EP2265419B1 - Machine manuelle pour outils entraînés en frappe - Google Patents

Machine manuelle pour outils entraînés en frappe Download PDF

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Publication number
EP2265419B1
EP2265419B1 EP08873253.2A EP08873253A EP2265419B1 EP 2265419 B1 EP2265419 B1 EP 2265419B1 EP 08873253 A EP08873253 A EP 08873253A EP 2265419 B1 EP2265419 B1 EP 2265419B1
Authority
EP
European Patent Office
Prior art keywords
counter
drive
power tool
oscillator
stroke
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
EP08873253.2A
Other languages
German (de)
English (en)
Other versions
EP2265419A1 (fr
Inventor
Otto Baumann
Hardy Schmid
Tobias Herr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2265419A1 publication Critical patent/EP2265419A1/fr
Application granted granted Critical
Publication of EP2265419B1 publication Critical patent/EP2265419B1/fr
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Classifications

    • 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
    • B25D17/24—Damping the reaction force
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • 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
    • B25D2250/045—Cams used in percussive 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
    • B25D2250/175—Phase shift of tool components

Definitions

  • the invention relates to a hand machine tool according to the preamble of independent claim 1 and as from WO 2008/010467 A1 described.
  • a hand machine tool for impact driven tools in particular a hammer drill and / or chisel hammer, is already known, which has an air cushion hammer mechanism with an impact axis and an intermediate shaft parallel to it, the exciter sleeve of the air cushion hammer mechanism being driven by means of a lift generator device designed as a wobble drive.
  • the wobble drive comprises a wobble plate with an integrally formed wobble finger, which is mounted on a drive sleeve by means of a wobble bearing in such a way that the wobble finger is axially deflected by means of a track of the bearing elements provided on the drive sleeve and tilted at an angle to the intermediate shaft by rotating the intermediate shaft is moved.
  • vibrations are generated in the handheld power tool. These oscillations are transmitted as vibrations to the housing of the handheld power tool and from there to an operator via the handle of the handheld power tool.
  • the handheld power tool has the DE 198 51 888 a counterweight designed as a counter-oscillator, which is driven by means of a second wobble finger formed on the wobble plate diametrically opposite the first wobble finger.
  • the diametrically opposite arrangement of the wobble fingers results in a phase shift ⁇ of 180 ° between the axial deflection movements of the wobble fingers.
  • the inertial forces that are set by the oscillating deflection movement of the exciter sleeve are particularly high at the reversal points, i.e. in the area of the maximum speed changes that occur, so that their compensation is particularly effective with a phase shift ⁇ of the counter-oscillator of 180 ° to the deflection movement of the exciter sleeve.
  • air forces occur in air cushion impact mechanisms, among other things due to cyclically changing pressure conditions in the air cushion of the air cushion impact mechanism, which also stimulate vibrations.
  • the air forces can even outweigh the inertia forces.
  • the maximum of the air forces is achieved by the compression of the air cushion typically between 260 ° and 300 ° after the front dead center of the axial movement of the exciter sleeve. From the DE 10 2007 061 716 A1 a hammer drill is known in which a second wobble finger is integrally formed on the wobble plate, but which includes an angle other than 180 ° to the first wobble finger for the exciter sleeve drive.
  • a phase difference ⁇ not equal to 180 ° is achieved between a deflection of the exciter sleeve by the first wobble finger and a deflection of a counter-oscillator by means of the second wobble finger.
  • the effect of the counter-oscillator on both vibration-generating forces - mass and air forces - can be achieved.
  • the arrangement of the DE 10 2007 061 716 A1 is, however, characterized by a severe restriction in terms of installation space, since the counter-oscillator must be arranged in the area of the optimal angular position of the second wobble finger, the installation space being limited by the air cushion hammer mechanism and necessary bearing elements.
  • the second wobble finger performs a non-linear, complex movement, so that the reception of the wobble finger on the counter-oscillator must have complex bearings.
  • the handheld power tool according to the invention which includes the features of independent main claim 1, has the advantage that the phase position of the movement of the counter-oscillator can be coordinated particularly effectively with the vibration-stimulating effective forces resulting from the mass and air forces.
  • the separate drive of the counter-oscillator also results in the advantage that the counter-oscillator can be arranged in a space-saving manner in the machine housing without the need for particularly complex mountings.
  • a compact design of a handheld power tool according to the invention is preferably achieved by driving the at least one additional second stroke generating device through the intermediate shaft.
  • the first stroke generating device is preferably arranged on or on a region of the intermediate shaft facing a drive motor.
  • the at least one additional stroke generating device is arranged on or on a region of the intermediate shaft facing away from the drive motor.
  • a handheld power tool according to the invention in which a bearing device fixed to the housing of a machine housing of the handheld power tool for rotatable mounting of the intermediate shaft is preferably provided between the first stroke generating device and the at least one additional second stroke generating device, has particularly good rotational decoupling of the intermediate shaft from the machine housing. It is advantageous here that the transverse forces caused by the two stroke generating devices, which act on the intermediate shaft, are introduced proportionally on both sides of the bearing device.
  • a particularly effective drive of the counter-oscillator is preferably achieved by a phase shift other than 90 °.
  • the phase shift ⁇ between the movement of the first lifting element and the movement of the second lifting element is preferably between 190 ° and 260 °. In a particularly preferred embodiment, the phase shift ⁇ is between 200 ° and 240 °.
  • a particularly effective embodiment of the counter-oscillator preferably has at least one counter-oscillating mass. This is guided along a linear or non-linear movement path, in particular along a straight line or a circular arc.
  • a compact and at the same time effective design of the counter-oscillator preferably has a center of gravity path that is close to the impact axis.
  • the path of the center of gravity lies parallel, preferably coaxially, to the impact axis.
  • the second stroke generating device has a coupling device.
  • the second stroke generating device can be coupled to the first of the stroke generating device in a rotationally fixed manner.
  • the second Stroke generating device is activated only in selected operating states of the hand power tool. For example, deactivation of the second Stroke generating device can be advantageous in an idle state of the hand power tool.
  • the clutch device is designed as an engagement clutch.
  • an axial displacement path between an engaged state and an open state is provided.
  • the second stroke generating device has an additional deflection element.
  • a second counter-oscillator can preferably be driven by the additional deflection element.
  • the movement of the additional deflecting element has a second phase shift ⁇ A , which in particular differs from the phase shift ⁇ .
  • the first stroke generating device is designed as a first wobble drive.
  • the first wobble drive comprises a drive sleeve carrying at least one first raceway, a wobble bearing and a wobble plate.
  • a wobble finger is arranged on the wobble plate as a lifting element, preferably integrally formed.
  • the second stroke generating device is designed as a second wobble drive.
  • This second wobble drive comprises at least one second drive sleeve carrying a second track, a second wobble bearing and a second wobble plate with a wobble finger arranged thereon.
  • the drive sleeve of the first wobble drive and the drive sleeve of the second wobble drive are connected to one another in a rotationally fixed manner.
  • the drive sleeves are preferably made in one piece.
  • the rotationally fixed connection defines a relative rotational position of the first raceway to the additional, second raceway. By defining the relative rotational position, the phase shift ⁇ between the movements of the first swash plate and the second swash plate is set.
  • the drive sleeve of the first wobble drive and the drive sleeve of the second wobble drive are detachably connected to one another.
  • drive sleeves are detachably connected to one another in a rotationally fixed manner.
  • an adjusting device is provided with which the relative rotational position of the first raceway to the second raceway can be fixed in an adjustable manner. By means of the adjusting device, it is thus possible to carry out the phase shift ⁇ between the movements of the first swash plate and the second swash plate in an adjustable manner.
  • the second stroke generating device is designed as a cam drive.
  • the cam drive is designed as a cylinder cam drive with a trajectory that is arranged on a lateral surface and deflects the at least one additional lifting element.
  • the counter-oscillator is deflected along the trajectory by the additional lifting element.
  • the cam drive is designed as a front cam drive or as a cam drive which has a surface profile.
  • Pressure element acts on the counter-oscillator so that the counter-oscillator can be pressed against the surface profile and can be deflected following the surface profile.
  • the second stroke generating device is designed as a push rod drive, the counter-oscillator being operatively connected to the intermediate shaft via a push rod.
  • the second stroke generating device is designed as a crank drive, the counter-oscillator being operatively connected to a crank disk via a connecting rod.
  • the crank disk is preferably driven by the intermediate shaft.
  • the second stroke generating device is designed as a link drive, the counter-oscillator being provided with a link.
  • the second stroke generating device is designed as a rocker arm drive, an eccentric, in particular arranged on the intermediate shaft, driving a rocker arm.
  • a preferred further development of the handheld power tool according to the invention has a movement sequence of the second lifting element with a time behavior that deviates from a sinusoidal shape.
  • the sequence of movements of the counter-oscillator can advantageously be adapted to a time behavior of the effective forces that excite oscillation.
  • a deflection of the first lifting element has a first frequency.
  • a deflection of the second lifting element of the second stroke generating device has a second frequency, which in particular differs from the first frequency.
  • the second frequency is in particular approximately half as large as the first frequency.
  • Fig. 1a shows a side view of a partial area of a hammer drill 1 as an example of a handheld power tool according to the invention.
  • the hammer drill 1 comprises a machine housing 2 (not shown here) which surrounds a drive motor (not shown here) and a gear area 3.
  • the gear area 3 is received by an intermediate flange 21, via which it is connected to a sub-area of the machine housing 2 that carries the drive motor.
  • the gear area 3 has a gear device 4, by means of which a hammer tube 5 can be coupled to the drive motor, see above that this can be driven to rotate.
  • the hammer tube 5 is arranged in the gear area 3 and is rotatably mounted in the intermediate flange 21.
  • the hammer tube 5 extends away from the intermediate flange 21 along a machine axis 6.
  • the gear device 4 transmits a torque provided by the drive motor to the hammer tube 5 via the gear device 4.
  • the transmission device 4 one can also speak of a rotary drive of the hammer tube 5 here.
  • the gear device 4 To drive the hammer tube 5 in rotation, the gear device 4 has an intermediate shaft 7 which is arranged parallel to the machine axis 6 in the gear area 3 of the machine housing 2 below the hammer tube 5.
  • the intermediate shaft 6 is rotationally decoupled from the machine housing 2 by a plurality of bearing devices 8.
  • an output gear 10 designed as an output spur gear 10a is arranged and connected to the intermediate shaft 7 in a rotationally fixed manner.
  • a drive spur gear 11, which meshes with the output spur gear 10a, is arranged on the hammer tube 5.
  • the drive spur gear 11 is operatively connected to the hammer tube 5 via an overload safety clutch 12. If the torque applied to the drive wheel 11 is below a limit torque of the overload safety clutch 12, the drive wheel 11 is non-rotatably connected to the hammer tube 5. As a result, the torque applied to the drive wheel 11 is transmitted to the hammer tube 5.
  • a tool holder 5a is provided, in which insert tools (not shown here) can be inserted.
  • the tool holder 5a is non-rotatably connected to the hammer tube 5. The tool holder 5a thus transmits the torque acting on the hammer tube to the insert tool.
  • the tool holder 5a moreover provides a limited axial mobility of the insert tool along a tool or impact axis defined by a longitudinal extension of the insert tool.
  • the tool or impact axis and the machine axis 6 are aligned coaxially to one another, so that the term impact axis 6 is used synonymously with the machine axis 6 in the following.
  • an air cushion hammer mechanism In addition to the rotary drive of the hammer tube, an air cushion hammer mechanism, not shown in detail here, can be driven by means of the gear device 4, as it is, for example, from FIG DE 198 51 888 C1 or the DE 10 2007 061 716 A1 is known.
  • a piston which is arranged axially displaceably in the hammer tube 5 is set in an oscillating axial movement, so that pressure modulations in one between the an inside of the hammer tube 5 facing end face of the piston and an end face facing this end face of an air spring also provided in the hammer tube 5 so as to be axially displaceable.
  • the striking element is accelerated along the striking axis 6.
  • the impact element is accelerated until it hits an end area of the insert tool.
  • the impulse from the striking element is transmitted to the tool as a striking pulse.
  • the transmission device 4 according to the invention from Fig. 1a comprises a first stroke generating device 13 designed as a wobble drive 13a.
  • the wobble drive 13a is arranged with a first drive sleeve 14 in an area 15 of the intermediate shaft 7 facing the drive motor.
  • the drive sleeve is preferably connected to the intermediate shaft 6 in a rotationally fixed manner.
  • a first raceway 16, not shown here, is provided on the drive sleeve 14.
  • the raceway 16 is circular and tilted in a striking plane containing the striking axis 6 and the intermediate shaft 7 by an angle W1 that is greater than zero and less than 180 ° and particularly preferably between 45 ° and 135 °.
  • the wobble bearing 17 comprises at least one, but preferably two or more bearing elements 18, which are preferably designed as balls.
  • the raceway 16 and the wobble bearing 17 in are best Figure 1c to recognize.
  • a wobble finger 20, not shown here, is arranged on the wobble plate 19, preferably integrally formed.
  • the wobble finger 20 extends away from the intermediate shaft 7 in the direction of the impact axis 6. Its front end, not shown here, is received in a pivot bearing which is provided at the rear end of the piston of the air cushion hammer mechanism.
  • a rotary movement of the intermediate shaft 6 causes the drive sleeve 14 with the raceway 16 provided thereon to rotate.
  • the swash bearing 17 is positively guided with its bearing elements 18 on the raceway 16, so that the swash plate 19 is decoupled from the intermediate shaft 7 in terms of rotation, but is caused to wobble by the forced guidance.
  • wobble finger 20 performs an oscillating axial movement in the direction of impact axis 6.
  • the wobble finger 20 acts as the first lifting element 20a of the first stroke generating device 13.
  • the oscillating axial movement of the wobble finger 20 is transmitted to the piston of the air cushion hammer mechanism via the rotary bearing.
  • the transmission device 4 according to the invention from Fig. 1a furthermore has a second stroke generating device 23, which in the present exemplary embodiment is designed as a second wobble drive 23a.
  • the second wobble drive 23a is arranged on an end face of the first wobble drive 13a on the intermediate shaft 7 facing away from the drive motor.
  • the second wobble drive 23a is similar to the first wobble drive 13a already described.
  • the second wobble drive 23a has a second drive sleeve 24 with a second raceway 26, the second drive sleeve 24 preferably being non-rotatably coupled to the intermediate shaft 7.
  • a second swash bearing 27 is provided with bearing elements 28 which are guided along the second track 26 and are encompassed by a second swash plate 29.
  • the swash plate 29 carries a second wobble finger 30.
  • the second track 26 is tilted in the plane of the stroke containing the stroke axis 6 and the intermediate shaft 7 by an angle W2 which is greater than zero and less than 180 ° and in particular preferably between 45 ° and 135 °.
  • the second wobble finger 30 is rotated with respect to the first wobble finger 20 by an angle of rotation WV in the circumferential direction of the intermediate shaft 7 from the plane of impact, as shown in FIG Figure 1b is shown.
  • the second wobble drive 23a is adapted to structural conditions in the machine housing 2.
  • the angle of rotation WV prevents the first wobble finger 20 from colliding with the second wobble finger 30 when the transmission device 4 is in operation, even with large strokes of the wobble finger 20 .30 avoided.
  • the end of the wobble finger pointing away from the second wobble plate 29 is received in a counter-oscillator 31.
  • the counter-oscillator 31 can have a receiving rotary bearing 32 for the low-friction reception of the wobble finger 30, which is shown in FIG Figure 1c is shown.
  • the counter-oscillator 31 is designed essentially as a counter-oscillating mass 33.
  • the counter-oscillating mass 33 is designed as a cylindrical mass body.
  • the counter-oscillator 31 is arranged to be axially displaceable laterally on a sleeve-shaped section 22 of the intermediate flange 21.
  • the sleeve-shaped section 22 is provided with a receiving groove 36 in which the cylindrical counter-oscillating mass 33 is received.
  • the counter-oscillator 31 is encompassed by a guide element 34, as shown in FIG Figure 1b is shown.
  • the guide element 34 is detachably fastened to the sleeve-shaped section 22 by means of screw connections.
  • the person skilled in the art is also familiar with other fastening options, such as, for example, clamping, locking, riveting, soldering or welding connections, which can be advantageous here.
  • the guide element can also be arranged in the surrounding machine housing 2.
  • the counter-oscillator 31 is guided by the guide element 34 and receiving groove 25 on a linear path, in particular a straight section parallel to the impact axis 6.
  • a linear path in particular a straight section parallel to the impact axis 6.
  • the person skilled in the art will not find it difficult to select the most suitable web shape for the respective application.
  • the first drive sleeve 14 and the second drive sleeve 24 are non-rotatably connected to one another in the present exemplary embodiment.
  • a relative rotational position of the raceways to one another is set between the first raceway 16 and the second raceway 26 by selecting an orientation angle WO in the circumferential direction of the intermediate shaft 7.
  • the orientation angle WO is equal to the angle of rotation WV of the second wobble finger 20. This is, inter alia, in FIG Figure 1b to recognize.
  • a phase shift ⁇ between the oscillating axial movements of the two wobble fingers 20, 30 results from the relative rotational position and the angles W1 and W2 of the first and second wobble fingers 20, 30.
  • connection techniques can be used to produce a non-rotatable connection.
  • the first drive sleeve 14 can be provided at its end facing the second drive sleeve 24 with latching elements such as, for example, a face toothing, a toothing on the outer surface or similar formations.
  • the second drive sleeve 24, on the other hand, is provided with corresponding receiving elements, in which, in particular during the assembly of the transmission device 4, the latching elements engage in order to produce a form-fitting connection.
  • a non-positive connection can be brought about, for example, by a press fit between the first drive sleeve 14 and the second drive sleeve 24.
  • more complex connections which for example comprise an additional connecting member, for example a connecting sleeve, can also be used under certain circumstances.
  • connection techniques such as, for example, gluing, soldering or welding, which can be used advantageously under certain circumstances.
  • the first drive sleeve and the second drive sleeve can also be produced in one piece.
  • Sintering technology or metal injection molding (MIM) are particularly suitable for this.
  • non-rotatable connection is detachable, in particular axially detachable. Possible designs are in the Figure 10a and 10b shown and described, to which reference is made at this point.
  • inertial forces are referred to below as inertial forces.
  • a change in the state of motion of the piston sometimes generates very high inertia forces.
  • the inertial forces depend in particular on the mass of the piston and thus on its geometry and the material used.
  • the inertial forces act directly on the piston, the striking element and the hammer barrel and stimulate them to vibrate.
  • the accelerations at the reversal points of the axial movement of the piston are relatively high, so that the inertial forces show a pulse-like behavior over time and particularly strong vibration excitations occur.
  • the time response is synchronous with the movement of the piston.
  • the counter-oscillator 31 is preferably deflected in phase opposition to the oscillating axial movement of the piston.
  • a phase shift ⁇ of 180 ° advantageously prevails between the oscillating axial movement of the piston and the oscillating axial movement of the counter-oscillator 31.
  • the stroke of the oscillating axial movement of the counter-oscillator 31 represents a parameter for coordinating a reduction effect of the counter-oscillator 31 on the respective air-cushion hammer mechanism.
  • inertial forces do not only stimulate vibrations in air cushion impact mechanisms. Rather, the so-called air forces can have a considerable influence on the excitation of vibrations.
  • the air forces play a dominant role in the excitation of vibrations, particularly when the hammer drills increase while the mass of the moving components, such as the piston, is reduced at the same time.
  • due to fluid-mechanical effects the air forces are subject to a phase shift to the oscillating axial movement of the piston, which is typically in the range between 260 ° and 300 °° after a front dead center VT of the oscillating axial movement of the piston.
  • phase shift ⁇ between the oscillating axial movement of the piston and the oscillating axial movement of the counter-oscillator 31 can be made and set in a simple manner.
  • the adjustment of the phase shift ⁇ will take into account a time behavior of the effective forces that stimulate vibrations, which are composed of the inertial forces and the air forces.
  • the phase shift ⁇ will preferably be between 190 ° and 260 °. In a particularly preferred embodiment, the phase shift ⁇ is between 200 ° and 240 °.
  • the parameters counter-oscillating mass, stroke of the counter-oscillating element 31 and the phase shift ⁇ represent optimization parameters which are dependent on the respective air cushion hammer mechanism and which can be determined mathematically and / or experimentally.
  • a preferred further development provides an additional articulation element (not shown here) on the second swash plate 29 of the second swash drive 23a.
  • the additional articulation element is preferably arranged at a circumferential angle WA to the second wobble finger 30 on the wobble plate 29, preferably integrally formed.
  • a second counter-oscillator is preferably driven with this articulation element.
  • FIGS. 3a and 3b show, in a perspective view, a further development of the embodiment of a handheld power tool according to the invention described above as a second embodiment.
  • Fig. 3a shows a counter-oscillator 131 which comprises three counter-oscillating masses 133a, 133b, 133c connected by a bow-shaped connecting element 135.
  • the counter-oscillator 131 is constructed from two predominantly mirror-symmetrical half-elements in order to enable easier assembly. The half-elements are screwed together during assembly.
  • a receiving rotary bearing 132 is provided in counter-oscillating mass 133a, in which the second wobble finger 130 of the second wobble drive 123 is received.
  • the counter-oscillator 131 is arranged around the sleeve-shaped section 122 of the intermediate flange 121 and is supported axially displaceably thereon.
  • the sleeve-shaped section 122 has receiving grooves 136a, 136b, 136c in which the cylindrical counter-oscillating masses 133a, 133b, 133c are received.
  • the counter-oscillator 133a is held and guided by a guide element 134 on the sleeve-shaped section 122.
  • the counter-oscillating masses 133a, 133b, 133c of the second exemplary embodiment are designed in terms of their masses and their positioning such that the counter-oscillating element 131 has a center of gravity M located centrally.
  • This center of gravity M is arranged in such a way that it comes to lie essentially on the impact axis 106.
  • the center of gravity M describes a path of the center of gravity which runs essentially parallel, preferably coaxially, to the impact axis 106.
  • the counter-oscillator 131 can counteract the oscillation-stimulating effective forces particularly effectively, since these effective forces act directly on components of the hammer drill 101, such as the piston of the air cushion hammer, which are predominantly cylinder-symmetrical in a known manner are arranged around the lay axis 6, so that their center of gravity tracks also run parallel, predominantly even coaxially to the lay axis 6.
  • a counter-oscillator 131 In addition to the three-part design of a counter-oscillator 131 described here, the person skilled in the art is familiar with further designs of counter-oscillators which enable a center of gravity path of the counter-oscillator that is predominantly coaxial with the impact axis 6.
  • the shape and number of the counter-oscillating masses 133a, 133b, 133c connected to one another can differ from the embodiment shown here.
  • An embodiment of the counter-oscillator 131 as a sleeve-shaped component can also represent an advantageous modification.
  • modifications of the counter-oscillator 131 shown here can result from different subdivisions into different half-elements or other sub-elements and / or their mutual connection.
  • Figure 4a shows a perspective schematic view of a third embodiment of a transmission device 204 according to the invention.
  • the reference numerals of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 204 is shown in FIG Figure 4a only the first and second stroke generating devices 213, 223 arranged on the region 215 of the intermediate shaft 207 facing the drive motor are shown, with only one intermediate shaft axis 207a being shown instead of the intermediate shaft 207.
  • the stroke generating devices are designed as a first wobble drive 213a and as a second wobble drive 223a.
  • the first wobble drive 213a is constructed in a manner known from the previous exemplary embodiments, so that its description is dispensed with.
  • the third exemplary embodiment differs from the preceding exemplary embodiments in that the second wobble drive 223a is modified.
  • Two output fingers 237a, 237b are provided on the second swash plate 229. These output fingers 237a, 237b are connected to the swash plate 229 in the laterally circumferential direction, preferably molded onto it.
  • the output fingers 237a, 237b extend arcuately around a piston 238 of the air cushion hammer which is connected to the first wobble finger 220.
  • output fingers 237a, 237b are designed mirror-symmetrically to the lay plane, which contains the lay axis 206 and the intermediate shaft axis 207a. However, it can be advantageous if this symmetry is deviated from.
  • the output fingers 237a, 237b are connected to a finger head 240 carrying an output element 239, preferably made in one piece therewith.
  • the output element 239 is with the counter-oscillator 231 in operative connection.
  • the output element 239 similar to the already known second wobble finger 30, 130, can be received in a receiving rotary bearing 232 provided on the counter-oscillating mass 233.
  • the oscillating axial movement of the counter-oscillator 231 lies in the plane of impact. This arrangement means that a stroke of the second wobble drive 223 does not need to be rotated with respect to the flapping plane.
  • the phase shift ⁇ between the oscillating axial movement of the piston 238 triggered by the first wobble finger 220 and the oscillating axial movement of the counter-oscillator 231 of the third embodiment is determined solely by an angular difference between the angles W1 and W2.
  • the third exemplary embodiment corresponds to the first exemplary embodiment, so that reference is made to the description thereof.
  • Figure 4b is a modified version of the third embodiment from Figure 4a shown as a fourth embodiment.
  • the representation is analogous to the representation in Figure 4a .
  • only a modification is discussed, since the basic structure and the mode of operation correspond to those of the third exemplary embodiment.
  • the second swash plate 229 of the second swash drive 223a has an output finger 237a on only one side.
  • the output finger 237a is arcuate.
  • the finger head 240, which carries the output element 239, is attached to its end facing away from the swash plate 229.
  • the counter-oscillator 231 is arranged in the plane of impact above the piston 238.
  • the fourth exemplary embodiment corresponds to the first exemplary embodiment, so that reference is made to the description thereof.
  • Figure 4c is a combination of the second embodiment Fig. 3a and the third embodiment Figure 4a shown as a fifth embodiment.
  • the representation is analogous to the representation in Figure 4a .
  • only a modification is discussed, since the basic structure and the mode of operation correspond to those of the third exemplary embodiment.
  • the counter-oscillator 231 of the fifth exemplary embodiment is similar in structure to the counter-oscillator 131 known from the second exemplary embodiment
  • Counter-oscillator 231 is provided in the middle counter-oscillator mass 233b, since this is arranged analogously to the counter-oscillator 231 of exemplary embodiments three and four in the striking plane below the finger head 240.
  • the center of gravity M of the counter-oscillator is located centrally between the counter-oscillator masses 233a, 233b, 233c.
  • Figure 4d is a modified version of the third embodiment from Figure 4a shown as a sixth embodiment.
  • the representation is analogous to the representation in Figure 4a .
  • only a modification is discussed, since the basic structure and the mode of operation correspond to those of the third exemplary embodiment.
  • the finger head 240 of the two output fingers 237a, 237b itself is designed as a counter-oscillating mass 233.
  • the finger head 240 thus acts as a counter-oscillator 231. Due to a swiveling movement of the output fingers 237a, 237b triggered by the swash plate 229, the counter-oscillator in the present case performs a swiveling movement in the flapping plane.
  • the counter-oscillator is guided in particular on a circular arc-shaped path.
  • a guide pin 241 can be arranged, in particular molded, on the finger head 240.
  • This guide pin 241 is preferably oriented away from the swash plate 229.
  • a counter-oscillator 231 (not shown here), which includes a link 242, can also be arranged on the guide pin 241.
  • the guide pin 241 protrudes into this link 242 and transmits the oscillating axial movement of the finger head 240 to the counter-oscillator 231 carrying the link 242.
  • An exemplary embodiment of a link 242 is shown in FIG Figure 8b shown.
  • a second stroke generating device 23 according to the invention in the form of a second wobble drive 23a, 123a, 223a can result, among other things, from combinations of the individual features of the above-described exemplary embodiment with one another and with characteristics of wobble drives known to those skilled in the art.
  • Figure 5a shows a schematic side view of a hammer drill 301 with a gear device 304 according to the invention.
  • the reference numerals of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 304 comprises, as the first stroke generating device 313, a wobble drive 313a already known from the above. This is therefore not discussed in more detail at this point.
  • the second stroke generating device 323 for driving a counter-oscillator 331 is designed as a cam drive 323b.
  • the second stroke generating device 323, 323b has a cam cylinder 343, which in the area 309 of the intermediate shaft 307 facing away from the drive motor is arranged on the latter and is preferably connected to it in a rotationally fixed manner.
  • a path curve 344 is provided on an outer jacket surface of the cam cylinder 343.
  • the trajectory has an axial course 345 that varies in the circumferential direction of the cam cylinder 343.
  • the axial course 345 can be given by a circular path tilted by an angle W3 to the intermediate shaft.
  • other, in particular non-linear, path shapes, such as spiral paths, sinusoidal paths and similar path courses may also be advantageous under certain circumstances.
  • the trajectory 344 is let into the outer jacket surface of the cam cylinder 343 in the form of a groove.
  • the cam cylinder is covered or wrapped with a sleeve element that has just been produced and carries a cam profile.
  • the sleeve element can be produced by punching and then wound into a sleeve. Further methods for this purpose are known to the person skilled in the art.
  • the counter-oscillator 331 has a guide element 346, for example a guide ball 346a or a guide pin 346b, which is arranged on the side of the counter-oscillator facing the cam cylinder.
  • the guide element 346 is in a predominantly fixed radial position in relation to the cam cylinder 343.
  • the guide element 346 engages in the path curve 344 and is guided by it.
  • the cam cylinder 343 is driven to rotate by the intermediate shaft 307.
  • the guide element 346 becomes along the axial course 345 of the trajectory 344 deflected, so that one can speak of an oscillating axial movement.
  • the axial movement of the guide element 346 is typically repeated after a full revolution of the cam cylinder 343.
  • trajectories 344 are also possible which deviate from this relationship.
  • the repetition of the axial movement can be an integral multiple or an integral portion of a revolution of the cam cylinder 343. An example to which reference is made at this point is shown in FIGS. 12a to 12c.
  • the counter-oscillator 331 Due to the oscillating axial movement of the guide element 346, the counter-oscillator 331 is set in oscillating axial movements.
  • a desired phase shift ⁇ between the first wobble finger 320 and the guide element 346 as the lifting element 330a of the second stroke generating device 323, 323b can be set by a suitable choice of the angle W3 and / or the axial course 345 of the trajectory 344.
  • the counter-oscillator 331 acts analogously to the previous exemplary embodiments.
  • the axial course 345 of the trajectory 344 can be selected, in this exemplary embodiment of a transmission device 304 according to the invention there is an additional degree of freedom for the optimal adaptation of the oscillating axial movement of the counter-oscillator to the timing of the oscillation-stimulating effective forces, which can advantageously be used for further oscillation reduction.
  • a movement profile of the counter-oscillator 331 that deviates from a sinusoidal shape typical for oscillating movements can be generated.
  • FIG. 5b is a further development of the embodiment from Figure 5a shown as an eighth embodiment.
  • the counter-oscillator 331 is designed as a sleeve-shaped counter-oscillator mass 333.
  • the counter-oscillator 331 is arranged at least partially around the hammer tube 305 and is mounted axially displaceably thereon.
  • the counter-oscillating mass 333 carries a radially protruding guide ring 347 on its circumference.
  • This guide ring 347 can be designed as a separate component, for example as an insert ring, or it can be molded directly onto the counter-oscillating mass 333.
  • it is possible to use a guide element 346, in particular a guide pin 346b, as already shown in FIG Figure 5a is known.
  • a cam cylinder 307 is arranged on the intermediate shaft 307, for the description of which at this point refer to the description of Figure 5a is referred.
  • the guide ring 347 or the guide element 346 engages in the trajectory 344 of the cam cylinder 343 on the side of the counter-oscillator facing the intermediate shaft 307.
  • the counter-oscillator 331 is set in oscillating axial movements by the guide ring 347 or the guide element 346 following the axial course 345 of the trajectory 344.
  • This embodiment therefore compensates for that of the embodiment in its mode of operation Figure 5a . Due to the sleeve-shaped structure of the counter-oscillating mass 333, however, in the present case it has a center of gravity path which runs essentially coaxially to the impact axis 306.
  • Figure 5c shows a modification of the from Figure 5b known embodiment of a transmission device 304 according to the invention as a ninth embodiment.
  • the counter-oscillator 331 is provided with a trajectory 344 arranged on an outer surface of the sleeve-shaped counter-oscillator mass 333, the counter-oscillator mass 333 being arranged axially displaceably on the hammer tube 305.
  • a drive pulley 348 is arranged on the part 309 of the intermediate shaft 307 facing away from the drive motor and can be driven in rotation by the intermediate shaft 307.
  • the drive pulley 348 engages in the trajectory 344 of the counter-oscillating mass 333 and transmits a rotary movement to the counter-oscillating mass 333. If the counter-oscillating mass 333 is set in rotation, it follows the axial course 345 of the trajectory 344, so that it executes an oscillating axial movement in addition to the rotation. In its mode of operation, this version corresponds to that from Figure 5b known embodiment, whereby a center of gravity path of the counter-oscillator 331 running essentially coaxially to the impact axis 306 can also be realized here by the sleeve-shaped construction of the counter-oscillator 331.
  • Fig. 6 shows a schematic side view of a hammer drill 401 with a transmission device 404 according to the invention as a tenth embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 404 comprises, as the first stroke generating device 413, a wobble drive 413a already known from the above. This is therefore not discussed in more detail at this point.
  • the second stroke generating device 423 for driving a counter-oscillator 431 is a front cam drive 423c.
  • the end cam drive 423c has a cam disk 450 carrying a surface profile 449 on an end face which is perpendicular to the intermediate shaft 307 and is oriented away from the drive motor. One can therefore also from one Talk to cam drive 423c.
  • the surface profile 449 has in particular an axial profile 451 that varies in the circumferential direction of the cam disk 450.
  • the counter-oscillator 431 is arranged facing away from the drive motor axially in front of the intermediate shaft 307, in particular in front of the cam disk 450 in the machine housing 402.
  • the counter-oscillator 431 has a pressure element 452 by means of which the counter-oscillating mass 433 of the counter-oscillator 431 is axially pretensioned in the direction of the cam disk 450.
  • the pressure element 452 is designed as a pretensioned helical spring 452a.
  • the helical spring 452a is supported on a contact element 454 fixed to the housing in the machine housing 302.
  • pressure elements 452 such as elastomers or other spring elements are known to those skilled in the art, which can be used advantageously in the context of the invention. When assembling the pressure element 452, contact and / or assembly elements that differ from the shape shown here can also be advantageous.
  • the counter-oscillating mass 433 is pressed against the surface profile 449 by this prestressing.
  • the counter-oscillating mass 433 has a contact element 453 on its side facing the cam disk, which contact element 453 is pressed against the surface profile in an outer radius region of the cam disk 450. If the cam disk 450 is driven to rotate by the intermediate shaft 407, the counter-oscillating mass 433 is axially deflected via the contact element 453 as a lifting element 430a of the second stroke generating device 423, 423c. Because of the axial profile 451 that recurs with one revolution of the cam disk 450, the counter-oscillator 431 executes an oscillating axial movement.
  • the course of the axial movement over time can be influenced in a targeted manner via the cam profile 449, in particular the axial course 451.
  • motion profiles that deviate from a sinusoidal shape that is typical for oscillating motions can be generated.
  • a multiple deflection per revolution of the cam disk 450 is also possible, depending on the cam profile 450.
  • Fig. 7 shows a schematic side view of a hammer drill 501 with a gear device 504 according to the invention as an eleventh embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 504 comprises, as the first stroke generating device 513, a wobble drive 513a already known from the above. This is therefore not discussed in more detail at this point.
  • the second stroke generating device 523 for driving a counter-oscillator 531 is designed as a push rod drive 523d.
  • a drive pulley 556 is arranged on the part 509 of the intermediate shaft 507 facing away from the drive motor and can be driven in rotation by the intermediate shaft 507.
  • a swivel joint 557 is provided on an end face of the drive pulley 556 in a radially outer region.
  • One end of a push rod 558 is operatively connected to the drive pulley 556 via this swivel joint 557.
  • a second swivel joint 559 is provided on the push rod 558, which connects the push rod 558 to the counter-oscillating mass 533 of the counter-oscillating 531.
  • the counter-oscillator 531 in particular the second rotary joint 559, is placed at a radial distance from the intermediate shaft axis 507a.
  • the counter-oscillating mass 533 is preferably guided axially displaceably along a path. In a particularly preferred manner, this path is straight parallel to the lay axis 506.
  • the drive pulley 556 is driven to rotate by the intermediate shaft 507, as a result of which the push rod 558 follows the rotary movement via the first swivel joint 557. Due to the axial guides of the counter-oscillating mass 533, the movement of the push rod 558 at the second rotary joint 559 is transmitted to the counter-oscillating mass 533 in the form of an oscillating axial movement.
  • the counter-oscillator 531 therefore behaves analogously to the already known designs.
  • a phase shift ⁇ is set in this exemplary embodiment by a circumferential angle WU at which the first rotary joint 557 is arranged on the drive disk 556, as well as via the relative position of the second rotary joint 559 to the first rotary joint 557 the piston is at its front dead center VT, as shown in FIG Fig. 7 is shown.
  • Modifications of this embodiment of a transmission device according to the invention result, among other things, in the design of the swivel joints 557, 559 and / or the push rod 558. Furthermore, the design of the counter-oscillating mass 533 can be varied. In particular, advantageous combinations can result from the exemplary embodiments that are easily recognized by those skilled in the art.
  • Figure 8a shows a schematic side view of a hammer drill 601 with a transmission device 604 according to the invention as a twelfth exemplary embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 604 comprises, as the first stroke generating device 613, a wobble drive 613a already known from the above. This is therefore not discussed in more detail at this point.
  • the second stroke generating device 623 for driving a counter-oscillator 631 is designed as a crank drive 623e.
  • a first bevel gear 660 is arranged on the part 609 of the intermediate shaft 607 facing away from the drive motor and can be driven in rotation by the intermediate shaft 607.
  • the first bevel gear 660 meshes with a second bevel gear 661, which is arranged on an intermediate gear shaft 662 perpendicular to the intermediate shaft 607.
  • an eccentric pin 663 is arranged, preferably integrally formed, in a radially outer one.
  • the second bevel gear 661 thus acts as a crank disk 661a.
  • the eccentric pin 663 is arranged on an eccentric wheel additionally connected to the intermediate wheel shaft 662 and preferably connected to it in a rotationally fixed manner.
  • Such solutions are sufficiently known to the person skilled in the art, so that their description can be dispensed with.
  • the counter-oscillator 631 is arranged axially in front of the first bevel gear 660 in the machine housing 602.
  • the movably mounted counter-oscillating mass 633 is provided in an axial guide, preferably parallel to the impact axis 606. At its end facing the first bevel gear 660, the counter-oscillating mass is operatively connected to the eccentric pin 663 via a connecting rod 664.
  • the first bevel gear 660 is driven to rotate by the intermediate shaft 607.
  • the eccentric pin 663 is set in motion via the second bevel gear 661, as a result of which the counter-oscillating mass 633 finally performs an oscillating axial movement.
  • the counter-oscillator 631 therefore behaves analogously to that of Fig. 1a known execution.
  • a phase shift ⁇ is set by means of a circumferential angle WE of the eccentric pin 663 on the second bevel gear 661.
  • Figure 8b shows a modification of the embodiment according to Figure 8a as a thirteenth embodiment.
  • this embodiment there is a counter oscillating mass 633
  • Link 642 is provided, in which the eccentric pin 663 engages directly.
  • the counter-oscillating mass 633 is moved by the oscillating eccentric pin 663 that moves back and forth in the link 642.
  • the movement path of the counter-oscillating mass 633 depends on the shape of the link, in particular its axial course 665.
  • a phase shift ⁇ is set by means of a circumferential angle WE of the eccentric pin 663 on the second bevel gear 661 and by designing the link 642, in particular axial profile 665.
  • Fig. 9 shows a schematic side view of a hammer drill 701 with a transmission device 704 according to the invention as a fourteenth embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the transmission device 704 comprises, as the first stroke generating device 713, a wobble drive 713a already known from the above. This is therefore not discussed in more detail at this point.
  • the second stroke generating device 723 for driving a counter-oscillator 731 is designed as a rocker arm drive 723f.
  • an eccentric cam wheel 766 is arranged on the part 709 of the intermediate shaft 707 facing away from the drive motor and can be driven in rotation by this.
  • the first lever arm 767 of a rocker arm 768 is arranged.
  • One end of the first lever arm 767 is rotatably mounted in a pivot bearing 769.
  • the pivot bearing 769 is also supported in a fixed manner to the housing below the intermediate shaft 707 in the machine housing.
  • a cam profile 770 of the eccentric cam wheel 766 acts from a second end of the first lever arm 767, so that the first lever arm 767 performs a pitching movement about the pivot bearing 769.
  • a second lever arm 771 of the rocker arm 768 is also arranged on the pivot bearing 769. This is preferably rigidly connected to the first lever arm 767, so that the pitching movement is transmitted to the second lever arm 771.
  • the counter-oscillator 731 is arranged at an end of the second lever arm 771 opposite the rotary joint 769.
  • the counter-oscillating mass 733 is operatively connected to the second lever arm 771 in such a way that the pitching movement is converted into a movement of the counter-oscillating mass.
  • the counter-oscillating mass is designed in the form of a sleeve and is mounted axially displaceably on the hammer tube 705. Due to the sleeve-shaped design of the counter oscillating mass 733, a preferred center of gravity path that is coaxial with the impact axis 706 can be achieved.
  • the eccentric cam wheel 766 is driven to rotate by the intermediate shaft 707, so that the pitching movement of the first lever arm 767 with the cam profile 770 occurs repeatedly. Due to the operative connection between the second lever arm 771 and the counter-oscillating mass 733, the latter is driven to an oscillating axial movement. Due to the recurring cam profile 770 with one revolution of the eccentric cam wheel 766, the counter-oscillator 731 executes an oscillating axial movement. The course of the axial movement over time can be influenced in a targeted manner via the cam profile 771. In particular, motion profiles that deviate from a sinusoidal shape that is typical for oscillating motions can be generated.
  • a multiple deflection per revolution of the eccentric cam wheel 766 is also possible, depending on the cam profile 770.
  • a phase shift ⁇ is set by setting the cam profile 771, in particular with respect to a rotational position relative to the first raceway 716 of the first wobble drive 713a.
  • FIG. 11 shows a schematic side view of a further development of the embodiment from FIG Fig. 1a as the fifteenth embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the stroke generating devices 813, 823 designed as first and second wobble drives 813a, 823a are shown in a further development.
  • first drive sleeve 814 is connected to the intermediate shaft 807 in a rotationally fixed manner.
  • the second drive sleeve 824 is axially displaceable and loosely rotatable on the intermediate shaft 807.
  • a clutch device 873 designed as an engagement clutch 872 is provided between the first drive sleeve 814 and the second drive sleeve.
  • the clutch device 872, 873 is brought into an activated or engaged state by an axial displacement along a displacement path V, so that the second drive sleeve 824 is now connected to the first drive sleeve 814 in a rotationally fixed manner.
  • At least one, but preferably two or more coupling elements 874 are provided on the side of the first drive sleeve facing the second drive sleeve 824.
  • the mating coupling elements 875 are brought into engagement with the coupling elements 874 by axially displacing the second drive sleeve 824.
  • coupling elements 874 and the mating coupling elements 875 that correspond to them.
  • toothing on the face or on the circumference and counter-toothing can be used.
  • Coupling devices 873 with coupling elements such as balls and ball seats are also conceivable, to name just two known designs.
  • the drive of the counter-oscillator 831 can be made switchable via the second wobble drive 823a.
  • the drive of the counter-oscillator 831 is deactivated when the hammer drill 801 is idling. Only when a work activity is started, in particular with a percussion drive of the tool insert, is the drive of the counter-oscillator 831 put into operation manually or automatically.
  • FIG. 11 shows a schematic side view of a further development of the embodiment from FIG Figure 10a as a sixteenth embodiment.
  • the embodiment of an engagement clutch 872 shown here has in particular already ended DE 10 2004 007 046 A1 known, the description of which is explicitly referred to at this point.
  • an axially displaceable displacement sleeve 876 is arranged, which carries a conically tapering displacement wedge 877 on its side facing the second drive sleeve 824.
  • the second drive sleeve 824 is arranged freely rotatable on the intermediate shaft 807.
  • the intermediate shaft 807 has a through-hole 878 which, in both directions along the intermediate shaft 807, has a conically opening receiving diameter with different cone angles in each case.
  • the side of the through hole facing the displacement sleeve 876 has a cone angle corresponding to the displacement wedge 877.
  • the displacement sleeve 876 When the hammer drill 801 is idle, the displacement sleeve 876 is held in a disengaged position by means of a restoring element 879, which is designed here as a spring element 880.
  • the idle state is defined in such a way that in this state the insert tool accommodated in the tool holder 805a is not pressed against a workpiece. Due to the positioning in the disengaged state, the displacement wedge 877 is not in engagement with the conical receiving diameter corresponding to it. As a result, the second drive sleeve 724 is not rotatably connected to the intermediate shaft.
  • the raceway 826 provided on the second drive sleeve 824 is in a resting state tilted 90 ° to the intermediate shaft 807, so that the counter-oscillator 731 does not experience any deflection for this reason either. If the insert tool is now pressed against a workpiece, the displacement sleeve 876 is displaced axially in the direction of the second drive sleeve 824 and the displacement wedge 877 comes into engagement with the corresponding receiving diameter. As a result, on the one hand, a rotary connection is established between the second drive sleeve 824 and the intermediate shaft 807.
  • the angle W2 of the raceway 826 is inclined more towards the intermediate shaft 807, as a result of which a stroke of the second wobble finger 830 increases.
  • the cone angle of the other receiving diameter limits the maximum possible angle W2max.
  • FIG. 11 shows a schematic side view of a further development of the embodiment from FIG Figure 5a as the seventeenth embodiment.
  • the reference symbols of the same or identically acting features are increased by 100 in the illustration.
  • the second stroke generating device 923, 923b has a cam cylinder 943 which is arranged on the intermediate shaft 907 in the area 909 of the intermediate shaft 907 facing away from the drive motor and is preferably connected to it in a rotationally fixed manner.
  • a trajectory 944 is provided on an outer jacket surface of the cam cylinder 943.
  • the trajectory 944 is designed as an opposing, intersecting spiral trajectory 981.
  • the spiral path 981 has two revolutions in each direction.
  • the guide element 946 provided on the counter-oscillating mass 933 is designed here as a rail glider 982, which is best shown in FIG Figure 11b can be seen.
  • the rail slider 982 has at least two guide elements 983, which are preferably designed as balls.
  • the guide elements 983 are freely rotatably arranged on a carrier element 984 at a distance from one another that extends in the circumferential direction of the cam cylinder 943.
  • the cam cylinder 943 rotates at the same speed as the intermediate shaft 907.
  • the counter-oscillator 931 is axially deflected via the rail slider 982 at a reduced speed.
  • the oscillating axial movement of the second lifting element 30a driving the counter-oscillator takes place at a second, here lower frequency F2 compared to a first frequency F1 of the oscillating axial movement of the first wobble finger 920.
  • Figure 11c shows a schematic stroke-time diagram for the deflections of the piston and counter-oscillator, as it corresponds to this embodiment.
  • an adjusting device acting on the raceway 26 of the second drive sleeve 24 is provided, which goes beyond the stroke setting known from the sixteenth embodiment for the lifting element 30a of the second stroke generating device 23. It can thus be advantageous with the adjustment device to enable the rotational position of the track of the second drive sleeve 24 and thus the phase shift ⁇ to the oscillating movement of the lifting element 20a of the first stroke generating device 13.
  • the displacement wedge could be designed asymmetrically and its rotational position relative to the machine housing 2, in particular the lay plane, could be changed either manually or by an actuator. To this end, the person skilled in the art is familiar with other ways of realizing such an adjusting device.
  • such an adjusting device can also be used advantageously in second stroke generating devices 23, which are designed as a curve, front curve, push rod, crank or rocker arm drive.
  • the rotary position of the cam cylinder (343), the cam disk (450), the drive disk (556), the eccentric pin (663) or the eccentric cam wheel (766) can be varied by means of the adjustment device.
  • a bearing device 8 is provided between the first stroke generating device 13 and the second stroke generating device 23.
  • the bearing device 8 is fixed to the housing in the machine housing 2. This bearing device 8 rotates the intermediate shaft 7 in the machine housing 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
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  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Percussion Or Vibration Massage (AREA)

Claims (23)

  1. Machine-outil portative pour des outils à queue à entraînement principalement frappant, notamment des marteaux-perforateurs et/ou burineurs, comprenant un axe de frappe (6, 106, 206, 306, 406, 506, 606, 706, 806, 906) et un arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) parallèle à cet axe de frappe (6, 106, 206, 306, 406, 506, 606, 706, 806, 906), comprenant un premier dispositif générateur d'excursion (13, 113, 213, 313, 413, 513, 613, 713, 813, 913) pour un entraînement frappant, disposé au niveau de ou sur l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) et pouvant être entraîné par celui-ci, présentant un élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a) et comprenant au moins un deuxième dispositif générateur d'excursion supplémentaire (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) présentant un deuxième élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a), pour l'entraînement d'un contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931), un déphasage Δ différent de zéro étant prévu entre un mouvement du premier élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a) et un mouvement de l'au moins un deuxième élément d'excursion (30a, 130a, 230a, 330a, 430a, 530a, 630a, 730a, 830a, 930a), caractérisée en ce que ce déphasage Δ est également différent de 180°.
  2. Machine-outil portative selon la revendication 1, caractérisée en ce que l'au moins un deuxième dispositif générateur d'excursion supplémentaire (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) peut être entraîné par l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907).
  3. Machine-outil portative selon la revendication 1 ou 2, caractérisée en ce que le premier dispositif générateur d'excursion (13, 113, 213, 313, 413, 513, 613, 713, 813, 913) est disposé au niveau de ou sur une région de l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) tournée vers un moteur d'entraînement et l'au moins un deuxième dispositif générateur d'excursion supplémentaire (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est disposé au niveau de ou sur une région de l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) opposée au moteur d'entraînement.
  4. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le déphasage Δ est différent de 90°.
  5. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) présente au moins une masse de contre-oscillateur (33, 133, 233, 333, 433, 533, 633, 733, 833, 933) qui est guidée le long d'une trajectoire de déplacement linéaire ou non linéaire, notamment le long d'une droite ou d'un arc de cercle.
  6. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) possède une trajectoire de centre de gravité qui se trouve à proximité de l'axe de frappe (6, 106, 206, 306, 406, 506, 606, 706, 806, 906), notamment parallèle à l'axe de frappe (6, 106, 206, 306, 406, 506, 606, 706, 806, 906), de préférence orientée de manière coaxiale par rapport à celui-ci.
  7. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) présente un dispositif d'accouplement (873) avec lequel le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) peut être accouplé de manière solidaire en rotation au premier dispositif générateur d'excursion (13, 113, 213, 313, 413, 513, 613, 713, 813, 913).
  8. Machine-outil portative selon la revendication 7, caractérisée en ce que le dispositif d'accouplement (873) est réalisé sous forme d'accouplement à enclenchement (872), avec lequel il est notamment prévu une course de translation axiale entre un état enclenché et un état ouvert.
  9. Machine-outil portative selon la revendication 8, caractérisée en ce qu'une excursion de l'élément d'excursion du deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) varie linéairement avec la course de translation.
  10. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) comprend un élément de déviation supplémentaire par le biais duquel un deuxième contre-oscillateur peut notamment être entraîné.
  11. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le premier dispositif générateur d'excursion (13, 113, 213, 313, 413, 513, 613, 713, 813, 913) est réalisé sous la forme d'un premier dispositif d'entraînement en nutation (13a, 113a, 213a, 313a, 413a, 513a, 613a, 713a, 813a, 919a) comprenant une douille d'entraînement (14, 114, 214, 314, 414, 514, 614, 714, 814, 914) supportant au moins une première trajectoire de roulement (16, 116, 216, 316, 416, 516, 616, 716, 816, 916), un palier de nutation (17, 117, 217, 317, 417, 517, 617, 717, 817, 917) et un plateau oscillant (19, 119, 219, 319, 419, 519, 619, 719, 819, 919), un tenon oscillant (20, 120, 220, 320, 420, 520, 620, 720, 820, 920) étant disposé en tant qu'élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a) sur le plateau oscillant (19, 119, 219, 319, 419, 519, 619, 719, 819, 919).
  12. Machine-outil portative selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est réalisé sous la forme d'un deuxième entraînement en nutation (23a, 123a, 223a, 823a) qui comprend au moins une deuxième douille d'entraînement (24, 124, 224, 824) portant une deuxième trajectoire de roulement (26, 126, 226, 826), un deuxième palier de nutation (27, 127, 227, 827) et un deuxième plateau oscillant (29, 129, 229, 829) avec un tenon oscillant (30, 130, 230, 830) disposé sur celui-ci.
  13. Machine-outil portative selon la revendication 12, caractérisée en ce que la douille d'entraînement (14, 114, 214, 314, 414, 514, 614, 714, 814, 914) du premier entraînement en nutation (13a, 113a, 213a, 313a, 413a, 513a, 613a, 713a, 813a, 919a) ainsi que la douille d'entraînement (24, 124, 224, 824) du deuxième entraînement en nutation (23a, 123a, 223a, 823a) sont connectées de manière solidaire en rotation l'une à l'autre, en particulier sont réalisées d'une seule pièce de telle sorte qu'une position de rotation relative de la première trajectoire de roulement (16, 116, 216, 316, 416, 516, 616, 716, 816, 916) par rapport à la trajectoire de roulement supplémentaire (26, 126, 226, 826) soit établie.
  14. Machine-outil portative selon la revendication 12, caractérisée en ce que la douille d'entraînement (14, 114, 214, 314, 414, 514, 614, 714, 814, 914) du premier entraînement en nutation (13a, 113a, 213a, 313a, 413a, 513a, 613a, 713a, 813a, 919a) ainsi que la douille d'entraînement (24, 124, 224, 824) du deuxième entraînement en nutation (23a, 123a, 223a, 823a) sont connectées de manière desserrable l'une à l'autre, en particulier sont connectées l'une à l'autre de manière solidaire en rotation et desserrable, un dispositif de réglage étant notamment prévu, avec lequel la position de rotation relative de la première trajectoire de roulement (16, 116, 216, 316, 416, 516, 616, 716, 816, 916) par rapport à la deuxième trajectoire de roulement (26, 126, 226, 826) peut être définie de manière réglable.
  15. Machine-outil portative selon l'une quelconque des revendications 1 à 11, en particulier selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est réalisé sous la forme d'un entraînement à cames (323b), notamment sous la forme d'un entraînement à cames cylindriques comprenant une portion de trajectoire (344) disposée sur une surface d'enveloppe et déviant l'au moins un élément d'excursion supplémentaire, le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) étant dévié par l'au moins un deuxième élément d'excursion (30a, 130a, 230a, 330a, 430a, 530a, 630a, 730a, 830a, 930a) le long de la portion de trajectoire (344).
  16. Machine-outil portative selon la revendication 15, caractérisée en ce que l'entraînement à cames (423c) est réalisé sous la forme d'un entraînement à cames frontales ou d'un entraînement à ergot, lequel possède un profil de surface (449), un élément presseur (452) agissant sur le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) de telle sorte que le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) puisse être poussé contre le profil de surface (349) et puisse être dévié en suivant le profil de surface (449).
  17. Machine-outil portative selon l'une quelconque des revendications 1 à 11, notamment selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est réalisé sous la forme d'un entraînement à tige-poussoir (523d), le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) étant en liaison fonctionnelle avec l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) par le biais d'une tige-poussoir (558).
  18. Machine-outil portative selon l'une quelconque des revendications 1 à 11, notamment selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est réalisé sous la forme d'un entraînement à manivelle (623e), le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) étant en liaison fonctionnelle avec un plateau de manivelle (661, 661a) par le biais d'une bielle (664).
  19. Machine-outil portative selon l'une quelconque des revendications 1 à 11, notamment selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) est réalisé sous la forme d'un entraînement à coulisse (623e), le contre-oscillateur (31, 131, 231, 331, 431, 531, 631, 731, 831, 931) étant pourvu d'une coulisse (642).
  20. Machine-outil portative selon l'une quelconque des revendications 1 à 11, notamment selon la revendication 11, caractérisée en ce que le deuxième dispositif générateur d'excursion (23, 123, 223, 323, 423, 523, 623, 723, 823) est réalisé sous la forme d'un entraînement à levier basculant (723f), une roue à ergot excentrique (766) disposée notamment sur l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807) entraînant un levier basculant (768).
  21. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un déroulement d'un mouvement de l'au moins un élément d'excursion supplémentaire présente un tracé dans le temps différent d'une forme sinusoïdale.
  22. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une déviation du premier élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a) présente une première fréquence et en ce qu'une déviation du deuxième élément d'excursion (20a, 120a, 220a, 320a, 420a, 520a, 620a, 720a, 820a, 920a) de l'au moins un deuxième dispositif générateur d'excursion supplémentaire (23, 123, 223, 323, 423, 523, 623, 723, 823, 923) présente une deuxième fréquence F2 s'écartant notamment de la première fréquence F1, la deuxième fréquence étant notamment égale à environ la moitié de la première fréquence.
  23. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'entre le premier dispositif générateur d'excursion (13, 113, 213, 313, 413, 513, 613, 713, 813, 913) et l'au moins un deuxième dispositif générateur d'excursion supplémentaire (23, 123, 223, 323, 423, 523, 623, 723, 823, 923), il est prévu un dispositif de palier (8) en position fixe par rapport à un carter de machine (2, 102, 202, 302, 402, 502, 602, 702, 802, 902) de la machine-outil portative, servant au support sur palier rotatif de l'arbre intermédiaire (7, 107, 207, 307, 407, 507, 607, 707, 807, 907) dans le carter de machine (2, 102, 202, 302, 402, 502, 602, 702, 802, 902).
EP08873253.2A 2008-03-14 2008-11-19 Machine manuelle pour outils entraînés en frappe Active EP2265419B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008000677A DE102008000677A1 (de) 2008-03-14 2008-03-14 Handwerkzeugmaschine für schlagend angetriebene Einsatzwerkzeuge
PCT/EP2008/065845 WO2009112101A1 (fr) 2008-03-14 2008-11-19 Appareil portatif pour outils entraînés en percussion

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EP2265419A1 EP2265419A1 (fr) 2010-12-29
EP2265419B1 true EP2265419B1 (fr) 2021-05-05

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EP (1) EP2265419B1 (fr)
CN (1) CN101970181B (fr)
DE (1) DE102008000677A1 (fr)
RU (1) RU2518020C2 (fr)
WO (1) WO2009112101A1 (fr)

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RU2518020C2 (ru) 2014-06-10
EP2265419A1 (fr) 2010-12-29
DE102008000677A1 (de) 2009-09-17
CN101970181B (zh) 2013-06-19
CN101970181A (zh) 2011-02-09
RU2010141586A (ru) 2012-04-20
WO2009112101A1 (fr) 2009-09-17
US8464805B2 (en) 2013-06-18
US20110017483A1 (en) 2011-01-27

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