EP2265420A1 - Machine-outil portative pour outils entraînés en percussion - Google Patents

Machine-outil portative pour outils entraînés en percussion

Info

Publication number
EP2265420A1
EP2265420A1 EP08873254A EP08873254A EP2265420A1 EP 2265420 A1 EP2265420 A1 EP 2265420A1 EP 08873254 A EP08873254 A EP 08873254A EP 08873254 A EP08873254 A EP 08873254A EP 2265420 A1 EP2265420 A1 EP 2265420A1
Authority
EP
European Patent Office
Prior art keywords
hand tool
tool according
drive
intermediate shaft
counter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08873254A
Other languages
German (de)
English (en)
Other versions
EP2265420B1 (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
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 EP2265420A1 publication Critical patent/EP2265420A1/fr
Application granted granted Critical
Publication of EP2265420B1 publication Critical patent/EP2265420B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • 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
    • 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
    • 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
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
    • 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 tool according to the preamble of the independent claims.
  • the wobble drive comprises a swash plate with an integrally formed wobble finger, which is mounted on a drive sleeve by means of a wobble bearing such that the wobble finger by means provided on the drive sleeve, tilted to the intermediate shaft against an angle raceway of the bearing elements by rotation of the intermediate shaft in an axial deflection movement is offset.
  • the handheld power tool of DE 198 51 888 has a counterweight designed as a counterweight, which is driven by means of a second, diametrically formed against the first wobble finger on the swash plate wobble finger. Due to the diametrically opposite arrangement of the wobble fingers, a phase shift ⁇ of 180 ° occurs between the axial deflection movements of the wobble fingers.
  • the mass forces which are adjusted by the oscillating deflection movement of the exciter sleeve, are particularly high in the reversal points, ie in the region of the maximum occurring speed changes, so that their compensation is particularly effective at a phase shift ⁇ of the counteroscillator of 180 ° to the excursion movement of the exciter sleeve.
  • so-called air forces occur in air cushion impact devices, inter alia due to cyclically changing pressure conditions in the air cushion of the air cushion impactor, which also stimulate vibrations. Especially with very easily constructed exciter sleeves, the air forces can even outweigh the mass 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.
  • a hammer drill is known in which a second wobble finger is formed on the swash plate, but which includes an angle not equal to 180 ° to the first wobble finger for driving exciter sleeve.
  • 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 hand tool of the invention with the features of the main claim has the advantage that the movement of the counter-oscillator in its phase position on the resulting from the mass and air forces, vibration-inducing effective forces can be tuned particularly effective.
  • the separate drive of the counter-oscillator further 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 expensive bearings.
  • a compact design of a hand tool according to the invention is achieved by a drive of the at least one additional second Huber Wegungsvoriques by the intermediate shaft.
  • a particularly effective drive of the counter-oscillator is achieved by a phase shift ⁇ not equal to 90 °.
  • the phase shift ⁇ between the movement of the first lifting element and the movement of the second lifting element is between 190 ° and 260 °.
  • the phase shift ⁇ is between 200 ° and 240 °.
  • a particularly effective embodiment of the counter-oscillator has at least one counter-oscillatory mass. This will be along a linear or non-linear
  • Movement path in particular along a straight line or a circular arc out.
  • a compact and at the same time effective embodiment of the counter-oscillator has a center of gravity track close to the striking axis.
  • the center of gravity path is parallel, preferably coaxial to the impact axis.
  • the second stroke generating device has a coupling device.
  • the second Huber Wegungsvortechnik can be rotatably coupled to the first of the Huber Wegungsvortechnische.
  • the second lift generating device is activated only in selected operating states of the hand tool. For example, deactivation of the second lift generating device in an idle state of the handheld power tool may be advantageous.
  • the coupling device is designed as an engaging clutch.
  • an axial displacement path between an engaged state and an open state is provided.
  • the one amplitude of the movement of the counter-oscillator can be made adjustable in a particularly simple manner.
  • the second stroke generating device has an additional deflection element.
  • a second counteroscillator can be driven by the additional deflecting element.
  • the first Huber Wegungsvorraum is designed as a first crank drive.
  • the crank drive comprises at least one connecting rod and a crank disk.
  • On the crank disc an eccentric pin is provided.
  • the connecting rod engages the eccentric pin.
  • the connecting rod acts as a first lifting element.
  • first bevel gear which is arranged on the intermediate shaft.
  • the first bevel gear is rotationally driven by the intermediate shaft.
  • a second bevel gear is provided, which is arranged on a bevel gear shaft.
  • the bevel gear shaft advantageously extends perpendicular to the intermediate shaft.
  • the second bevel gear is rotatably connected to the bevel gear shaft and is rotatably driven by the first bevel gear.
  • crank pin bearing the eccentric pin is arranged on the bevel gear shaft.
  • the crank disk is driven.
  • the second stroke generating device is designed as a second wobble drive.
  • This second wobble drive comprises at least one second drive sleeve bearing a second raceway, a second wobble bearing and a second wobble plate with a wobble finger arranged thereon.
  • the second Huberzeugungsvorraum is designed as a cam drive.
  • the cam drive is a cylinder-crank drive with a on arranged a lateral surface, which forms at least one additional lifting element deflecting trajectory.
  • the counteroscillator is deflected by the additional lifting element along the trajectory.
  • 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 counteroscillator, so that the counteroscillator 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, wherein the counteroscillator is operatively connected via a push rod with the intermediate shaft.
  • a preferred development of the hand tool according to the invention has a sequence of movement of the second lifting element on a time behavior deviating from a sinusoidal shape.
  • the movement sequence of the counteroscillator can advantageously be adapted to a time behavior of the vibration-inducing effective forces.
  • a deflection of the first lifting element has a first frequency.
  • a deflection of the second lifting element of the second lifting device has a, in particular deviating from the first frequency, second frequency.
  • the second frequency is in particular about half as large as the first frequency.
  • Fig. Ia is a side view of a first embodiment
  • FIG. 1b is a sectional view through the embodiment of FIG. Ia (line T-T)
  • 1 c is a sectional view through the embodiment I of FIG. Ic (line U-
  • 3a and 3b each show a perspective view of an alternative counter-oscillator as a second embodiment
  • Fig. 4a is a perspective schematic view of a third embodiment
  • 4b is a perspective schematic view of a fourth embodiment
  • Fig. 4c is a schematic perspective view of a fifth embodiment
  • Fig. 4d is a schematic perspective view of a sixth embodiment
  • Fig. 5a is a schematic side view of a further development of the embodiment of Fig. Ia as the seventh embodiment
  • 5b is a schematic side view of another development of the
  • Fig. 6 is a schematic side view of a ninth embodiment
  • Fig. 7 is a schematic side view of a tenth embodiment
  • 8a is a schematic side view of a further development of
  • FIG. 8b is a sectional view through the embodiment of Fig. 8a (line A-A)
  • Fig. 8c is a schematic representation of the phase relationship of the movements of
  • Fig. 9 is a schematic side view of a twelfth embodiment
  • Fig. 10 is a schematic side view of a thirteenth embodiment
  • the hammer drill 1 comprises a not shown here machine housing 2, which surrounds a drive motor not shown here and a transmission portion 3.
  • the transmission section 3 is through an intermediate flange 21, via which it is connected to a, the drive motor-bearing portion of the machine housing 2.
  • the transmission region 3 has a transmission device 4, by means of which a hammer tube 5 can be coupled to the drive motor, so that it can be driven in rotation.
  • the hammer tube 5 is arranged in the transmission area 3 and is rotatably mounted in the intermediate flange 21.
  • the hammer tube 5 extends along a machine axis 6 away from the intermediate flange 21.
  • a torque provided by the drive motor is transmitted to the hammer tube 5 via the transmission device 4.
  • the transmission device 4 it is also possible to speak here of a rotary drive of the hammer tube 5.
  • the transmission device 4 has an intermediate shaft 7, which is arranged parallel to the machine axis 6 in the transmission region 3 of the machine housing 2 below the hammer tube 5.
  • the intermediate shaft 6 is rotationally coupled by a plurality of bearing devices 8 from the machine housing 2.
  • a driven spur gear 10a output gear 10 In a side facing away from the drive motor portion 9 of the intermediate shaft 7 is designed as a driven spur gear 10a output gear 10 and rotatably connected to the intermediate shaft 7.
  • a Antriebsstirnrad 11 is arranged, which meshes with the output spur gear 10a.
  • the Antriebsstirnrad 11 is operatively connected via an overload safety coupling 12 with the hammer tube 5.
  • the drive wheel 11 If the torque applied to the drive wheel 11 is below a limit torque of the overload safety clutch 12, then the drive wheel 11 is connected in a rotationally fixed manner 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 used.
  • the tool holder 5 a is rotatably connected to the hammer tube 5.
  • the tool holder 5a thus transmits the torque acting on the hammer tube to the insertion tool.
  • the tool holder 5a also provides a limited axial mobility of the insert tool along a defined by a longitudinal extent of the insert tool tool or striking axis.
  • the tool or impact axis and the machine axis 6 are aligned coaxially with each other, so that in the following the term impact axis 6 synonymous with the machine axis 6 is used.
  • the striking element If the piston moves in the direction of the tool holder, the striking element is accelerated until it strikes an end region of the insertion tool. In this case, the momentum of the striking element is transmitted as impact pulse to the insert tool.
  • the gear device 4 according to the invention from FIG. 1 a comprises a first stroke generating device 13 designed as a wobble drive 13 a.
  • the wobble drive 13 a is arranged with a first drive sleeve 14 in a region 15 of the intermediate shaft 7 facing the drive motor.
  • the drive sleeve is hereby preferably rotatably connected to the intermediate shaft 6.
  • a first career 16, not shown here is provided on the drive sleeve 14.
  • the track 16 is circular and tilted in an impact axis 6 and the intermediate shaft 7 containing impact plane by an angle Wl, which is greater than zero and less than 180 ° and in particular preferably between 45 ° and 135 °.
  • wobble bearing 17 is arranged, which is preferably designed as a ball bearing.
  • 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 Fig. Ic are best seen.
  • a swash plate 19 is arranged, which comprises the bearing elements 18 of the swash bearing 17.
  • wobble finger 20 is arranged, preferably formed.
  • the wobble finger 20 extends away from the intermediate shaft 7 in the direction of the striking 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 impact mechanism.
  • the drive sleeve 14 is set with the career provided thereon 16 in rotation.
  • the wobble bearing 17 is forcibly guided with its bearing elements 18 on the raceway 16, so that the swash plate 19 is indeed woodrekoppelt of the intermediate shaft 7, but is offset by the positive guidance in a tumbling movement.
  • the tumbling motion causes the tumbling finger 20 to perform an oscillating axial movement in the direction of the striking axis 6.
  • the tumble-finger 20 acts as the first lifting element 20a of the first Huber Wegungsvorraum 13.
  • the oscillating axial movement of the wobble finger 20 is transmitted to the piston of the Heilpolster Kunststoffwerks.
  • the transmission device 4 according to the invention from Fig. Ia further comprises a second Huber Wegungsvorraum 23, which is designed in the present embodiment as the second wobble drive 23a.
  • the best way is to see the second wobble drive 23a in FIG. 1c.
  • the second wobble drive 23a is arranged on the intermediate shaft 7 on a front side of the first wobble drive 13a 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 track 26, wherein the second drive sleeve 24 is preferably non-rotatably coupled to the intermediate shaft 7.
  • a second wobble bearing 27 is provided with bearing elements 28, which are guided along the second raceway 26 and are covered by a second swash plate 29.
  • the swash plate 29 carries a second wobble finger 30.
  • the second race 26 is tilted in the impact plane containing the striking 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 relative to the first wobble finger 20 by a twist angle WV in the circumferential direction of the intermediate shaft 7 from the impact planes, as shown in Fig. Ib.
  • Rotation angle WV is an adjustment of the second wobble drive 23a to structural constraints in the machine housing 2.
  • the possible twisting WV a possible collision of the first wobble finger 20 with the second wobble finger 30 during operation of the transmission device 4 even with large strokes of the tumble finger 20, 30 avoided ,
  • the end of the wobble finger facing away from the second swash plate 29 is received in a counter-oscillator 31.
  • the counteroscillator 31 may have a receiving bearing 32 for low-friction reception of the wobble finger 30, which is shown in Fig. Ic.
  • the counteroscillator 31 is designed essentially as a counteroscillating mass 33.
  • the counter-oscillator mass 33 is designed as a cylindrical mass body.
  • the counteroscillator 31 is in the first embodiment laterally on a sleeve-shaped portion 22 of the intermediate flange
  • the sleeve-shaped portion 22 is provided for this purpose with a receiving groove 36, in which the cylindrical counter-oscillator mass 33 is received.
  • the counter-oscillator 31 is encompassed by a guide element 34, as shown in Fig. Ib.
  • the guide member 34 is releasably secured in the present example by means of screw on the sleeve-shaped portion 22.
  • further attachment options such as clamping, latching, riveting, soldering or welded joints are known, which can be advantageous here.
  • the guide element can also be arranged, for example, in the surrounding machine housing 2.
  • the counter-oscillator 31 is guided by the guide element 34 and the receiving groove 25 on a linear path, in particular a line piece parallel to the impact axis 6.
  • a linear path in particular a line piece parallel to the impact axis 6.
  • the expert will not be difficult to select the most suitable web form in each application.
  • the first drive sleeve 14 and the second drive sleeve 24 are rotatably connected to each other in the present embodiment.
  • a relative rotational position of the raceways is adjusted to one another between the first track 16 and the second track 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 can be seen, inter alia, in FIG. From the relative rotational position and the angles W1 and W2 of the first and second wobble finger 20, 30 there is a phase shift ⁇ between the oscillating axial movements of the two wobble fingers 20, 30.
  • the second drive sleeve 24 is in contrast provided with corresponding receiving elements, in which, in particular during assembly of the transmission device 4, the locking elements engage to produce a positive connection.
  • a frictional connection can be brought about, for example, by a press fit between the first drive sleeve 14 and the second drive sleeve 24.
  • this simple non-positive connection may also be more complex Compounds, for example, include an additional link, such as a connecting sleeve.
  • the first drive sleeve and the second drive sleeve can also be produced in one piece.
  • the sintering technique or the metal injection molding (MIM) come into question.
  • rotationally fixed connection is detachable, in particular axially detachable. Possible embodiments are shown and described in FIGS. 10a and 10b, to which reference is made at this point.
  • the inertial forces act directly on the piston, the impact element and the hammer tube and stimulate them to vibrate.
  • the accelerations at the reversal points of the axial movement of the piston are relatively high, so that the mass forces show a pulse-like time response and particularly strong vibration excitations occur.
  • the time behavior is synchronous with the state of motion of the piston.
  • the counteroscillator 31 is preferably deflected in antiphase to the oscillating axial movement of the piston. Between the oscillating axial movement of the piston and the oscillating axial movement of the counter-oscillator 31, in the case of pure mass forces, a phase shift ⁇ of 180 ° advantageously takes place.
  • the stroke of the oscillating axial movement of the Jacobschwingers 31 is a parameter for tuning a reduction effect of the counter-oscillator 31 to the respective air cushion impact mechanism.
  • phase shift ⁇ between the oscillating axial movement of the piston and the oscillating axial movement of the counter-oscillator 31 can be made and adjusted in a simple manner.
  • the adjustment of the phase shift ⁇ is a temporal behavior of the vibration-inducing effective forces, which are composed of the inertial forces and the air forces, take into account.
  • the phase shift ⁇ will be between 190 ° and 260 °.
  • the phase shift ⁇ is between 200 ° and 240 °.
  • FIGS. 2a to 2b the sequence of the oscillating axial movements of a piston 38 and the counter-oscillator 31 and thus of the first wobble finger 20 and the second wobble finger 30 is shown by way of example in one case.
  • the figures show different phases of movement.
  • the piston 38 is in its forward dead center, which is marked by the marking "Impact drive VT 0 °.”
  • the counter-oscillator 31 is at this point in a position before its rear dead center, which is indicated by the marking "counterweight HT”. is designated.
  • the piston 38 is on its way to its rear dead center (mark “Impact Drive HT 180 °"), while the counteroscillator 31 has just reached its rear dead center
  • a preferred further development provides for an additional, not shown, articulation element on the second swash plate 29 of the second wobble drive 23a.
  • the additional coupling element is preferably arranged at a circumferential angle WA to the second wobble finger 30 on the swash plate 29, preferably formed.
  • a second counteroscillator is preferably driven.
  • 3a and 3b show a perspective view of a further development of the above-described embodiment of a hand tool according to the invention as a second embodiment.
  • the reference numerals of the same or equivalent features are increased by 100 in the illustration.
  • FIG. 3 a shows a counter-oscillator 131, which comprises three counter-oscillatory masses 133 a, 133 b, 133 c connected by a bow-shaped connecting element 135.
  • the counter-oscillator 131 is constructed of two predominantly mirror-symmetrical half-elements in order to allow easier mounting. The half elements are screwed together during assembly.
  • a receiving pivot bearing 132 is provided in the counterweight 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 portion 122 of the intermediate flange 121 and mounted on this axially displaceable.
  • the sleeve-shaped portion 122 receiving grooves 136a, 136b, 136c, in which the cylindrical counter-oscillator masses 133a, 133b, 133c are received.
  • the counteroscillator 133a is held and guided by a guide element 134 on the sleeve-shaped section 122.
  • the counter-oscillator masses 133a, 133b, 133c of the second embodiment are designed in their masses and their positioning so that the counter-oscillator 131 has a center of gravity M located centrally.
  • This center of gravity M is arranged so that it comes to lie substantially on the striking axis 106.
  • the center of gravity M describes a center of gravity track which runs essentially parallel, preferably coaxially, to the striking axis 106.
  • the counter-oscillator 131 can counteract the vibration-inducing 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 impactor, which are arranged predominantly cylindrically symmetrical about the striking axis 6 in a known manner that their centers of gravity also run parallel, predominantly even coaxial with the axis of impact 6.
  • FIG. 4a shows a perspective schematic view of a third exemplary embodiment of a transmission device 204 according to the invention.
  • the reference signs of identical or equivalent features are increased by 100 in the illustration. 4a, only the first and second lift generating devices 213, 223 arranged on the region 215 of the intermediate shaft 207 facing the drive motor are shown in FIG. 4a, wherein instead of the intermediate shaft 207, only one intermediate shaft axis 207a is shown.
  • the Huberzeugungsvorraumen are executed in this embodiment as a first wobble drive 213a and a second wobble drive 223a. In this case, the first wobble drive 213a in to the preceding
  • Embodiments known manner constructed, so that waived its description.
  • the third embodiment differs from the previous embodiments by a modification of the second wobble drive 223a.
  • two output fingers 237a, 237b are provided on the second swash plate 229. These output fingers 237a, 237b are connected in laterally circumferential direction of the swash plate 229 with this, preferably formed on this.
  • the output fingers 237a, 237b extend arcuately about a piston 238 of the air cushion impact mechanism connected to the first wobble finger 220.
  • output fingers 237a, 237b are designed mirror-symmetrically to the beating plane, which defines the striking axis 206 and the Intermediate shaft axis 207a includes. However, it may be advantageous to deviate from this symmetry.
  • the output fingers 237a, 237b are connected to a finger head 240 carrying an output element 239, preferably in one piece with the latter.
  • the output element 239 is in operative connection with the counteroscillator 231.
  • the driven element 239 can be accommodated similarly to the already known second wobble finger 30, 130 in a receiving pivot bearing 232 provided on the counter-oscillator mass 233.
  • 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 embodiment corresponds to the first embodiment, so that reference is made to the description thereof.
  • FIG. 4b a modified embodiment of the third embodiment of Fig. 4a is shown as a fourth embodiment.
  • the representation is analogous to the representation in FIG. 4a. It will be discussed at this point only to a modification, since the basic structure and operation corresponds to that of the third embodiment.
  • the second swash plate 229 of the second wobble drive 223a has an output finger 237a on only one side.
  • the output finger 237a is arcuate.
  • the finger head 240 is mounted, which carries the driven element 239.
  • the counteroscillator 231 is disposed in the beating plane above the piston 238.
  • the fourth embodiment corresponds to the first embodiment, so that reference is made to the description thereof.
  • a combination of the second embodiment of Fig. 3a and the third embodiment of Fig. 4a is shown as a fifth embodiment.
  • the representation is analogous to the representation in FIG. 4a. It will be discussed at this point only to a modification, since the basic structure and operation corresponds to that of the third embodiment. Contrary to the embodiment of the third 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.
  • the receiving rotary bearing 232 is provided in the counter-oscillator 231 in the central counter-oscillator mass 233b, since this is analogous to the counter-oscillator 231 of the exemplary embodiments three and four is arranged in the beating plane below the finger head 240. Due to its three-part design, the center of gravity M of the counter-oscillator is located centrally between the counter-oscillator masses 233a, 233b, 233c. By a suitable choice of the counter-oscillatory masses a predominantly coaxial to the striking axis shaping of the center of gravity is achieved in an oscillating axial movement of the counter-oscillator.
  • Fig. 4d a modified embodiment of the third embodiment of Fig. 4a is shown as a sixth embodiment.
  • the representation is analogous to the representation in FIG. 4a. It will be discussed at this point only to a modification, since the basic structure and operation corresponds to that of the third embodiment.
  • the finger head 240 of the two output fingers 237a, 237b itself is designed as a counter-oscillator mass 233.
  • the finger head 240 thus acts as a counter-oscillator 231. Due to a pivoting movement of the output fingers 237a, 237b triggered by the swash plate 229, the counteroscillator in the present case performs a pivoting movement in the impact plane.
  • the counteroscillator is performed as in particular on a circular arc-shaped path.
  • a guide pin 241 can alternatively be arranged on the finger head 240 as an alternative to the counter-oscillator 231 of the sixth exemplary embodiment or in addition thereto, in particular be formed.
  • This guide pin 241 is preferably oriented away from the swash plate 229.
  • On the guide pin 241 can further be arranged a counter-oscillator 231, not shown here, which comprises a gate 242.
  • the guide pin 241 protrudes into this slot 242 and transmits the oscillating axial movement of the finger head 240 to the counter-oscillator 231 carrying the gate 242.
  • An exemplary embodiment of a slot 242 is shown in FIG. 8b.
  • a second stroke generating device 23 according to the invention in the form of a second wobble drive 23a, 123a, 223a
  • combinations of the individual features of the exemplary embodiment described above may result among one another as well as features of wobble drives known to the person skilled in the art.
  • FIG. 5a shows a schematic side view of a further development of the embodiment from FIG. 1a as a seventh exemplary embodiment.
  • the reference signs of the same or equivalent features are indicated in this illustration by a prefix 8.
  • the lift generating devices 813, 823 configured as first and second wobble drive 813 a, 823 a are shown in a further development.
  • first drive sleeve 814 is rotatably connected to the intermediate shaft 807.
  • the second drive sleeve 824 is axially displaceable, loosely rotatably mounted 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 coupling device 872, 873 is brought into an activated or engaged state, so that the second drive sleeve 824 is now rotatably connected to the first drive sleeve 814.
  • 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.
  • At the side of the second drive sleeve 824 corresponding to this side at least one, but preferably two or more mating coupling elements 875 are provided, with which the coupling elements 874 can be coupled between the first drive sleeve 814 and the second drive sleeve 824 to produce a rotary connection.
  • the counter-coupling elements 875 by an axial displacement of the second drive sleeve 824 with the
  • Coupling elements 874 engaged.
  • the person skilled in the art for concrete execution of the coupling elements 874 and corresponding to these counter-coupling elements 875 various embodiments are known.
  • frontal or circumferential gears and counter teeth can be used.
  • coupling devices 873 are provided with coupling elements such as e.g. Balls and ball receivers conceivable to name just two known versions.
  • the drive of the counter-oscillator 831 can be made switchable via the second wobble drive 823a.
  • the counter-oscillator 831 is disabled. Only when starting a work activity, in particular with impact drive of the insert tool, the drive of the counter-oscillator 831 is manually or automatically put into operation.
  • Fig. 5b shows a schematic side view of a further development of the embodiment of Fig. 5a as a sixteenth embodiment.
  • the embodiment of an engagement clutch 872 shown here is already known in particular from DE 10 2004 007 046 A1, to the description of which reference is explicitly made at this point.
  • an axially displaceable displacement sleeve 876 is arranged on the side of the intermediate shaft 807 facing away from the drive motor, which on its side facing the second drive sleeve 824 carries a conically tapering displacement wedge 877.
  • the second drive sleeve 824 is freely rotatably mounted on the intermediate shaft 807 in this embodiment.
  • a through hole 878 which has a conically opening receiving diameter with in each case different cone angles in both directions along the intermediate shaft 807.
  • the displacement of the sleeve 876 facing side of the through hole in this case has a corresponding to the displacement wedge 877 cone angle.
  • the displacement sleeve 876 is held in an idle state of the hammer drill 801 by means of a return element 879, which is designed here as a spring element 880, in a disengaged position.
  • the idling state is defined so that in this state, the recorded in the tool holder 805a insert tool is not pressed against a workpiece.
  • the displacement wedge 877 is not engaged with its corresponding tapered receiving diameter.
  • 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 rest state tilted at 90 ° to the intermediate shaft 807, so that the counteroscillator 731 also experiences no deflection due to this. If now the insert tool is 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 engages the corresponding reception diameter. As a result, on the one hand, a rotary connection between the second drive sleeve 824 and the intermediate shaft 807 is produced.
  • FIG. 6 shows a schematic side view of a rotary hammer 601 with a gear device 604 according to the invention.
  • the reference signs of identical or equivalent features are indicated in this illustration by a preceding 6.
  • the transmission device 604 includes as the first lift generating device 613 a crank drive 613b.
  • Bevel gear 685 arranged and rotatably driven by the intermediate shaft 607.
  • the first bevel gear 685 rotatably, preferably releasably rotatably connected to the intermediate shaft 607.
  • a second bevel gear 686 is arranged above the intermediate shaft 607.
  • the second bevel gear 686 is arranged on a bevel gear shaft 687 and preferably rotatably connected thereto.
  • the bevel gear shaft 387 extends perpendicular to the intermediate shaft 607 in the direction of the impact axis 606.
  • the second bevel gear 686 is rotationally driven by the first bevel gear 685. In this way, a rotational movement of the intermediate shaft 607 via the first and second bevel gear 685, 686 transmitted to the bevel gear 687.
  • crank disc 688 At one of the impact axis 606 facing the end of the bevel gear shaft 687, a crank disc 688 is provided.
  • This crankshaft 688 is non-rotatably, preferably releasably rotatably connected to the bevel gear shaft 687, so that a rotational movement of the bevel gear shaft 687 can be transferred to the crank disc 688.
  • an eccentric pin 689 is arranged in a radially outer region, preferably formed. At the eccentric pin 689 engages a connecting rod 690, preferably with its one end. At another end of the connecting rod 690 this is operatively connected to the piston 638 of the air cushion impact mechanism.
  • a receiving pivot bearing in which the connecting rod 690 engages, is preferably provided in the piston 638.
  • crank pulley 688 and thus the eccentric pin 689 arranged thereon are set in a rotary motion.
  • the eccentric pin 689 and the connecting rod 690 acting thereon perform an oscillating axial movement, which is transmitted to the piston 638.
  • the skilled person many modifications of the schematically sketched crank drive 613b are known, which may result in the context of the present invention advantageous embodiments of a hand tool of the invention.
  • the crank drive 613b can be advantageously supplemented by a coupling device acting between bevel gear shaft 687 and second bevel gear 686 or between bevel gear shaft 687 and crank disk 388.
  • the second bevel gear 386 and the crank pulley 688 may be made in one piece.
  • the eccentric pin 689 may be arranged directly on the second bevel gear 686.
  • the transmission device 604 includes, as a second lift generating device 623, a wobble drive 623a already known from the foregoing. These will therefore not be discussed further here. Also, the above-described modifications of the wobble drive 623b may be applied to the embodiment of the present embodiment.
  • the counteroscillator 631 therefore behaves analogously to the embodiment known from FIG.
  • the adjustment of a phase shift ⁇ takes place in this
  • Embodiment by selection of the angle W2 of the track 626 of the wobble drive 623a, taking into account the circumferential angle WE of the eccentric pin 689 on the crank disk 688.
  • FIG. 7 shows a schematic side view of a hammer drill 301 with a gear device 304 according to the invention as a ninth exemplary embodiment.
  • the transmission device 304 comprises as the first lift generating device 313 a crank drive 313b, which is already known from the preceding embodiment. Their description is referenced at this point.
  • the second lift generating device 323 for driving a counter-swing 331 is designed as a cam drive 323b.
  • a trajectory 344 is provided on an outer circumferential surface of the cam cylinder 343.
  • the trajectory has an axial course 345 which varies in the circumferential direction of the curve cylinder 343.
  • the axial course 345 can be given by a circular path tilted at an angle W3 to the intermediate shaft. It can however, other, in particular non-linear, web forms, such as, for example, spiral paths, sinusoidal paths and similar pathways, may also be advantageous.
  • the trajectory 344 is groove-shaped in the outer circumferential surface of the cam cylinder 343.
  • the sleeve elements can be produced by punching and then wound into a sleeve. The skilled worker is known to other methods.
  • 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 member 346 is in a predominantly fixed radial position to the cam cylinder 343. The guide member 346 engages the trajectory 344 and is guided by this.
  • the cam cylinder 343 is rotationally driven by the intermediate shaft 307.
  • the guide element 346 is deflected along the axial course 345 of the trajectory 344, so that it is possible to speak of an oscillating axial movement.
  • the adjustment of a phase shift ⁇ in this embodiment takes place by selecting a rotational position of the trajectory 344, taking into account the circumferential angle WE of the eccentric pin 389 on the crank disc 388 of the first stroke generating device 313, 313b.
  • the axial movement of the guide member 346 is repeated after one complete revolution of the cam cylinder 343.
  • the counter-oscillator 331 therefore behaves analogously to the embodiment known from FIG.
  • trajectories 344 are also possible which deviate from this relationship.
  • repetition of the axial movement may be an integer multiple or an integral proportion of one revolution of the cam cylinder 343.
  • FIGS. 8a to 8c an example is made in FIGS. 8a to 8c, to which reference is made at this point.
  • the counteroscillator 331 Due to the oscillating axial movement of the guide element 346, the counteroscillator 331 is set into oscillating axial movements.
  • a desired phase shift ⁇ between the first wobble finger 320 and the guide member 346 is set as a lifting element 330a of the second Huber Wegungsvorraum 323, 323b become.
  • the counteroscillator 331 acts analogously to the preceding exemplary embodiments.
  • the transmission device 904 includes as the first lift generating device 913 a crank drive 913b already known from the foregoing. Their description is referenced at this point.
  • the second Huber Wegungsvortechnisch 923, 923b on a cam cylinder 943 which is arranged in the drive motor remote area 909 of the intermediate shaft 907 on this and preferably rotatably connected thereto.
  • a trajectory 944 is provided on an outer circumferential surface of the cam cylinder 943.
  • the trajectory 944 is executed in the embodiment shown here as an opposite, intersecting spiral path 981.
  • the spiral track 981 has two revolutions in each direction.
  • the guide element 946 provided on the counter-oscillator mass 933 is designed here as a rail slide 982, which can best be seen in FIG. 8b.
  • the rail slider 982 has, in the form shown here, at least two guide elements 983, which are preferably designed as balls.
  • the guide elements 983 are freely rotatably mounted on a carrier element 984 in a distance extending in the circumferential direction of the cam cylinder 943.
  • the cam cylinder 943 rotates at the same speed as the intermediate shaft 907.
  • the spiral path 981 causes the axial deflection of the counter-oscillator 931 to take place via the spiral cam 981
  • FIG. 8c shows to a schematic stroke-time diagram for the deflections of the piston and counter-oscillator, as it corresponds to this embodiment.
  • FIG. 9 shows a schematic side view of a hammer drill 401 with a gear device 404 according to the invention as an eleventh exemplary embodiment.
  • the reference signs of the same or equivalent features are indicated in this illustration by a prefixed 4.
  • the transmission device 404 includes as the first lift generating device 413 a crank drive 413b already known from the foregoing. Their description is referenced at this point.
  • the second lift generating device 423 for driving a counter-swing 431 is a front curve drive 423c.
  • the Stirnkurvenantrieb 423c has a, on a for
  • the surface profile 449 has, in particular, an axial course 451 which varies in the circumferential direction of the cam disk 450.
  • the counteroscillator 431 is pioneered axially by the drive motor in front of the intermediate shaft 307, in particular in front of the cam disc 450 in the machine housing 402.
  • the counteroscillator 431 has a pressure element 452, by which the counter-oscillator mass 433 of the counter-oscillator 431 is biased axially in the direction of the cam disc 450.
  • the pressure element 452 is designed in the present case as a prestressed coil spring 452a.
  • the coil spring 452a is supported on its end remote from the transmission device on a housing-fixed contact element 454 in the machine housing 302. Their opposite end is supported on an abutment ring 455 provided on the counterweight 433.
  • further pressure elements 452 such as, for example, elastomers or other spring elements, which can be used advantageously within the meaning of the invention, are known to the person skilled in the art. Also, in the assembly of the pressure elements 452 of the shape shown here deviating investment and / or mounting elements may be advantageous.
  • the counter-oscillator mass 433 is pressed against the surface profile 449 by this bias.
  • the counter-oscillator mass 433, on its side facing the cam disk has a contact element 453 which is pressed against the surface profile in an outer radius region of the cam disk 450. If the cam 450 is rotatably driven by the intermediate shaft 407, the
  • the temporal course of the axial movement can be influenced in a targeted manner via the cam profile 449, in particular the axial course 451.
  • deviating motion profiles can be generated by a sinusoidal form that is typical for oscillating movements.
  • a multiple deflection per revolution of the cam plate 450 is possible depending on the cam profile 450.
  • FIG. 10 shows a schematic side view of a hammer drill 501 with a transmission device 504 according to the invention as a twelfth exemplary embodiment.
  • the reference signs of the same or equivalent features are indicated in this illustration by a preceding 5.
  • the transmission device 504 includes as the first lift generating device 513 a crank drive 513b already known from the foregoing. Their description is referenced at this point.
  • the second lift generating device 523 for driving a counter-swing 531 is designed as a push rod drive 523d.
  • a drive pulley 556 is arranged and rotatably driven by the intermediate shaft 507.
  • the first bevel gear 585 is formed as a drive pulley 556.
  • a rotary joint 557 is provided on an end face of the drive pulley 556.
  • a push rod 558 is operatively connected at one end to the drive pulley 556.
  • a second pivot 559 is provided which the push rod 558 operatively connected to the counter-oscillator mass 533 of the counter-oscillator 531.
  • the counteroscillator 531, in particular the second pivotable 559 is placed at a radial distance away from the intermediate shaft axis 507a.
  • the counter-oscillator mass 533 is axially displaceable along a path. In a particularly preferred manner, this track is a straight line parallel to the impact axis 506.
  • the drive pulley 556 is rotationally driven by the intermediate shaft 507, whereby the push rod 558 follows the rotary motion via the first pivot 557. Due to the axial guides of the counter-oscillator mass 533, the movement of the push rod 558 is transmitted to the second pivot 559 in the form of an oscillating axial movement of the counter-oscillator mass 533.
  • the counteroscillator 531 therefore behaves analogously to the already known embodiments.
  • a phase shift ⁇ is done in this embodiment by a circumferential angle WU below the first pivot 557 on the drive pulley 556, and the relative position of the second pivot 559 to the first pivot 557.
  • the circumferential angle WE of the eccentric pin 589 on the Crankshaft 588 of the first lift generating device 513, 513b to consider.
  • Variations of this embodiment of a transmission device according to the invention arise inter alia in the design of the hinges 557, 559 and / or the push rod 558.
  • the design of the counter-oscillator mass 533 can be diverse. In particular, advantageous combinations may result from the already exemplary embodiments which the person skilled in the art will readily recognize.
  • an adjusting device acting on the raceway 26 of the second drive sleeve 24 is provided, which goes beyond the stroke setting for the lifting element 30a of the second lift generating device 23 known from the sixteenth embodiment.
  • the displacement wedge could be executed asymmetrically and either manually or by an actuator in its rotational position relative to the machine housing 2, in particular beating plane, be changeable.
  • the person skilled in the art will be familiar with further ways of implementing such an adjustment device.
  • a bearing device 8 is provided between the first lift generating device 13 and the second lift generating device 23.
  • the bearing device 8 is fixed to the housing in the machine housing 2.
  • This bearing device 8 serves a pivot bearing of the intermediate shaft 7 in the machine housing. 2

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Transmission Devices (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Percussion Or Vibration Massage (AREA)
  • Drilling And Boring (AREA)
  • Harvester Elements (AREA)

Abstract

L'invention concerne une machine-outil portative pour outils entraînés principalement en percussion, en particulier des marteaux perforateurs et/ou burineurs, avec un axe de percussion (606) et un arbre intermédiaire (607) parallèle à cet axe de percussion (606), ainsi qu'un premier dispositif de génération de course (613) avec un élément mobile pour un entraînement en percussion. Par ailleurs, il est prévu au moins un autre dispositif de génération de course (623) comprenant au moins un deuxième élément mobile et destiné à entraîner un oscillateur antagoniste qui est monté contre ou sur l'arbre intermédiaire (607) et qui peut être entraîné par l'arbre intermédiaire (607). Un décalage de phase Δ différent de zéro et non égal à 180° a lieu entre un mouvement du premier élément mobile et un mouvement du deuxième élément mobile.
EP08873254.0A 2008-03-14 2008-11-18 Machine-outil portative pour outils entraînés en frappe Active EP2265420B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008000687A DE102008000687A1 (de) 2008-03-14 2008-03-14 Handwerkzeugmaschine für schlagend angetriebene Einsatzwerkzeuge
PCT/EP2008/065707 WO2009112100A1 (fr) 2008-03-14 2008-11-18 Machine-outil portative pour outils entraînés en percussion

Publications (2)

Publication Number Publication Date
EP2265420A1 true EP2265420A1 (fr) 2010-12-29
EP2265420B1 EP2265420B1 (fr) 2016-06-29

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EP08873254.0A Active EP2265420B1 (fr) 2008-03-14 2008-11-18 Machine-outil portative pour outils entraînés en frappe

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US (1) US8292002B2 (fr)
EP (1) EP2265420B1 (fr)
CN (1) CN101970182B (fr)
DE (1) DE102008000687A1 (fr)
ES (1) ES2594705T3 (fr)
RU (1) RU2010141587A (fr)
WO (1) WO2009112100A1 (fr)

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US9630307B2 (en) 2012-08-22 2017-04-25 Milwaukee Electric Tool Corporation Rotary hammer
CN104227634B (zh) * 2013-06-09 2017-01-18 南京德朔实业有限公司 冲击类紧固工具及其控制方法
DE102013212554B4 (de) * 2013-06-28 2023-12-14 Robert Bosch Gmbh Handwerkzeugmaschinenantriebsvorrichtung
JP6348337B2 (ja) * 2014-05-16 2018-06-27 株式会社マキタ 往復動式作業工具
CN105465271B (zh) * 2014-06-23 2019-02-22 博世电动工具（中国）有限公司 平衡重机构和电动工具
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Also Published As

Publication number Publication date
CN101970182A (zh) 2011-02-09
US8292002B2 (en) 2012-10-23
DE102008000687A1 (de) 2009-09-17
CN101970182B (zh) 2013-01-16
ES2594705T3 (es) 2016-12-22
RU2010141587A (ru) 2012-04-20
WO2009112100A1 (fr) 2009-09-17
EP2265420B1 (fr) 2016-06-29
US20110005791A1 (en) 2011-01-13

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