EP2265420B1 - Hand-held power tool for impacting driven tool attachments - Google Patents

Description

State of the art

The invention relates to a hand tool according to the preamble of the independent claim 1 and as from DE 87 08 167 U1 known.

Out DE 198 51 888 is already a hand tool for impact driven tools, in particular a drill and / or chipping hammer, known, which has a Luftpolsterschlagwerk with a striking axis and a parallel intermediate shaft, wherein the excitation sleeve of the air cushion impact mechanism driven by means designed as a tumble drive Huberzeugervorrichtung. 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. By repercussions of the air cushion impactor, which are caused inter alia by acting on the exciter sleeve mass forces, vibrations are generated in the power tool. These vibrations are transmitted as vibrations to the housing of the power tool and from there via the handle of the power tool to an operator. To reduce the mass forces that occur, the hand tool of the DE 198 51 888 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 Δ 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 Δ of the counteroscillator of 180 ° to the excursion movement of the exciter sleeve.

In addition to the mass forces, 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.

In addition to the inter alia from the DE 198 51 888 and the DE 10 2007 061 716 Known wobble drives the air cushion impactors are also known Luftpolsterschlagwerke in which the piston of the percussion is done by a crank drive. In particular, crank drives are known in which the piston is connected and driven by means of a connecting rod with a crank disc.

Disclosure of the invention Advantages of the invention

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.

The measures listed in the dependent claims, advantageous refinements and improvements of the main claim features. A compact design of a hand tool according to the invention is achieved by a drive of the at least one additional second Huberzeugungsvorrichtung by the intermediate shaft.

A particularly effective drive of the counter-oscillator is achieved by a phase shift Δ not equal to 90 °. Preferably, the phase shift Δ between the movement of the first lifting element and the movement of the second lifting element is between 190 ° and 260 °. In a particularly preferred embodiment, the phase shift Δ is between 200 ° and 240 °.

A particularly effective embodiment of the counter-oscillator has at least one counter-oscillatory mass. This is guided along a linear or non-linear trajectory, in particular along a straight line or a circular arc. A compact and at the same time effective embodiment of the counter-oscillator has a center of gravity track close to the striking axis. In a particularly preferred manner, the center of gravity path is parallel, preferably coaxial to the impact axis.

In a preferred embodiment, the coupling device is designed as an engaging clutch. In a particularly preferred form, an axial displacement path between an engaged state and an open state is provided.

An embodiment in which a stroke of the lifting element of the second lifting device changes linearly with the displacement path is particularly favorable. Thereby the one amplitude of the movement of the counter-oscillator can be made adjustable in a particularly simple manner.

In another development of the hand tool according to the invention, the second stroke generating device has an additional deflection element. Preferably, a second counteroscillator can be driven by the additional deflecting element. Depending on the relative positioning of the additional articulating member to the lifting of the second lift generating apparatus, the movement of the additional articulating member to a second, in particular the phase shift Δ different phase shift Δ _A.

In a particularly powerful embodiment of a hand tool according to the invention, the first stroke generating device 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. As a result, the connecting rod acts as a first lifting element.

An effective and compact drive of the crank drive is possible by a first bevel gear, which is arranged on the intermediate shaft. The first bevel gear is rotationally driven by the intermediate shaft.

Advantageously, 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.

In a particularly compact design, the crank pin bearing the eccentric pin is arranged on the bevel gear shaft. By a non-rotatable, preferably releasably rotatable connection to the bevel gear, the crank disk is driven.

In a preferred embodiment of a hand tool according to the invention, 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.

In a further preferred embodiment of a hand tool according to the invention, the second stroke generating device is designed as a cam drive. In particular, 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.

In a preferred development, 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.

In a further preferred embodiment of a hand tool according to the invention, 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. By a time behavior deviating from the sinusoidal shape, the movement sequence of the counteroscillator can advantageously be adapted to a time behavior of the vibration-inducing effective forces.

In a further preferred development of the hand tool according to the invention, 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. In a particularly preferred embodiment, the second frequency is in particular about half as large as the first frequency. As a result, an additional degree of freedom for adapting the movement of the counter-oscillator to the time behavior of the vibration-inducing effective forces is advantageously achieved.

Description of the drawings

• Fig. 1a eine Seitenansicht eines ersten nicht erfindungsgemäßen Beispiels
• Fig. 1b eine Schnittansicht durch das Beispiel nach Fig. 1a (Linie T-T)
• Fig. 1c eine Schnittansicht durch das Beispiel I nach Fig. 1c (Linie U-U)
• Fig. 2a bis 2d je eine Darstellung der Huberzeugungsvorrichtungen aus Fig. 1a in unterschiedlichen Phasen der Bewegung
• Fig. 3a und 3b je eine perspektivische Darstellung eines alternativen Gegenschwingers als zweites nicht erfindungsgemäßes Beispiel
• Fig. 4a eine perspektivische Schemaansicht eines dritten nicht erfindungsgemäßen Beispiels
• Fig. 4b eine perspektivische Schemaansicht eines vierten nicht erfindungsgemäßen Beispiels
• Fig. 4c eine perspektivische Schemaansicht eines fünften nicht erfindungsgemäßen Beispiels
• Fig. 4d eine perspektivische Schemaansicht eines sechsten nicht erfindungsgemäßen Beispiels
• Fig 5a eiene schematische Seitenansicht einer Weiterentwicklung des Beispiels aus Fig. 1a als erstes erfindungsgemäßes Ausführungsbeispiel
• Fig. 5b eine schematische Seitenansicht einer anderen Weiterentwicklung des Beispiels aus Fig. 1a als zweites erfindungsgemäßes Ausführungsbeispiel
• Fig. 6 eine schematische Seitenansicht eines siebten nicht erfindungsgemäßen Beispiels
• Fig. 7 eine schematische Seitenansicht eines achten nicht erfindungsgemäßen Beispiels
• Fig. 8a eine schematische Seitenansicht einer Weiterentwicklung des Beispiels aus Fig. 7 als neuntes nicht erfindungsgemäßes Beispiel
• Fig. 8b eine Schnittansicht durch das Beispiel aus Fig. 8a (Linie A-A)
• Fig. 8c eine schematische Darstellung der Phasenbeziehung der Bewegungen der Hubelemente gemäß dem Beispiel aus Fig. 8a
• Fig. 9 eine schematische Seitenansicht eines zehnten nicht erfindungsgemäßen Beispiels
• Fig. 10 eine schematische Seitenansicht eines elften nicht erfindungsgemäßen Beispiels Beschreibung der Beispiele und der erfindungsgemäßen Ausführungsbeispiele

Embodiments of the invention and examples which facilitate the understanding of the invention are illustrated in the drawings and explained in more detail in the following description. Show it:

• Fig. 1a a side view of a first example not according to the invention
• Fig. 1b a sectional view through the example Fig. 1a (Line TT)
• Fig. 1c a sectional view through the example I after Fig. 1c (Line UU)
• Fig. 2a to 2d depending on a representation of the Huberzeugungsvorrichtungen Fig. 1a in different phases of the movement
• Fig. 3a and 3b each a perspective view of an alternative counter-oscillator as a second non-inventive example
• Fig. 4a a perspective schematic view of a third non-inventive example
• Fig. 4b a perspective schematic view of a fourth non-inventive example
• Fig. 4c a perspective schematic view of a fifth example not according to the invention
• Fig. 4d a perspective schematic view of a sixth non-inventive example
• Fig. 5a eiene schematic side view of a further development of the example Fig. 1a as the first embodiment of the invention
• Fig. 5b a schematic side view of another development of the example Fig. 1a as the second embodiment according to the invention
• Fig. 6 a schematic side view of a seventh example not according to the invention
• Fig. 7 a schematic side view of an eighth example not according to the invention
• Fig. 8a a schematic side view of a further development of the example Fig. 7 as the ninth example not according to the invention
• Fig. 8b a sectional view through the example Fig. 8a (Line AA)
• Fig. 8c a schematic representation of the phase relationship of the movements of the lifting elements according to the example Fig. 8a
• Fig. 9 a schematic side view of a tenth example not according to the invention
• Fig. 10 a schematic side view of an eleventh non-inventive example description of the examples and embodiments of the invention

Fig. 1a shows a side view of a portion of a hammer drill 1 as an example of a non-inventive hand tool. 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. In this case, the hammer tube 5 extends along a machine axis 6 away from the intermediate flange 21. By the transmission device 4, a torque provided by the drive motor is transmitted to the hammer tube 5 via the transmission device 4. With regard to the transmission device 4, it is also possible to speak here of a rotary drive of the hammer tube 5.

For the 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. 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. At the hammer tube 5 a Antriebsstirnrad 11 is arranged, which meshes with the output spur gear 10a. The Antriebsstirnrad 11 is operatively connected via an overload safety clutch 12 with the hammer tube 5. 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.

At one end of the hammer tube 5, a tool holder 5a is provided, in which insert tools not shown here can be used. In this case, 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.

In typical hammer drills, such as those from the DE 198 51 888 C1 In addition, the tool holder 5a provides a limited axial mobility of the insert tool along a tool or striking axis defined by a longitudinal extent of the insert tool. Typically, 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.

In addition to the rotary drive of the hammer tube can be driven by means of the transmission device 4 is not shown in detail here Luftpolsterschlagwerk, as for example from the DE 198 51 888 C1 is known. In such Luftpolsterschlagwerken a piston axially displaceably arranged in the hammer tube 5 is set in oscillating axial movement, so that pressure modulations in one of the interior of the hammer tube 5 facing end face of the piston and one of these face facing end face of a likewise axially displaceable hammer tube 5 slidably arranged striking element provided air spring be generated. As a result, the striking element is accelerated along the striking axis 6.

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 transmission device 4 off Fig. 1a comprises a wobble drive 13a designed as first Huberzeugungsvorrichtung 13. The wobble drive 13a is arranged with a first drive sleeve 14 in a drive motor facing region 15 of the intermediate shaft 7 on this. The drive sleeve is hereby preferably rotatably connected to the intermediate shaft 6. On the drive sleeve 14, a first career 16, not shown here, is provided. The track 16 is circular and tilted in an impact axis 6 and the intermediate shaft 7 containing impact plane by an angle W1, which is greater than zero and less than 180 ° and in particular preferably between 45 ° and 135 °. On this first track 16 a not shown here 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 best are the track 16 and the swash bearing 17 in Fig. 1c to recognize. To the swash bearing 17, a swash plate 19 is arranged, which comprises the bearing elements 18 of the swash bearing 17. At the swash plate 19 a not shown here 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.

By a rotational movement of the intermediate shaft 6, 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 drehdrekoppelt of the intermediate shaft 7, but is offset by the positive guidance in a tumbling movement. As a result, 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 Huberzeugungsvorrichtung 13. About the pivot bearing, the oscillating axial movement of the wobble finger 20 is transmitted to the piston of the Luftpolsterschlagwerks.

The transmission device 4 off Fig. 1a further comprises a second lift generating device 23, which in the present example is designed as a second wobble drive 23a. The best is the second wobble drive 23a in Fig. 1c to see. 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. In construction and principal function, the second wobble drive 23a is similar to the first wobble drive 13a already described. In particular, 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. In addition, 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. In this case, 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 in Fig. 1b is shown. By choosing the angle of rotation WV, the second wobble drive 23a adapts to structural boundary conditions in the machine housing 2. In addition, due to the angle of rotation 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 wobble 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 counter-oscillator 31 may have a receiving bearing 32 for low-friction reception of the wobble finger 30, which in Fig. 1c is shown. In the example shown here, the counteroscillator 31 is designed essentially as a counter-oscillatory mass 33. The counter-oscillator mass 33 is designed as a cylindrical mass body. The counteroscillator 31 is arranged in the first example laterally displaceable axially on a sleeve-shaped portion 22 of the intermediate flange 21. 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 it is in Fig. 1b is shown. The guide member 34 is releasably secured in the present example by means of screw on the sleeve-shaped portion 22. The skilled person are also known further fastening options such as clamping, latching, riveting, soldering or welded joints, which can be advantageous here. In addition, 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. However, it may be advantageous to guide the counter-oscillator 31 to other web shapes, in particular along a circular arc or other non-linear path shapes such as parabolic, elliptical or hyperbolic paths. 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 example. In this case, 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. In the present example of the power tool, the orientation angle WO is equal to the angle of rotation WV of the second wobble finger 20. This is, inter alia, in Fig. 1b to recognize. From the relative rotational position and the angles W1 and W2 of the first and second wobble finger 20, 30 results in a phase shift Δ between the oscillating axial movements of the two wobble fingers 20, 30th

To produce a non-rotatable connection different connection techniques come into question.

For a positive connection, the first drive sleeve 14 at its second drive sleeve 24 facing the end with locking elements such. a spur toothing, a toothing on the outer lateral surface or similar formations be provided. 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. In addition to this simple non-positive connection may also be more complex Compounds, for example, include an additional link, such as a connecting sleeve.

In addition to the positive and / or non-positive connections, the person skilled in the art knows of other joining techniques, such as gluing, soldering or welding, which under certain circumstances can be advantageously used.

In a preferred, particularly cost-effective form, the first drive sleeve and the second drive sleeve can also be produced in one piece. In particular, the sintering technique or the metal injection molding (MIM) come into question.

In addition, it may also be advantageous if the rotationally fixed connection is detachable, in particular axially detachable.

During operation of the hammer drill 1 caused by the oscillating axial movements of the piston and / or the striking element and / or the insert tool upon change of the respective state of motion of the piston and / or the striking element and / or the insertion tool due to their mass inertial forces. These inertial forces are referred to below as mass forces. In particular, a change in the state of motion of the piston sometimes generates very high mass forces. In addition to the kinematic variables of the course of motion, such as the momentary accelerations, the mass 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 impact element and the hammer tube and stimulate them to vibrate. Particularly in the case of a sinusoidal movement sequence of the piston, 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. Due to their direct connection to the movement sequence of the piston, the time behavior is synchronous with the state of motion of the piston.

In order to reduce the mass forces of the air cushion impact mechanism described above, 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 Δ of 180 ° advantageously takes place. In addition to a mass of the counter-oscillator mass 33, the stroke of the oscillating axial movement of the Gegenschwingers 31 is a parameter for tuning a reduction effect of the counter-oscillator 31 to the respective air cushion impact mechanism.

As already described above, however, not only inertial forces act to stimulate the vibration in air cushion impact devices. Rather, the so-called air forces can have a significant influence on a vibration excitation. In particular, with increasing impact performance of the rotary hammers with simultaneous mass reduction of the moving components such. of the piston, the air forces assume a dominant importance in the vibration excitation. As already described, 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 ° to a front dead center VT of the oscillating axial movement of the piston. With the counteroscillator 31 can be made and adjusted in a simple manner an optimal choice of the phase shift Δ between the oscillating axial movement of the piston and the oscillating axial movement of the counter-oscillator 31. In real Luftpolsterschlagwerken the adjustment of the phase shift Δ is a temporal behavior of the vibration-inducing effective forces, which are composed of the inertial forces and the air forces, take into account. Preferably, the phase shift Δ will be between 190 ° and 260 °. In a particularly preferred example, the phase shift Δ is between 200 ° and 240 °.

In the Fig. 2a to 2b the sequence of 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 for a case. The figures show different phases of movement. In Fig. 2a is the piston 38 in its forward dead center, which is marked by the mark "impact drive VT 0 °". The counter-oscillator 31 is at this time in a position before its rear dead center, which is designated by the mark "counterweight HT". In Fig. 2b is the piston 38 on its way to its rear dead center (marking "impact drive HT 180 °"), while the counteroscillator 31 has just reached its rear dead center. In Fig. 2c the piston 38 has reached its rear dead center, while the counteroscillator 31 is still striving towards its front dead center (marking "counterweight VT"). Only when, as in Fig. 2d shown, the piston 38 has already continued its way towards the front dead center, the counter-oscillator 31 reaches its front dead center and reverses its direction of movement.

The parameters Gegenschwingermasse, stroke of the counter-oscillator 31 and the phase shift Δ thereby dependent on the respective air cushion impact mechanism Optimization parameters, which can be determined by calculation and / or experimentally.

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. With this coupling element, in particular a second counteroscillator is preferably driven.

The Fig. 3a and 3b show a perspective view of a further development of the hand tool described above as a second example. The reference numerals of the same or equivalent features are increased by 100 in the illustration.

Fig. 3a shows a counter-oscillator 131, which comprises three, connected by a bow-shaped connecting member 135 counter-oscillating masses 133a, 133b, 133c.

In the example shown here, 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.

Analogously to the first example, 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. For this purpose, the sleeve-shaped portion 122 receiving grooves 136a, 136b, 136c, in which the cylindrical counter-oscillator masses 133a, 133b, 133c are received. Analogous to the first example, 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 exemplary embodiment are designed in terms of their masses and their positioning such that the counter-oscillator 131 has a center of gravity M in the center.

This center of gravity M is arranged so that it comes to lie substantially on the striking axis 106. In the case of an oscillating axial movement of the counter-oscillator 131, the center of gravity M describes a center of gravity track which runs essentially parallel, preferably coaxially, to the striking axis 106.

By means of the center of gravity track of the counter-oscillator 131, the counter-oscillator 131 can counteract the vibration-inducing effective forces particularly effectively, since these effective forces are applied directly to components of the hammer drill 101, e.g. the piston of the air cushion impactor, attack, which are arranged in a known manner predominantly cylindrically symmetric about the striking axis 6, so that their centers of gravity also parallel, mostly even coaxial with the axis of impact 6.

In particular, the shape and number of connected counter-oscillator masses 133a, 133b, 133c may differ from the embodiment shown here.

An example of the counter-oscillator 131 as a sleeve-shaped component may also represent an advantageous modification. In addition, modifications of the counter-oscillator 131 shown here can result from deviating splits into deviating half-elements or other sub-elements and / or their mutual connection.

Fig. 4a shows a schematic perspective view of a third example of a gear device 204. The reference numerals of the same or equivalent features are increased by 100 in the illustration. From the transmission device 204 are in Fig. 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, wherein instead of the intermediate shaft 207 only one intermediate shaft axis 207a is shown. The lift generating devices are in this example designed as a first wobble drive 213a and as a second wobble drive 223a. In this case, the first wobble drive 213a is constructed in a manner known from the preceding examples, so that its description is dispensed with.

The third example differs from the previous examples by a modification of the second wobble drive 223a. On the second swash plate 229, two output fingers 237a, 237b are provided. 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. In the example shown, output fingers 237a, 237b are mirror-symmetrical 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. At their end facing away from the swash plate 229, 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. In particular, 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. By this arrangement, the oscillating axial movement of the counter-oscillator 231 is in the beating plane. By this arrangement, no rotation of a stroke of the second wobble drive 223 against the impact plane is necessary. This simplifies the tuning and may be advantageous in terms of space. Contrary to the first two examples, the phase shift Δ 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 example is determined solely by an angular difference of the angles W1 and W2. In its mode of operation, the third example corresponds to the first example, so that reference is made to its description.

In Fig. 4b is a modified transmission device of the third example Fig. 4a shown as a fourth example. The representation is analogous to the representation in FIG Fig. 4a , It will be dealt with here only to a modification, since the basic structure and operation of the third example corresponds.

Contrary to the transmission device of the third example, 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. At its end remote from the swash plate 229, the finger head 240 is mounted, which carries the driven element 239. Also in this transmission device, the counteroscillator 231 is disposed in the beating plane above the piston 238. In its mode of operation, the fourth example corresponds to the first example, so that reference is made to its description.

In Fig. 4c is a combination of the second example Fig. 3a and the third example Fig. 4a presented as a fifth example. The representation is analogous to the representation in FIG Fig. 4a , It will be dealt with here only to a modification, since the basic structure and operation of the third example corresponds.

Contrary to the gear device of the third example, the counter-oscillator 231 of the fifth example is similar in structure to the counter-oscillator 131 known from the second example. The take-up pivot 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 examples three and four is arranged in the beating plane below the finger head 240. Due to its tripartite shape, 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.

In Fig. 4d is a modified transmission device of the third example Fig. 4a as the sixth example. The representation is analogous to the representation in FIG Fig. 4a , It will be dealt with here only to a modification, since the basic structure and operation of the third example corresponds.

In the sixth example, 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.

In a further modification, a guide pin 241 may alternatively be arranged, in particular formed, on the finger head 240 as an alternative to the counter-oscillator 231 of the sixth example or in addition thereto. 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 gate 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 link 242 is shown in FIG Fig. 8b shown.

Fig. 5a shows a schematic side view of a further development of the example Fig. 1a as the first embodiment of the invention. The reference signs of the same or equivalent features are indicated in this illustration by a prefix 8.

Building on the off Fig. 1a The example shows the lift generating devices 813, 823, which are designed as first and second wobble drives 813a, 823a, are shown in a further development. In this embodiment, only the 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. Between the first drive sleeve 814 and the second drive sleeve, a clutch device 873 designed as an engagement clutch 872 is provided. By an axial displacement along a displacement path V, 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.

In the embodiment shown here, 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. For this purpose, the counter-coupling elements 875 are brought into engagement with the coupling elements 874 by an axial displacement of the second drive sleeve 824. 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. Thus, for example, frontal or circumferential gears and counter teeth can be used. Also, coupling devices 873 are conceivable with coupling elements such as balls and ball receivers, to name just two known designs. By integrating a coupling device 872, 873, the drive of the counter-oscillator 831 can be made switchable via the second wobble drive 823a. In particular, it is conceivable that in an idle state of the hammer drill 801 of the Drive 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 Fig. 5a as the second embodiment according to the invention. The embodiment of an engagement clutch 872 shown here is in particular already off DE 10 2004 007 046 A1 whose description is explicitly referenced at this point. On the side of the intermediate shaft 807 facing away from the drive motor, an axially displaceable displacement sleeve 876 is arranged, 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. It has for this purpose 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. By positioning in the disengaged state, the displacement wedge 877 is not engaged with its corresponding tapered receiving diameter. As a result, the second drive sleeve 724 is not rotatably connected to the intermediate shaft. In addition, 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. On the other hand, as the displacement wedge displaces, the angle W2 of the raceway 826 inclines more toward the intermediate shaft 807, whereby a stroke of the second wobble finger 830 increases. The cone angle of the other recording diameter limits the maximum possible angle W2max.

• Fig. 6 zeigt eine schematische Seitenansicht eines Bohrhammers 601 mit einer Getriebevorrichtung 604. Die Bezugszeichen gleicher oder gleichwirkender Merkmale werden in dieser Darstellung durch eine vorangestellte 6 gekennzeichnet.

The following examples of a hand tool not according to the invention show examples with alternative, second hoist generating devices:

• Fig. 6 shows a schematic side view of a hammer drill 601 with a gear device 604. The reference numerals of the same or equivalent features are marked in this illustration by a prefixed 6.

The transmission device 604 includes as the first lift generating device 613 a crank drive 613b.

On the, the drive motor side facing the intermediate shaft 607, a first bevel gear 685 is arranged and rotatably driven by the intermediate shaft 607. For this purpose, the first bevel gear 685 rotatably, preferably releasably rotatably connected to the intermediate shaft 607. In the direction of the impact axis 606, a second bevel gear 686 is arranged above the intermediate shaft 607. Here, the second bevel gear 686 is arranged on a bevel gear shaft 687 and preferably rotatably connected thereto. In a preferred form, the bevel gear shaft 387 extends perpendicular to the intermediate shaft 607 in the direction of the striking 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.

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. On 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. For this purpose, a receiving pivot bearing, in which the connecting rod 690 engages, is preferably provided in the piston 638.

In operation, the crank pulley 688 and thus the eccentric pin 689 arranged thereon are set in a rotary motion. In an axial extension along the striking axis 606, the eccentric pin 689 and the connecting rod 690 acting thereon perform an oscillating axial movement, which is transmitted to the piston 638.

In particular, 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. Also, the second bevel gear 386 and the crank pulley 688 may be made in one piece. In particular, 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.

The counteroscillator 631 therefore behaves analogously to that Fig. 1a known example.

The adjustment of a phase shift Δ in this embodiment takes place by selecting 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 as the eighth example.

The reference signs of the same or equivalent features are indicated in this illustration by a prefixed 3.

The transmission device 304 includes as the first lift generating device 313 a crank drive 313b already known from the previous example.

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. In this case, the second Huberzeugungsvorrichtung 323, 323b on a cam cylinder 343, which is arranged in the drive motor remote area 309 of the intermediate shaft 307 on this and preferably rotatably connected thereto. On an outer circumferential surface of the cam cylinder 343, a trajectory 344 is provided. The trajectory has an axial course 345 which varies in the circumferential direction of the curve cylinder 343. In particular, 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.

In the example shown here, the trajectory 344 is groove-shaped in the outer circumferential surface of the cam cylinder 343. However, it is also possible to produce a trajectory 344 by means of suitable formations or formations. Furthermore, it is conceivable that for producing the trajectory 344 of the cam cylinder is coated or wrapped with a just made, a curve profile bearing sleeve member. In this case, for example, 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. In this case, 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.

In operation, the cam cylinder 343 is rotationally driven by the intermediate shaft 307. As a result, 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 setting of a phase shift Δ in this example 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 lifting device 313, 313b.

Typically, the axial movement of the guide member 346 repeats after a full revolution of the cam cylinder 343. The counter-oscillator 331 therefore behaves analogously to that Fig. 1a known example.

However, trajectories 344 are also possible which deviate from this relationship. In particular, repetition of the axial movement may be an integer multiple or an integral proportion of one revolution of the cam cylinder 343. This is in the Fig. 8a to 8c an example is made, to which reference is made at this point.

Due to the oscillating axial movement of the guide element 346, the counteroscillator 331 is set into oscillating axial movements. By a suitable choice of the angle W3 and / or the Axialverlaufs 345 of the trajectory 344, a desired phase shift Δ between the first wobble finger 320 and the guide member 346 is set as a lifting element 330a of the second Huberzeugungsvorrichtung 323, 323b become. As a result, the counteroscillator 331 acts analogously to the preceding examples.

By the selectability of Axialverlaufs 345 of the trajectory 344 is in this example of a transmission device 304, an additional degree of freedom for the optimal adjustment of the oscillating axial movement of the counter-oscillator to the timing of the vibration-inducing effective forces ready, which can be used advantageously for further vibration reduction. In particular, by selecting the trajectory 344 or the Axialverlaufs 345 deviating motion profile of the counter-oscillator 331 deviating from a sinusoidal shape typical for pendulum movements.

Fig. 8a shows a schematic side view of a further development of the example Fig. 7 as ninth example.

The reference numerals of the same or equivalent features are indicated in this illustration by a prefix 9.

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.

In this case, the second Huberzeugungsvorrichtung 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. On an outer circumferential surface of the cam cylinder 943, a trajectory 944 is provided. The trajectory 944 is executed in the example shown here as an opposite, intersecting spiral path 981. In particular, the spiral track 981 has two revolutions in each direction. The provided on the counter-oscillator mass 933 guide member 946 is designed here as a rail slider 982, which is best in Fig. 8b can be seen. 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. In operation, the cam cylinder 943 rotates at a same speed as the intermediate shaft 907. The spiral path 981 causes the axial deflection of the counteroscillator 931 via the rail slide 982 to take place at a reduced speed. In other words, the oscillating axial movement of the counter-oscillator-driving second lifting element 30a takes place at a second, here lower frequency F2, relative to a first frequency F1 of the oscillating axial movement of the first wobble finger 920. Fig. 8c shows to a schematic stroke-time diagram for the deflections of the piston and counter-oscillator, as it corresponds to this example.

As already indicated in the description of some previous examples, further possibilities for influencing a second frequency F2 of the second lift generating device 923 may result. In addition, the person skilled in the art is familiar with further possibilities for modifying the examples shown here.

Fig. 9 shows a schematic side view of a hammer drill 401 with a gear device 404 as a tenth example.

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 front cam drive 423c has a cam plate 450 carrying a surface profile 449, which is perpendicular to the intermediate shaft 307 and oriented away from the drive motor. One can therefore also speak of a cam drive 423c. 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. In this case, 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.

In operation, the counter-oscillator mass 433 is pressed against the surface profile 449 by this bias. In this case, 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 disk 450 is driven to rotate by the intermediate shaft 407, the counterweight 433 is deflected axially via the contact element 453 as a lifting element 430a of the second lift generating device 423, 423c. Due to the axial course 451 recurring with one revolution of the cam disk 450, the counteroscillator 431 performs an oscillating axial movement. The setting of a phase shift Δ is done in this example by selecting a rotational position of the cam profile 449, taking into account the circumferential angle WE of the eccentric pin 489 of the first lift generating device 413, 413b.

In this case, 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. In particular, deviating motion profiles can be generated by a sinusoidal form that is typical for oscillating movements. Also, depending on the cam profile 450, a multiple deflection per revolution of the cam plate 450 is possible.

Fig. 10 shows a schematic side view of a hammer drill 501 with a gear device 504 as an eleventh example.

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. On the side remote from the drive motor part 509 of the intermediate shaft 507, a drive pulley 556 is arranged and rotatably driven by the intermediate shaft 507. In the present example, the first bevel gear 585 is formed as a drive pulley 556. In a radially outer region, a rotary joint 557 is provided on an end face of the drive pulley 556. About this pivot 557, a push rod 558 is operatively connected at one end to the drive pulley 556. At the other end of the push rod 558, 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. Preferably, 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.

In operation, 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 examples.

The adjustment of a phase shift Δ is made in this example by a circumferential angle WU below the first pivot 557 on the drive pulley 556, as well as the relative position of the second pivot 559 to the first pivot 557. In this case, the circumferential angle WE of the eccentric pin 589 on the Crankshaft 588 of the first lift generating device 513, 513b to consider.

Modifications to this example of a transmission device result inter alia in the design of the hinges 557, 559 and / or the push rod 558. Furthermore, the design of the counter-oscillator mass 533 can be diverse.

In a particularly preferred further development, 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 example. Thus, it may be advantageous with the adjustment of the rotational position of the track of the second drive sleeve 24 and thus the phase shift Δ allows the oscillating movement of the lifting element 20a of the first Huberzeugungsvorrichtung 13. For this purpose, 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. For this purpose, the person skilled in the art will be familiar with further ways of implementing such an adjustment device. In particular, such an adjustment can also be used advantageously in the second Huberzeugungsvorrichtungen 23, which are designed as curves, end curves, push rod, crank or rocker arm drive. This is a rotational position the cam cylinder 343, the cam disc 450, the drive pulley 556 or the eccentric pin 663 made variable by means of the adjusting device.

In a further preferred modification of a transmission 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. By this bearing device 8 serves a pivot bearing of the intermediate shaft 7 in the machine housing. 2

Claims (18)

1. Hand-held power tool for predominantly percussively driven tool attachments, in particular hammer drills and/or chisel hammers, having a percussion axis and an intermediate shaft (807) that is parallel to this percussion axis, having a first reciprocation generating device (813) having a reciprocating element (820) for a percussion drive, and having at least one additional second reciprocation generating device (823) arranged at or on the intermediate shaft (807), driven by the latter and having at least one second reciprocating element (820), for driving an opposing vibrator, a phase shift Δ that is different from zero and 180° being provided between a movement of the first reciprocating element (820) and a movement of the at least one second reciprocating element (830),
   characterized in that the second reciprocation generating device (823) has a coupling device (872, 873) with which the second reciprocation generating device (823) can be coupled in a rotationally fixed manner to the intermediate shaft (807).
2. Hand-held power tool according to Claim 1,
   characterized in that the phase shift Δ is not equal to 90°.
3. Hand-held power tool according to one of the preceding claims,
   characterized in that the opposing vibrator has at least one opposing vibrator mass, which is guided along a linear or non-linear movement path, in particular along a straight line or a circular arc.
4. Hand-held power tool according to one of the preceding claims,
   characterized in that the opposing vibrator has a centre of gravity path that is located close to the percussion axis, in particular a centre of gravity path that is oriented parallel, preferably coaxially, to the latter.
5. Hand-held power tool according to Claim 1,
   characterized in that the coupling device (873) is implemented as an engagement clutch (872), in which in particular an axial displacement travel between an engaged state and a disengaged state is provided.
6. Hand-held power tool according to Claim 5,
   characterized in that a reciprocation of the reciprocating element of the second reciprocation generating device (823) changes linearly with the displacement travel.
7. Hand-held power tool according to one of the preceding claims,
   characterized in that the second reciprocation generating device comprises an additional deflection element, by means of which in particular a second opposing vibrator can be driven.
8. Hand-held power tool according to one of the preceding claims,
   characterized in that the first reciprocation generating device is implemented as a first crank drive, which comprises a connecting rod and a crank disc having an eccentric pin, wherein the connecting rod acts as a first reciprocating element.
9. Hand-held power tool according to one of the preceding claims, in particular according to Claim 8,
   characterized in that a first bevel gear is arranged on the intermediate shaft and can be driven in rotation by the intermediate shaft.
10. Hand-held power tool according to Claim 9,
    characterized in that a second bevel gear is provided, which is arranged on a bevel gear shaft that is arranged at right angles to the intermediate shaft and is rotationally fixedly connected to the latter, wherein the second bevel gear can be driven in rotation by the first bevel gear.
11. Hand-held power tool according to Claim 10,
    characterized in that the crank disc carrying the eccentric pin is arranged on the bevel gear shaft and is rotationally fixedly, preferably detachably rotationally fixedly, connected to the bevel gear shaft.
12. Hand-held power tool according to at least one of Claims 8 to 11,
    characterized in that the second reciprocation generating device is implemented as a swash-plate drive, which comprises at least one second drive sleeve carrying a raceway, a swash-plate bearing and a swash-plate disc with swash-plate finger arranged thereon.
13. Hand-held power tool according to at least one of Claims 8 to 11,
    characterized in that the second reciprocation generating device is formed as a cam drive, in particular as a cylindrical cam drive having a curve that is arranged on a circumferential surface and deflects at least one additional reciprocating element, wherein the opposing vibrator is deflected along the curve by the at least one second reciprocating element.
14. Hand-held power tool according to Claim 13,
    characterized in that the cam drive is implemented as a face cam drive or a peg cam drive, which has a surface profile, wherein a pressure element acts on the opposing vibrator such that the opposing vibrator can be pressed against the surface profile and the surface profile can consequently be deflected.
15. Hand-held power tool according to at least one of Claims 8 to 11,
    characterized in that the second reciprocation generating device is implemented as a thrust rod drive, wherein the opposing vibrator is operatively connected to the intermediate shaft via a thrust rod.
16. Hand-held power tool according to one of the preceding claims,
    characterized in that a movement sequence of the at least one additional reciprocating element has a time behaviour that deviates from a sinusoidal form.
17. Hand-held power tool according to one of the preceding claims,
    characterized in that a deflection of the first reciprocating element has a first frequency, and in that a deflection of the second reciprocating element of the at least one additional second reciprocation generating device has a second frequency F2, in particular differing from the first frequency F1, wherein the second frequency is in particular approximately half as high as the first frequency.
18. Hand-held power tool according to one of the preceding claims,
    characterized in that between the first reciprocation generating device and the at least one additional second reciprocation generating device, a bearing device (8) fixed to a machine housing of the hand-held power tool is provided for the rotatable mounting of the intermediate shaft in the machine housing.

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