a suitable, in particular translatory, striking movement of the racquet for a drilling and percussion drilling operation
  • a beating lever is preferably designed as a pneumatic beating unit and / or particularly preferably as a beater with a rocker arm first output coupling power to a second coupling area.
  • 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 "chuck drive shaft” is to be understood as meaning, in particular, 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 designed as a solid shaft.
  • the chuck drive shaft extends in the direction of impact over at least 40 mm.
  • the chuck drive shaft and the tool chuck are in a drilling and / or
  • the term "tool chuck” should be understood to mean a device which is intended to fix an insert tool detachably, at least non-rotatably, directly by an operator, without a tool, by a "direction of impact" to a rotational axis 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 term "movably support” is to be understood as meaning that the tool chuck drive shaft has a bearing surface which transmits bearing forces perpendicular to the direction of impact to the racket in at least one operating state to transmit at least by a positive connection movement from one component to another component.
  • 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. In particular, that is
  • the coupling means has a plurality of positive locking elements and a region connecting the interlocking elements.
  • rotationally fixed should be understood to mean that the coupling means and the tool chuck drive shaft are firmly connected to one another at least in the circumferential direction, preferably in each direction, specifically in each operating state be understood equipped.
  • driving in this context should be understood to mean that the coupling means has a kinetic energy, in particular a rotational energy, on at least one region of the
  • Impact generating unit transfers.
  • 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 connected to the tool chuck drive shaft in another manner which appears appropriate to the person skilled in the art, but is advantageously pressed, screwed and / or connected in a form-fitting manner in the circumferential direction and axially via a securing ring or a band.
  • in one piece is meant, in particular, at least materially bonded, for example by a welding process, a bonding process, an injection molding process and / or another process that appears expedient to the person skilled in the art, and / or advantageously shaped in one piece, for example by a production from a casting 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.
  • a "activation of a striking mode” is to be understood as meaning, in particular, a setting process in which, in particular, the operator adjusts the hammer impact mechanism in such a way that during operation the whipping production unit drives the hammer in a striking manner
  • 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 be understood limited region, the coupling means on at least one plane, which is advantageously aligned perpendicular to the direction of impact, by more than 180 degrees, preferably by more than 270 degrees, particularly advantageously 360 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.
  • the term "at least partially penetrate” is to be understood as meaning that the club surrounds the tool chuck drive shaft by more than 270 degrees, advantageously by 360 degrees, on at least one plane, which is advantageously aligned perpendicular to the direction of impact a direction perpendicular to the axis of rotation of the tool chuck drive shaft positively secured to the tool chuck drive shaft, that is movably mounted in the direction of the axis of rotation.
  • the hammer impact mechanism comprises at least one bearing which is provided for axially displaceably supporting the tool chuck drive shaft, whereby a structurally simple impact mechanism shut-off is possible.
  • a “bearing” is to be understood in particular as meaning a device which fixes the tool chuck drive shaft, in particular relative to a housing, so as to be movable and axially displaceable at least about the axis of rotation and is to be understood to mean “axially displaceable” that the bearing is the tool chuck drive shaft in particular relative to a housing attached movable parallel to the direction of impact.
  • a connection of the coupling means of the tool chuck drive shaft which drives 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 set preferably has a sun gear, a ring gear, a planet carrier and at least one planet wheel guided on a circular path around the sun gear by the planet carrier Planetary gear 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.
  • torque limiting device prevents the maximum torque, in particular adjustable by an operator, from being preferably opened by a torque limiting device between a drive motor and the tool chuck act on a power 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 as meaning an element of the hammer impact mechanism which transmits the impact pulse from the striker in the direction of the insertion tool in a striking operation of dust through the tool chuck in the hammer blower.
  • the impact generating 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 stroke rate of an insert 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 term "rotational speed for impact generation” should be understood as meaning a rotational speed of a drive means of the impact generation unit that appears appropriate to a person skilled in the art, 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
  • 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 whipping production shut-off unit with a blocking element which, at least at one
  • an annular operating element which encloses the striker or the tool chuck drive shaft can be implemented easily. In addition, little space is needed with this design.
  • a "impact generation shut-off unit” is to be understood in particular as meaning a unit which is provided to enable an operator to switch off the impact generation unit for a drilling and / or screwing operation
  • pressing in a chisel and / or percussion drilling mode causes an axial displacement of the chuck drive shaft
  • the blocking element is provided for axial displacement of the tool chuck secondary shaft, the tool chuck and / or advantageously
  • the phrase "parallel to a force” is to be understood to mean that the tool chuck drive shaft and the blocking element in at least one operating state at two and different places cause 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 hammer drill, 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 with a hammer impact mechanism according to the invention in a perspective view
  • FIG. 3 shows a coupling means, a tool chuck drive shaft, a striker and a part of a tool chuck of the hammer impact mechanism from FIG. 1, each shown individually in a perspective view, FIG.
  • FIG. 4 shows a further partial section of the hammer impact mechanism from FIG. 1, which shows a impact generation shut-off unit of the hammer impact mechanism
  • FIG. 5 shows a first alternative embodiment of a striker of the
  • FIG. 6 shows a second alternative embodiment of a striker of the
  • Fig. 7 shows a third alternative embodiment of a striker of the
  • FIG. 8 shows the striker of Figure 7 in a first perspective view
  • 9 shows the striker of Figure 7 in a second perspective view
  • Fig. 10 shows a part of a tool chuck of the hammer impact mechanism of Figure 7 in a perspective view
  • Fig. 1 1 shows a fourth alternative embodiment of a striker of the
  • 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 impact mechanism 22a according to the invention with a tool chuck 24a arranged on the outside and operating elements 26a, 28a.
  • Figure 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
  • 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 on fixing 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 fixing balls 46a are pushed out of the recesses and the ring gear 44a free, thereby interrupting power transmission between the rotor 40a and the tool chuck drive shaft 32a.
  • 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 are 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 impact mechanism 22a has a first bearing 58a, which fixes the second coupling means 54a relative to the housing 12a in the axial direction and rotatably supported coaxially with the tool chuck drive shaft 32a. Furthermore, the hammer impact mechanism 22a on a second bearing 60a, which rotatably supports the Malawifutteran- drive shaft 32a on a side facing the drive motor 14a side 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 generating unit 50a comprises a spur gear stage 72a which converts a rotational speed of the tool chuck drive shaft 32a into a higher rotational speed
  • 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.
  • the 84a of the drive means 82a is integrally formed with the percussion gear 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 drive 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. He has a spring constant between the eccentric sleeve 86 a and the
  • 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 12a in which, during a drilling or screwing operation, the insert tool 104a is fixed in the direction of impact 98a or is movably mounted in the impact direction 98a in 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 striker 102a, and the chuck drive shaft 32a relative to the housing 12a in a direction opposite to the striking direction 98a, that is, toward the driving 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
  • 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.
  • Locking elements 120a act via the tool chuck bearing 70a, via the tool feed 24a and the attachment 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 is operatively parallel
  • Proportion which rotationally drives the striker 102a in operation 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 shows a section oriented perpendicular to the section of FIG. 2 and parallel to the direction of impact 98a, wherein the operating element 28a is arranged in the sections of FIGS. 2 and 4 in two different positions.
  • the operating element 28a is annular. It encloses the axis of rotation of the chuck drive shaft 32a, namely coaxially.
  • 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 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.
  • a Schlagbohrvorgang causes the
  • Locking element 120a no 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 1 18a, 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 show further exemplary embodiments of the invention. The following descriptions and the drawings are limited to
  • FIG. 5 shows a part of a hammer impact mechanism 22b.
  • the impact generating unit 50b of the hammer impactor 22b is movably supported on a tool chuck drive shaft 32b of the hammer impactor 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 arranged on a side which faces a taper 1 14b of the tool chuck 24b.
  • the coupling means 108b is formed as a toothing.
  • a sealing portion 134b of the striker engages with the tool chuck 24b in an intermeshed manner and advantageously prevents dust from entering the impact generating unit 50b.
  • FIG. 6, like FIG. 5, shows 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 arranged in an operational 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 likewise show a 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 1 14d 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. 1 shows 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 tool chuck drive shaft 32e and the striker 102e are integrally formed. In one stroke, 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 rotatably connected to a planetary gear stage described in the embodiment of Figures 1 to 4.

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

Abstract

L'invention concerne un mécanisme de percussion à marteau comprenant : - au moins une unité de génération de percussion (50a-e) qui présente un marteau (94a-e), - un arbre d'entraînement (32a-e) qui est destiné au mandrin de serrage et qui, dans au moins un mode de fonctionnement, assure le montage du marteau (94a-e) mobile dans la direction de frappe (98a; 98e), et –un moyen de couplage (52a) qui est relié solidaire en rotation avec l'arbre d'entraînement (32a-e) du mandrin de serrage et qui est destiné à entraîner l'unité de génération de percussion (50a-e).
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 true EP2646198A1 (fr) 2013-10-09
EP2646198B1 EP2646198B1 (fr) 2014-07-30

Family

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Application Number Title Priority Date Filing Date
EP11770108.6A Active EP2646198B1 (fr) 2010-11-29 2011-10-14 Mécanisme de percussion à marteau

Country Status (5)

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

Families Citing this family (3)

* 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

Family Cites Families (7)

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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

Non-Patent Citations (1)

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Title
See references of WO2012072328A1 *

Also Published As

Publication number Publication date
EP2646198B1 (fr) 2014-07-30
US20130319708A1 (en) 2013-12-05
DE102011007691A1 (de) 2012-05-31
CN103221183A (zh) 2013-07-24
WO2012072328A1 (fr) 2012-06-07
US9434059B2 (en) 2016-09-06

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