EP2646201B1 - Mécanisme de percussion à marteau - Google Patents

Mécanisme de percussion à marteau Download PDF

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Publication number
EP2646201B1
EP2646201B1 EP11768040.5A EP11768040A EP2646201B1 EP 2646201 B1 EP2646201 B1 EP 2646201B1 EP 11768040 A EP11768040 A EP 11768040A EP 2646201 B1 EP2646201 B1 EP 2646201B1
Authority
EP
European Patent Office
Prior art keywords
tool chuck
impact
drive shaft
hammer
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
EP11768040.5A
Other languages
German (de)
English (en)
Other versions
EP2646201A1 (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 EP2646201A1 publication Critical patent/EP2646201A1/fr
Application granted granted Critical
Publication of EP2646201B1 publication Critical patent/EP2646201B1/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
    • 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
    • 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
    • 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
    • B25D2216/0038—Tools having a rotation-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
    • B25D2216/0069—Locking means
    • 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
    • B25D2217/0023—Pistons

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 translatory, striking movement of a hammer of the hammer impact mechanism suitable for a 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.
  • a “tool chuck drive shaft” is to be understood in particular as a shaft which is used in a drilling and / or percussion drilling operation transmits a rotational movement of a transmission, in particular a planetary gear, in the direction of a tool chuck.
  • the tool chuck drive 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.
  • 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.
  • 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. Due to the inventive design of the hammer impact mechanism can be achieved structurally simple and space-saving a particularly advantageous ratio between speed and stroke rate of an insert tool.
  • the impact generating unit has a percussion shaft whose axis of rotation is arranged in the radial direction next to the tool chuck drive shaft, whereby a particularly effective and low-vibration impact generation can be achieved.
  • a particularly advantageous leverage of the rocker arm can be achieved.
  • a "striking mechanism shaft” is to be understood, in particular, as meaning a shaft which rotatably fixes at least a part of the drive means of the impact generating unit about an axis.
  • the impactor shaft at least during a percussion drilling operation only delivers power to the drive means, which at least partially acts on a workpiece.
  • the percussion shaft shaft does not deliver any power to the tool chuck that rotatably drives the tool chuck.
  • at least one plane aligned perpendicular to the axes of rotation intersects the tool chuck drive shaft and the percussion shaft.
  • the impact generating unit has at least one bearing, which is provided to support the percussion shaft axially fixed, whereby a particularly low design effort can be achieved.
  • a bearing is to be understood as meaning, in particular, a means which is provided for rotatably fastening the impact generation unit about an axis of rotation relative to a housing.
  • the phrase "axially fixed” is understood to mean that the bearing immobile supports the percussion mechanism shaft relative to the housing in a direction parallel to the axis of rotation.
  • the impact generating unit has a racket, which supports the tool chuck drive shaft in at least one operating state in the direction of impact, whereby a low weight and a small size are possible.
  • the term "bat” is to be understood as meaning a means of the hammer impact mechanism which is intended to be accelerated in particular translationally during operation by the impact generation unit and to emit a pulse recorded during the acceleration as impact pulse in the direction of an insertion tool.
  • the racket is by an air pressure or advantageously by the rocker arm in the direction of impact accelerated stored.
  • the racket is unaccelerated immediately prior to a strike.
  • the racket is preferably in a shock from a shock pulse in the direction of the insert tool, in particular via a striker, to the insert tool.
  • 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.
  • 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 axially displaceably support the tool chuck drive shaft, whereby a structurally simple impact mechanism shutdown is possible.
  • a “bearing” is to be understood in this context, in particular a device which attaches the tool chuck drive shaft, in particular relative to the housing movable at least about the axis of rotation.
  • the term “axially displaceable” should be understood to mean that the bearing movably fixes the tool chuck drive shaft, in particular relative to the 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, which achieves an advantageous translation in a small space can be. 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 planet gear carried on a circular path around the sun gear by the planet carrier.
  • the planetary gear has at least two selectable by the operator gear ratios between an input and an output of the planetary gear.
  • 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.
  • tool chuck is to be understood as a device which is intended to fix the insert tool detachably, at least non-rotatably, by an operator, in particular without tools.
  • 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.
  • 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 means is designed as a coupling that appears meaningful to a person skilled in the art, but advantageously a jaw coupling and / or a toothing.
  • the coupling means has a plurality of positive locking elements and a region connecting the interlocking elements.
  • the hammer impact mechanism comprises a coupling means which is rotatably connected to the tool chuck drive shaft and which is intended to drive the impact generating unit, whereby a particularly compact and powerful hammer impact mechanism can be provided structurally simple.
  • 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.
  • driving in this context should be understood to mean that 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 hammer impact mechanism comprises a Schlager Wegungsabschalte unit with a locking element which acts at least during a drilling operation and in particular a screw parallel to at least one force of the tool chuck drive shaft on the striker, whereby an advantageous arrangement of an operating element of 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 preferably prevents a particularly automatic activation of the impact generation unit when the 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 an axial displacement of the tool chuck drive shaft, the tool chuck and / or advantageously the striker in the drilling and / or screwing mode.
  • the phrase "parallel to a force" should be understood to mean that the tool chuck drive shaft and the blocking element in at least one operating state at two different places a force on the striker cause.
  • 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.
  • the hammer impact mechanism comprises 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 used comfortably and efficiently 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.
  • 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, in particular, the hand tool has a coupling means, which is provided to supply a drive motor of the hand tool from a connected to the coupling means hand tool battery with an electrical energy.
  • 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.
  • 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 impact mechanism 22a on a second bearing 60a, the tool chuck drive shaft 32a on a side facing the drive motor 14a side about the axis of rotation rotatably supports.
  • 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 / imm.
  • 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 striker 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 are provided for transmitting the rotational movement to the tool chuck 24a.
  • 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 applies a force to 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 blocking element 120a acts on the striker 102a via the tool chuck bearing 70a, via the tool chuck 24a and via the fastening ring 116a.
  • Axial displacement of the striker 102a and tool chuck drive shaft 32a and thus activation of the impact generation unit 50a is prevented by the force of the locking member 120a in a drilling or screwing mode.
  • the force of the tool chuck drive shaft 32a is operatively parallel Proportion which rotationally drives the striker 102a in 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. As a result, the blocking element 120a prevents axial displacement of the tool chuck drive shaft 32a in the drilling screwing mode.
  • 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 embodiments, wherein with respect to the same named components, in particular with respect to components with the same reference numerals, in principle also to the drawings and / or the description of the other embodiments, in particular the 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 in which the coupling means 108c of the striker 102c at least partially engages.
  • 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 hexagon correspond to those that one bit for one Screwing usually has.
  • 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 have much the 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 tool chuck drive shaft 32e is akial fixed and rotatably connected to an anvil 102e of the hammer mechanism 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 (11)

  1. Mécanisme de percussion à marteau comprenant au moins une transmission (30a), une unité de génération de percussions (50a-e) et un arbre d'entraînement de mandrin d'outil (32a-e), lequel, en mode de perçage et/ou de perçage à percussion, transmet un mouvement de rotation de la transmission (30a) dans la direction d'un mandrin d'outil (24a), caractérisé en ce que l'unité de génération de percussions (50a-e) présente un étage de transmission à pignons droits (72a) qui est prévu pour multiplier une vitesse de rotation de l'arbre d'entraînement de mandrin d'outil (32a-e) à une vitesse de rotation plus élevée en vue de générer des percussions.
  2. Mécanisme de percussion à marteau selon la revendication 1, caractérisé en ce que l'unité de génération de percussions (50a-e) présente un arbre de mécanisme de percussion (78a), dont l'axe de rotation est disposé dans la direction radiale à côté de l'arbre d'entraînement de mandrin d'outil (32a-e).
  3. Mécanisme de percussion à marteau selon la revendication 2, caractérisé en ce que l'unité de génération de percussions (50a-e) présente au moins un palier (80a), qui est prévu pour supporter de manière fixée axialement l'arbre de mécanisme de percussion (78a).
  4. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de génération de percussions (50a-e) présente un dispositif de percussion (94a-e) qui supporte de manière mobile l'arbre d'entraînement de mandrin d'outil (32a-e) dans au moins un état de fonctionnement dans la direction de percussion (98a).
  5. Mécanisme de percussion à marteau selon la revendication 4, caractérisé en ce que l'arbre d'entraînement de mandrin d'outil (32a-e) traverse au moins en partie le dispositif de percussion (94a-e).
  6. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé par un palier (60a) qui est prévu pour supporter de manière déplaçable axialement l'arbre d'entraînement de mandrin d'outil (32a).
  7. Mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes, caractérisé en ce que la transmission (30a) est réalisée sous forme de transmission planétaire (30a) qui entraîne dans au moins un état de fonctionnement l'arbre d'entraînement de mandrin d'outil (32a).
  8. 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).
  9. Mécanisme de percussion à marteau selon au moins la revendication 4, caractérisé par un moyen d'accouplement (52a), qui est connecté de manière solidaire en rotation à l'arbre d'entraînement de mandrin d'outil (32a-e) et qui est prévu pour entraîner l'unité de génération de percussions (50a-e).
  10. Mécanisme de percussion à marteau selon au moins la revendication 8, 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 au moins une force de l'arbre d'entraînement de mandrin d'outil (32a).
  11. Outil à main comprenant un mécanisme de percussion à marteau selon l'une quelconque des revendications précédentes.
EP11768040.5A 2010-11-29 2011-10-14 Mécanisme de percussion à marteau Active EP2646201B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010062094A DE102010062094A1 (de) 2010-11-29 2010-11-29 Hammerschlagwerk
PCT/EP2011/067968 WO2012072327A1 (fr) 2010-11-29 2011-10-14 Mécanisme de percussion à marteau

Publications (2)

Publication Number Publication Date
EP2646201A1 EP2646201A1 (fr) 2013-10-09
EP2646201B1 true EP2646201B1 (fr) 2014-08-06

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EP11768040.5A Active EP2646201B1 (fr) 2010-11-29 2011-10-14 Mécanisme de percussion à marteau

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US (1) US9636814B2 (fr)
EP (1) EP2646201B1 (fr)
CN (1) CN103221184A (fr)
DE (1) DE102010062094A1 (fr)
WO (1) WO2012072327A1 (fr)

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Also Published As

Publication number Publication date
EP2646201A1 (fr) 2013-10-09
US9636814B2 (en) 2017-05-02
DE102010062094A1 (de) 2012-05-31
CN103221184A (zh) 2013-07-24
US20130319709A1 (en) 2013-12-05
WO2012072327A1 (fr) 2012-06-07

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