EP2366494B1 - Manually operated machine tool with a forced rotation eccentric drive - Google Patents

Description

The invention relates to a hand-held machine tool, in particular grinding machine and / or polishing machine, according to the preamble of claim 1.

Such a hand-held machine tool in the form of an eccentric sander goes out WO 02/062526 A1 out.

One out EP 1 491 291 A1 known hand-held machine tool in the form of a Exzentertellerschleifers can be switched between a forced rotation eccentric and a free rotation eccentric mode, ie a total of two different rotation eccentric modes. For example, the forced rotation eccentric mode is suitable for rough grinding, while the free rotation eccentric mode is suitable for finer surfaces.

At the out EP 1 491 291 A1 However, known eccentric grinding machine actually only round grinding pad or polishing plate can be used as polygonal outer contours, such as in so-called triangle grinders or delta cutters, can lead to injury to the operator. In fact, even in the free-rotation eccentric mode, it is not ensured that the tool holder and thus a tool fastened to the tool holder will start to rotate, even if a braking torque is applied to the tool shaft or the tool holder engages to overcome the bearing friction of the tool shaft bearing, so that the rotation is prevented.

It is therefore the object of the present invention to provide a hand-held machine tool in which a freer selection of attachable to the tool holder tools exists and can be conveniently switched and operated.

To solve the problem, a hand-held power tool according to claim 1 is provided.

A basic idea of the invention is that the hand machine tool has integrated rotation angle guide means for keeping the tool shaft rotationally stable in an eccentric only mode in which only eccentric movements are possible, at least within a narrow rotation angle sector. This prevents the tool, which is fastened to the tool holder, from starting to rotate, which, for example in the case of polygonal outer contours or circumferential contours of the tool, can lead to injuries to the operator.

In addition, the field of application of the hand-held machine tool expands decisively, since it is also possible, for example, to use cutting or scraping tools without any problems whose outer contours are intended for chip removal. Namely, the outer contours can not get into rotation, but are held by the rotation angle guide means rotational angle stable, at least within a narrow rotation angle sector, so that the corresponding workpiece machining is possible and also the operator is protected from injury. The inventive hand-power tool thus makes a total of three eccentric modes, namely a pure Exzentermodus (eccentric cam mode only), a forced rotation eccentric mode, which is particularly preferred for coarse grinding, as well as a free rotation eccentric mode in which the rotation of the tool holder or the tool can be limited by further measures, such as by suitable braking means. With the aid of the braking means, it is then also possible to set or fix the rotational speed of the tool holder or of the tool arranged thereon so that a multiplicity of different movement patterns and movement speeds can be realized with the hand-held machine tool according to the invention.

Thus, in the free-rotation eccentric mode, a rotation angle position relative to the machine housing changing rotation of the tool holder can be reduced by a braking torque or even canceled, which exceeds the bearing friction of the tool shaft bearing.

In a possible embodiment of the invention, the tool shaft advantageously strikes the side of rotational angle stops of the rotational angle guide means and is thus prevented from free, complete rotation. For example, the rotation angle guide means may comprise a fork or a frame which engages around the tool shaft laterally and comprises one or more rotational angle stops.

However, in particular linear guides (curved guideways are also possible) with transversely, for example, perpendicular, mutually extending guideways, in particular linear guides.

In principle, however, a linear guide could also interact with one or more rotational angle stops.

The switching means are expediently arranged entirely or at least essentially in the interior of a housing of the hand-held machine tool.

Furthermore, it is expedient if the rotation angle guide means and / or the switching means are arranged substantially in the interior of a transmission housing of the hand-held machine tool.

Of course, a manual operation is advantageous possible.

But it is also possible that the switching means are actuated by a motor, for example by an electric actuator. For example, the actuator could include one or more electromagnets.

For convenient switching and operation of the hand-held machine tool, the following measures contribute:

The switching means comprise an actuating gear with a link operating member having a cooperating with a counter-link backdrop follower or cooperating with a Gegenkulissenfolger backdrop. On the slide actuator so either a slide follower or a backdrop or both can be arranged. It is understood that several scenes or backdrops are conceivable. In an adjustment of the link operating member, such as a rotary adjustment or a linear adjustment, the counter scenery or the Gegenkulissenfolger is also adjusted, so that the switching component of the Exzentergetriebes, which is connected to the counter scenery or the Gegenkulissenfolger is operated. In this case, a preferred embodiment of Invention made such that the link operating member has both a gate follower and a gate, wherein the link follower actuates a first component of the eccentric, while the backdrop is suitable for sliding along a Gegenkulissenfolgers for a second component to be switched or a guide device of the eccentric.

It is understood that alternatively, for example, a direct linear or rotary adjustment of an actuator is possible.

The backdrop and / or the counter scenery has a latching recess for locking with the Gegenkulissenfolger or the scenery follower. Thus, certain switching positions can be determined by the recess. The gate follower thus directly forms a latching member which engages in the latching recess. It will be understood that independent measures can be taken to establish a particular gear position, e.g. corresponding latching receptacles or latching projections, bolts and the like.

The link operating member is suitably rotatably mounted about a rotation axis and actuates the counter-scenery or the Gegenkulissenfolger parallel or obliquely to the axis of rotation linear. Thus, therefore, causes a rotational adjustment of the link actuator a linear adjustment of the counterpart (counter scenery or Gegenkulissenfolger).

The axis of rotation of the link actuator expediently runs parallel or coaxial with the drive axle. Thus, therefore, the switching operations for switching the actuating gear can be parallel or coaxial with the drive axle, which allows a compact structure. Especially preferred It is when the operating gear members are moved linearly parallel or coaxial with the drive axle. This can be used, for example, for a compact design of the eccentric gear. Even an efficient, low-wear switching is so readily possible.

The backdrop or the counter scenery expediently have a Drehendanschlag for the Gegenkulissenfolger or the gate follower.

The slide actuator is suitably rotationally coupled by means of a universal joint with a rotary handle, which is rotatably mounted about an axis of rotation of the link actuating member angular axis. Thus, it is possible, for example, that the rotary handle is disposed at an ergonomic position of the machine housing. The power transmission to the crank actuator or actuating gear is then solved gimbal.

At least one of the modes of the eccentric is preselected with an actuator of the switching means. Thus, for example, an operator can preselect a respective switching position, for example by means of the actuator, e.g. the forced rotation eccentric mode, the free rotation eccentric mode or the only eccentric mode. For the preselection mode is provided that an engagement contour, for example on the actuator, but also on a transmission component or guide component, which is adjustable by the actuator, is spring-loaded in an engagement position with a mating contour. The engagement contour and the mating contour reach automatically when adjusting the eccentric or the guide component in the engaged position, for which the spring load is provided.

The forced rotation guide expediently comprises a rolling body which is rotationally fixed relative to the tool shaft and a rolling base which is rotationally fixed relative to the machine housing and at which the rolling body rolls in the forced rotation eccentric mode. It should be noted that the torsional strength is necessary only for the forced rotation eccentric mode, outside the same but can also be canceled.

Particularly preferably, the rolling element comprises a planetary gear, while the rolling base is formed by a ring gear or vice versa. The planet gear and the ring gear are engaged in the forced rotation eccentric mode. The outside diameter of the Planet wheel is of course smaller than the inner diameter of the ring gear.

With the switching means of the eccentric gear according to the invention is advantageously a relative position of the rolling base and the rolling element to each other adjustable. But also a non-rotatable connection between the rolling elements and the tool shaft or a rotationally fixed connection between the machine housing and Wälzbasis can be produced or solvable with the switching means. It is particularly preferred if the switching means can adjust a relative position of the ring gear relative to the planet gear, wherein the planetary gear, so the rolling elements, is arranged on the tool shaft.

The rolling element and the rolling base are in the forced rotation eccentric mode, for example by means of a toothing, friction surfaces or the like, in positive or frictional engagement with each other. It is understood that a partially positive and partially frictional engagement conceivable.

Preferably, the hand machine tool has brake means for decelerating the rotation of the tool shaft about the drive axis in the free rotation eccentric mode.

The drive shaft expediently comprises a hollow shaft in which the tool shaft is accommodated eccentrically.

Nachzutragen it is still that the drive shaft and the tool shaft may indeed have an elongated, rod-like shape. But it is also possible that the tool shaft and / or the drive shaft build relatively short, so therefore can include a compact, including disc-like shaft body.

Advantageously, it is provided that the eccentric gear has switching means for switching the rotational angle guide means between the eccentric cam mode and the rotary eccentric mode, that a sole eccentric tool mountable on the tool holder and unsuitable for a rotation eccentric mode has a locking contour, and the switching means have a locking body adjustable between a first position and a second position for abutment against the blocking contour, so that when the eccentric tool is mounted, switching into the rotation eccentric mode is blocked and / or assembly of the eccentric tool only the tool holder is blocked when the switching means are adjusted in the rotation eccentric mode.

The locking body is in the first position towards the tool holder, i. advanced in the assembly path of the locking contour or the end position or stands there.

In the second position, the blocking body is moved away from the end position or the mounting path of the locking contour of the tool.

Although it is possible that the blocking body by means of the switching means or other, for example, manual adjustment, in the first or second position is adjustable. However, it is preferred if the blocking body is spring-loaded in the first or second position.

The switching means expediently have an actuator acting on a transmission component of the eccentric drive for switching between the eccentric only mode and the rotary eccentric mode, for example the forced rotation eccentric mode and / or the free rotation eccentric mode.

The locking body can now be firmly connected to the actuator of the switching means or form a part of the actuator.

Preferably, however, an adjusting mechanism is arranged between the locking body and the actuating member, for example, a sliding gear, a bevel gear or a deflection gear. It is understood that even gears, belt or cable transmission or the like other gearboxes are possible.

In the embodiment described in more detail is an inclined surface gear, which comprises a locking body arranged on the blocking body oblique surface and arranged on the actuating member actuator oblique surface. It is understood that even a single bevel could be sufficient. The actuator is expediently rotatable, while the locking body is mounted linearly. In a rotational adjustment of the actuator expediently causes a linear adjustment of the locking body.

When the locking body is in the first position and abuts against the locking contour, it expediently forms a stop for the actuating member such that an adjustment from the eccentric-only mode in the rotation eccentric mode is not possible.

A blocking body guide for guiding the locking body with respect to the machine housing between the first and second position is expediently designed as a linear guide. It is understood that the locking body could also be mounted rotatably or rotatably and slide-movable.

Figur 1

eine erfindungsgemäße Hand-Werkzeugmaschine perspektivisch schräg von oben mit geöffnetem Gehäuse,

Figur 2

eine Schnittdarstellung der Hand-Werkzeugmaschine gemäß Figur 1 entsprechend einer Schnittlinie A-A,

Figur 3

eine perspektivische Schrägansicht von oben eines Exzentergetriebes der Hand-Werkzeugmaschine gemäß Figur 1, das in

Figur 4

teilweise geschnitten dargestellt ist,

Figur 5

einen Kulissenring mit einem Hohlrad für das Exzentergetriebe gemäß Figuren 3, 4

Figur 6

Drehwinkel-Führungsmittel des Exzentergetriebes gemäß Figur 3 in perspektivischer Schrägansicht,

Figur 7a

ein Führungselement der Drehwinkel-Führungsmittel gemäß Figur 6, zur Zusammenwirkung mit einem in

Figur 7b

dargestellten weiteren Führungselement, das an einem Planetenrad des Exzentergetriebes gemäß Figur 3 angeordnet ist,

Figur 8

eine perspektivische Teilansicht schräg von vorn der Hand-Werkzeugmaschine gemäß Figur 1 jedoch mit einem anderen Werkzeug,

Figur 9

eine Schnittansicht entsprechend Figur 8 entlang einer Schnittlinie B-B in Figur 8,

Figur 10a

das Exzentergetriebe gemäß Figur 3 von hinten mit einer Sperre in einer ersten Stellung,

Figur 10b

das Exzentergetriebe entsprechend Figur 10a, jedoch mit dem in Figur 8 dargestellten Werkzeug bestückt sowie mit der Sperre in einer zweiten Stellung,

Figur 11

eine perspektivische Schrägansicht von unten der Hand-Werkzeugmaschine gemäß Figur 1 jedoch ohne Werkzeug, das in Gestalt eines Schleiftellers in

Figur 12

von schräg oben dargestellt ist,

Figur 13a

das Werkzeug gemäß Figur 8 von schräg oben, das in

Figur 13b

von schräg unten dargestellt ist.

Hereinafter, an embodiment of the invention will be explained with reference to the drawing. Show it:

FIG. 1

a hand-held machine tool according to the invention obliquely from above with the housing open,

FIG. 2

a sectional view of the hand-held machine tool according to FIG. 1 according to a section line AA,

FIG. 3

a perspective oblique view from above of an eccentric of the hand-held machine tool according to FIG. 1 , this in

FIG. 4

partially shown in section,

FIG. 5

a sliding ring with a ring gear for the eccentric according to FIGS. 3, 4

FIG. 6

Rotation angle guide means of the eccentric gear according to FIG. 3 in perspective oblique view,

Figure 7a

a guide element of the rotation angle guide means according to FIG. 6 to interact with an in

FIG. 7b

shown further guide element, according to a planetary gear of the eccentric FIG. 3 is arranged

FIG. 8

a partial perspective view obliquely from the front of the hand-held machine tool according to FIG. 1 however with another tool,

FIG. 9

a sectional view accordingly FIG. 8 along a section line BB in FIG. 8 .

FIG. 10a

the eccentric gear according to FIG. 3 from behind with a lock in a first position,

FIG. 10b

the eccentric gear accordingly FIG. 10a , but with the in FIG. 8 equipped tool shown and with the lock in a second position,

FIG. 11

an oblique perspective view from below of the hand-held machine tool according to FIG. 1 However, without tools, in the form of a sanding plate in

FIG. 12

shown diagonally from above,

FIG. 13a

the tool according to FIG. 8 from diagonally above, that in

FIG. 13b

is shown obliquely from below.

The drawing shows a hand machine tool 10, which in the present case is designed as a grinding machine or polishing machine, depending on which tool is used. The hand machine tool 10 can be operated in an eccentric mode.

Of course, the innovative concepts described in detail below can also be used in other types of hand-held machine tools, such as, for example, in Schab machine tools, in which an oscillating reciprocating motion, even eccentric type, is appropriate. The tool could also be a cutting tool.

A machine housing 11 of the hand-held machine tool 10 comprises a tool area 12 and a motor area 13, which are connected to one another by a handle 14 and a connecting section 15. The machine housing 11 is for example are formed by two shell-like side parts 16a, 16b which delimit a receiving space for components of the hand-held power tool 10 to be protected.

The motor portion 13 and the tool portion 12 as well as the handle 14 and the connecting portion 15 have a substantially cylindrical shape, wherein the end faces of the cylinder defined by the handle 14 and the connecting portion 15 on the peripheral sides defined by the tool portion 12 and the motor portion 13 Adjacent cylinder.

In the motor region 13, a drive motor 17 is housed, in this case an electric motor, wherein pneumatic motors or other drive principles are also conceivable. The drive motor 17 is supplied with electrical energy via an electrical connection 18. The hand-held power tool 10 is therefore a wired electrical machine, whereby a battery operation, thus a wireless variant is well within the scope of the invention. The electrical connection 18 is arranged on a rear side 19 of the machine housing and is preferably suitable for fastening a connection cable by means of a known quick connection technology.

The tool region 12 forms a front side 20 of the machine housing 11. The connecting section 15 extends on a lower side 21, the handle 14 on an upper side 22 of the machine housing 11.

On the underside 21, a tool holder 23 for holding and receiving exemplified tools 24 or 25 is further arranged. The tool holder 23 is arranged on the front side of a tool shaft 26.

The tool holder 23 advantageously has a bayonet 118, wherein also other fastening means, e.g. Clamp or screw means are possible.

An eccentric weight 117 is advantageously arranged on the tool holder 23. The eccentric weight 117 projects as a segment of a circle segment from the drive part 33 downwards in the direction of the tool holder 23.

Although it would be conceivable in principle to drive the tool shaft 26 directly, so that the tool 24 or 25 makes a purely rotational movement. In the hand machine tool 10, however, an eccentric 27 is provided, with the eccentric movements of the tool shaft 26 can be generated. The eccentric 27 is disposed in the tool area 12 of the machine housing 11. It would be possible, for example, instead of the eccentric 27, for example, also. to accommodate a manual transmission with multiple speed levels in the tool area 12. The eccentric 27 forms, so to speak, a main gear of the hand-held power tool 10th

Since the tool region 12 and the motor region 13 are arranged on mutually opposite regions of the handle 14 and the connecting portion 15, a distance between the drive motor 17 and the driven eccentric 27 and the tool holder 23 with respect to a longitudinal axis 28 of the machine housing 11 is present. This distance is bridged by a transmission gear 29, which rotatably couples the drive motor 17 with the eccentric 27. The transmission gear 29 has a transmission member 30 in which it is present and a transmission belt 31. Conceivable, however, would be a transmission by means of a toothed gear or a transmission rod, for example, a propeller shaft.

The transmission belt 31 couples a driven part 32 of the drive motor 17 with a drive part 33 of the eccentric 27, thus a drive part for the tool holder 23. Matching the transmission belt 31 is the output member 32 and the drive member 33 to pulleys or pulleys to the Transmission belt 31 is looped. At the output member 32 and the drive member 33 edges 34 are advantageously provided, between which the transmission belt 31 finds secure hold. In addition, a corrugation 35 on the components 31, 32 and / or 33 is also expedient, so that reliable operation and reliable hold of the transmission belt 31 on the output part 32 and / or drive part 33 are ensured as well.

The drive member 33 rotates about a drive axis 36, to which a tool axis 37 of the tool holder 23 is eccentric by an eccentric 38, but parallel. A motor shaft 39 of the drive motor 17 rotates about a motor shaft 40. The output member 32 is rotatably mounted on the motor shaft 39.

The drive shaft 36 and the motor shaft 40 each extend from the top 22 to the bottom 21 of the machine housing 11. In the present case, the arrangement is such that the motor shaft 40 and the drive shaft 36 are parallel to each other, whereby inclination are conceivable. For this example, be angular gear possible. Furthermore, it does not necessarily have to be such that the tool axis 37 and the drive axle 36 are parallel to one another, even if this is preferred.

The motor shaft 40 and the drive axle 36 in the present case extend perpendicular to a working surface 41 of the tool 24 or 25, thus also perpendicular to a workpiece surface to be machined.

The remote arrangement of drive motor 17 and eccentric 27 in the hand-held power tool 10 allows ergonomically advantageous housing various components, such as a controller 42 which is disposed in the interior of the handle 14. From the controller 42, a board is exemplified. Coupled directly to the control 42 is an adjusting element 43, for example an adjusting element for setting a rotational speed.

At the front, the tool area 12 facing end portion of the handle 14, namely at a head portion 44 of the tool area 12, a motor switch 45 is arranged, which is ergonomically placed. Namely, an operator can comfortably grasp the handle 14 by grasping around the handle 14 through a through-hole 46 provided between the handle 14 and the connecting portion 15. The motor switch 45 can then be conveniently pressed with, for example, the thumb to turn the drive motor 17 on and off.

Towards the head section 44, the handle extends somewhat obliquely downwards, that is to say in the direction of the tool holder 23, so that a kind of waisting is provided at the transitional area between the tool region 12 and the handle 14, which is ergonomically advantageous. On the opposite side, that is to the motor region 13, the handle is slightly enlarged, which allows a comfortable palm rest.

Also, the connecting portion 15 is not only used for stiffening and reinforcing purposes, but also contains functional elements, namely, for example, a receiving space for the transmission member 30. The connecting portion 15 has a relatively large transverse width, which also benefits the stability of the machine housing 11. At the same time a broad receiving space for the transmission belt 31 is created so that its dreams 47 from the output part 32 to the drive part 33 and back again can have a relatively large distance from each other. The strands 47 run close to side walls 48 of the connecting portion 15th

Furthermore, a dust discharge channel 49 is arranged in the connecting section 15. The dust removal channel 49 extends in a channel housing 50, which encapsulates the dust removal channel 49, as far as it runs in the interior of the machine housing 11. Thus dust-laden air does not enter the interior of the machine housing 11. The dust removal channel 49 extends from the tool holder 23 to a configured for connection of a suction hose discharge port 51 on the rear side 19 of the machine housing 11, that is also on the output member 32 over. The channel housing 50 accordingly has an adapted outer contour, expediently also to provide movement space for the transmission member 30.

In particular with regard to grinding machines, but also with other manual machine tools, the space concept of the hand-held machine tool 10 also enables optimum cooling of the components which heat up during operation, also with regard to ergonomic handling.

Cooling air can in fact through inlet openings 52 at side portions of a peripheral wall 53 of the tool area 12 and on the side walls 48, close to the tool area 12 in the Machine housing 11 flow. The cooling air then flows on the one hand on the eccentric 27, so that this is cooled, wherein the cooling air flowing there is introduced in particular in the connecting portion 15, on the other hand through the handle 14 through, where it cools the controller 42 and also for a pleasant Temperature of the handle 14 provides for the operator to then pass the drive motor 17 before the cooling air leaves the machine housing 11 through discharge openings 54 on the rear side 19. Thus, therefore, all the essential components in the interior of the machine housing 11 are cooled.

A fan 55, which is arranged on the motor shaft 39, generates the cooling air flow. It goes without saying that a fan wheel can also be provided for generating a dust removal air stream, for example where a speed sensor 56 is arranged on the motor shaft 39. The fan 55 is arranged close to the outflow openings 54, namely in the vicinity of the underside 21. Thus, therefore, the fan 55 and the output member 32 are positioned side by side. It is understood that even at the top 22 of the machine housing 11, for example, a fan wheel would be conceivable. Furthermore, a fan wheel could also be provided, for example, on a transmission designed differently from the eccentric gear 27 in order to generate the air flow in the tool area 12.

The drive motor 17, which heats up relatively strongly during operation, is arranged away from the handle 14 in the space concept of the hand-held power tool 10, which represents a clear difference from conventional grinding machines in which the motor is arranged in the handle. Furthermore, the machine housing 11 is optimally balanced, so to speak, since the drive motor 17 can be counterweight for the eccentric gear.

Several innovative concepts are realized in the eccentric gear 27, which are advantageous in connection with the drive concept of the hand-held power tool 10, but can of course also be used when a drive motor is arranged, for example, directly next to the eccentric gear 27 and this directly drives, eg via an angle gear (bevel gear, etc.).

The drive member 33 is rotatably connected to a drive shaft 57, for example in one piece with this. The drive shaft 57 is mounted by means of drive shaft bearings 58, 59 rotatably about the drive shaft 36 to a transmission housing 60 of the eccentric 27. The drive shaft bearings 58, 59 are arranged, for example, in bearing receivers, in particular stages, of the transmission housing 60. In the present case, the drive shaft bearings 58, 59 are ball bearings, although other types of rolling bearings or slide bearings are also conceivable. The drive shaft 57 rotates centrically to the transmission housing 60th

The drive shaft 57 is configured here as a hollow shaft which receives the tool shaft 26. A middle, rod-like portion of the tool shaft 26 penetrates a central portion of the drive shaft 57, which is there, as it were, fitted. In this central region of the drive shaft 57 and the two bearings 58, 59 are arranged. The bearings 58, 59 are located between tool shaft bearings 61, 62, which are arranged at opposite end portions of the drive shaft 57, for example, on a bearing receiving part 63 on the tool holder 23 opposite side and in an interior of the drive part 33. Thus, so supports the order the eccentricity 38 eccentric tool shaft 26 at each other far away, each other opposite end portions of the drive shaft 57, which creates a high load capacity.

The bearing receiving part 63 is rotatably connected to the drive shaft 57, could also be integral therewith. A projection of the bearing receiving part 63, which is located in the interior of the drive shaft 57, could also serve for transverse support (transverse to the axes 36, 37), but this is not the case here, since the support on the two tool shaft bearings 61, 62 takes place.

The gear housing 60 is now rotatably received in the machine housing 11, for which suitable form-fitting contours, screws and the like are provided. A floating storage by means of rubber rings or other elastic elements, for example, is possible.

The tool shaft bearings 61, 62 form a tool shaft bearing. If the drive shaft 57 is now driven by the drive part 33, a bearing friction of the tool shaft bearings 61, 62 ensures that the tool shaft 26 is also taken to this rotation about the drive axle 36 and thus performs a rotational movement. When no braking torque acts on the tool shaft 26, the tool shaft 26 rotates at the same speed as the drive shaft 57. Such an operation mode of the eccentric gear 27 is hereinafter referred to as the free rotation eccentric mode F.

The tool holder 23 can also be placed in a forced rotation, whereby it undergoes so-called hypercycloidal movements, ie on the one hand a rotation about the drive shaft 36, on the other hand a superimposed eccentric caused by the eccentricity 38. This mode is called Zwangsrotation eccentric Z. so that means the hand machine tool with the eccentric modes F and Z has a total of two rotational eccentric modes F, Z.

For the forced rotation eccentric mode Z, a forcible rotation guide 64 is provided which includes a rolling element 65 and a rolling base 66. At least in the forced rotation eccentric mode Z of the rolling elements 65 with the tool shaft 26 is rotationally fixed and the rolling base 66 with the gear housing 60 rotatably, thus also the machine housing 11, rotatably. This is emphasized because by canceling one or both of the aforementioned rotational strengths, the forced rotation could be canceled, which is not the case in the embodiment. Rather, the rolling element 65 and the rolling base 66 are displaced relative to each other so that they are engaged in the forced rotation eccentric mode Z to effect the forced rotation. In the other rotation eccentric mode, namely the free rotation eccentric mode F, the rolling element 65 and the rolling base 66 are separated from each other.

In the present case, the rolling element 65 is configured as a planetary gear, which is arranged in the interior of a rolling gear 66 forming the ring gear. In the forced rotation eccentric mode Z, there is a form fit between these two components, so that the rolling element 65 with its toothing on the outer circumference meshes with the toothing on the inner circumference of the rolling base 66.

In addition, however, an only eccentric mode N is possible in which the tool 24 or 25 does not rotate about the drive axis 36, but only performs the eccentric 38 caused by the eccentric movements when the drive motor 17 is running. In this eccentric cam mode N, rotational angle guide means 67 are engaged with the tool shaft 26.

The rotation angle guide means 67 comprise a first linear guide 68, and a second linear guide 69, which are at right angles to each other at an angle, in the present case. A guide axis q of the first linear guide 68 extends, for example transversely to the longitudinal axis 28, a guide axis 1 of the second linear guide 69 parallel to the longitudinal axis 28, wherein of course other orientations of the first and second linear guides 68, 69 relative to each other and / or the machine housing 11 in principle also possible would.

The linear guides 68, 69 include first and second guide members 70, 71 and a guide base 72 rotatable relative to the gear housing 60. The second guide member 71 is sandwiched between the first guide member 70 and the guide base 72. The second guide element 71 forms an intermediate layer. The second guide element 71 is designed in the manner of a carriage, which is mounted so as to be bidirectionally movable between the first guide element 70 and the guide base 72, namely along the guide axes 1 and q of the two linear guides 68, 69.

The guide base 72 is rotatable with respect to the gear housing 60 except for a buffering, but linearly displaceable. For this purpose, a holder 73 has e.g. Linear guide bushings, grooves or the like comprehensive sliding guides 74, in which guide projections 75 of the guide base 72 are mounted so as to move along a control axis, for example parallel to the drive axis 36th

A coupling by means of a rotary adjustment or other angular positions of the adjusting axis to the drive shaft 36 would also be possible depending on the type of actuation of the rotation angle guide means for engaging and disengaging with the tool shaft 26.

The guide projections 75 protrude from the guide base 72 in the direction of the holder 73. This in turn is rotatably held in a receptacle 76. For example, by adjusting the guide base 72 relative to the bracket 73 by means of the slide guides 74, it is possible to bring the rotation angle guide means 67 into engagement and disengagement with the tool shaft 26 to switch to the only eccentric mode N or back out of it into one of the rotation eccentric modes F or Z.

A spring 78 loads the rotation angle guide means 67 in the coupling position. The spring 78 is supported on the one hand on the holder 73 and on the other hand on the guide base 72 from. The spring 78 is further penetrated by a pin 79 which also penetrates into a mating bore on the guide base 72 to provide further stabilization thereof.

The holder 73 is configured as an elastic holder. It comprises for example a block-like buffer 73b made of rubber or an elastic plastic, in which the sliding guides 74 are accommodated. The two sliding guides 74 are radially away from the drive axle 36, along which the central pin 79 extends. Thus, at a corresponding rotational stress around the drive shaft 36, a torque acts on the sliding guides 74. However, the sliding guides 74 can rotate slightly about the drive axis 36, namely around a buffer path 80. The buffer path 80 is advantageously limited by rotational stops 81. When the guide projections 75 are designed around the buffer path 80 at the maximum, they strike the rotation stops 81. However, this operating state is extremely rare, so that by the designed as an elastic buffer holder 73 a low-vibration operation of the hand-held power tool 10 is possible.

It is understood that the elastic buffering and / or the buffer travel limiting rotation stops are optional in connection with intersecting linear guides of rotational angle guide means in an eccentric hand machine tool, and in themselves constitute an independent invention.

Already by the play arm linearly sliding guide elements 70, 71 and the guide base 72 a low-vibration, precise operation is possible. The corresponding guides are in the present case configured as sliding guides, it being expedient to use matching metal materials or plastics, e.g. Brass on steel or the like, so that the rotation angle guide means 67 operate with low friction, which reduces the noise and is also energy efficient.

If rotation about the drive axis 36 were desired around a rotation angle sector, the linear guides 68 and / or 69 could have some play transverse to their axes q and 1.

In the eccentric only mode N, the first guide member 70, which is formed here by a projection 82 on the rolling body 65, in engagement with a guide receptacle 83 on the second guide member 71, so to speak, the intermediate element.

From the second guide element 71 is upwards, ie in the direction of the guide base 72, side guides 160 from. Of the side guides 160, which are configured as walls (frame-like Embodiments or hooks are also possible) stand inwardly, ie in the direction of the guide base 72, retaining projections 161, so that the guide base 72 can be guided from the side under the guide projections 163 therethrough. The retaining projections 161 hold the second guide element 71 on the guide base 72, in particular when disengaging from the tool shaft 26.

As a further expedient measure can be provided that the rotation angle guide means 67 are balanced so to speak. For example, a balance recess 62 is arranged on the projection 82. Further guidance measures can be taken so that, for example, a guide projection 163 is arranged in the guide receptacle 83 and engages in the direction of a guide recess 164 on the associated projection 82 of the rolling element 65.

The eccentric 27 is easily switchable. A one-hand operation for switching between the operating modes F, Z and N is possible. There are not several controls or controls required, but it is sufficient a single handle 84, which is designed here as a rotary handle. Schiebebetätigungskonzepte, bevel gear or the like would be optional in other embodiments, but are not realized in the hand-held power tool 10. The shift handle 84 is disposed on the top 22 of the machine housing 11 so that it can be easily gripped. Conveniently, the arrangement of the switching handle 84 on the head portion 44 of the tool area 12. The switching handle 84 are provided appropriately marks that represent the operating modes F, N and Z symbolically, so that an operator at the respective rotational position of the control handle 84 directly set respectively recognize the selected operating mode. It is preferably provided that the motor switch 45 blocks an adjustment of the control handle 84 when it turns on the drive motor 17. It is also possible that the switching handle 84 blocks the motor switch 45 when no unique switching position is set. Between a drive switch and a gearshift switch of a hand-held machine tool according to the invention, a locking of the gearshift switch by the engine switch and / or vice versa in at least one position of the engine switch or the gearshift switch is expediently provided.

The switching handle 84 forms a component of switching means 85 for switching the eccentric gear 27. The switching handle 84 acts via a coupling joint, which in the present case is designed as a universal joint 86 (other joints would be conceivable) on an actuating member 87, which in turn is coupled with a link operating member 88 in turn. in the present case is rotationally coupled. The actuator 87 is configured as a kind of cap for the transmission. In any case, the actuating member 87 is rotatably mounted on a front of the cover 77 projecting portion of the bolt 79. Conveniently, a projection 89 of the lid 77 engages in a receptacle 90 of the actuating member 87, so that in this respect a rotary guide is realized. In any case, the actuator 87 can rotate on the cover 77, in the embodiment about the drive shaft 36, wherein an axial offset would be optional.

The slide actuator 88 includes an annular body 91 which is also rotatably mounted about the drive axle 36 within the transmission housing 60. From the annular body 91 are pivot bearing projections 92 radially outward from which engage in a rotary guide 93 of the gear housing 60. The rotary guide 93 is designed for example as an annular groove. The Rotary guide 93 is formed for example between the lid 77 and the gear housing 60, which facilitates the assembly of the slide actuator 88.

The switching handle 84 rotates about an axis which is angled relative to the drive axis 36, wherein the angular offset between the axis of rotation of the control handle 84 and the axis of rotation of the actuating member 87 actuated by it is bridged by the coupling joint designed as a universal joint 86.

Of the annular body 91 are driving projections 94, for example three, frontally from, i. The driving projections 94 penetrate the cover 77. This has this ring grooves 95, for example, on the outer circumference of the receptacle 90. The driving projections 94 engage in driving recesses 96 of the actuator 87 rotatably (a rotational game would be conceivable), so that the actuator 87 entrains the slide actuator 88 in a rotary actuator.

By a rotary actuation of the actuator 87 so the slide actuator 88 can drehverstellen to one hand to adjust the position of the rotation angle guide means 67 relative to the tool shaft 26 (switching between the modes F and N) and on the other hand, the relative position of the rolling element 66 to the rolling element 65 (switching between the operating modes Z and F). In this case, the switching sequence is such that the eccentric 27 passes from the forced rotation eccentric Z mode in the free rotation eccentric mode F and from there into the only eccentric mode N and vice versa (N - F - Z).

When switching from the free rotation eccentric mode F to the eccentric cam mode N only, counter track followers 97 slide along a gate 98 of the gate actuator 88 from a lower portion (closer to the first guide member 70) to a higher portion 100 (further away from the first guide member) 70), so that thereby the second guide member 71 and the guide base 72 are lifted from the first guide member 70 against the spring force of the spring 78. The linear guide engagement between the guide elements 70, 71 is then canceled, so that the tool shaft 26 can rotate freely.

In the reverse direction, i. in a reverse rotational movement of the link actuator 88, the Gegenkulissenfolger 97 can in turn get back into the lower portion 99, so that the guide elements 70, 71 engage and the eccentric cam mode N is set. The Gegenkulissenfolger 97 are presently designed as radially outwardly projecting projections of the second guide member 71.

The "package" of guide base 72 and second guide member 71 can be moved into the interior of the ring body 91 in turn or something out of it to switch between the two operating modes N and F.

For actuation of the rolling base 66, ie for their adjustment in the forced rotation eccentric mode Z or out, the slide actuator 88 also has link follower 101, which cooperate with a counter runner 102 of a counter link member 103. The Gegenkulissenglied 103 includes an annular body 104, on the front side of the counter-backdrop 102 is arranged. The Gegenkulissenglied 103 in turn actuates the rolling base 66th

In the present case, the Wälzbasis 66 and the Gegenkulissenglied 103 are both rotationally fixed, as well as with respect to the drive shaft 36 firmly connected to each other, so that an adjustment of the Gegenkulissengliedes 103 causes an adjustment of the Wälzbasis 66 directly and vice versa. The Wälzbasis 66 is locked with the Gegenkulissenglied 103, for example. For example, are latching hooks 165 from the Gegenkulissenglied 103 in the direction of the rolling base 66 from and under or behind this.

The Gegenkulisse 102 is a ring backdrop, so that the slide follower 101 slides on rotation of the slide operating member 88 on the counter-guide 102 along. The Gegenkulisse 102 now has deep portions 106 and higher portions 107, which are rotatably offset by 120 ° to each other corresponding to the gate followers 101, so that an annular uniform support of the gate follower 101 is given to the Gegenkulisse 102 and vice versa. Incidentally, this is also the case with the upper pair of links, since the counter-link followers 97 are arranged diametrically opposite one another, so that a uniform support of the rotational-angle guide means 67 on the link 98 is possible.

The Gegenkulissenfolger 97 are formed by the Drehlagervorsprüngen 92, at least from the radially inner portions. On the underside of these rotary bearing projections 92 locking projections 108 are arranged, which slide on the counter-guide 102 along. Now, when the slide followers 101 slide along the higher portions 107, thereby the counter link member 103 is force-applied in a direction away from the rolling element 65, so that the rolling base 66 is moved away from the rolling element 65 and disengages. Then, the tool shaft 26 is free of the forced rotation guide 64 and can rotate freely relative to the drive shaft 36. The free rotation eccentric mode F is set.

However, if the slide actuator 88 is rotated in the opposite direction, the counter slide 102 slides along the slide follower 101 until the higher sections 107 face the slide followers 101. A force applied by a spring 109 which acts on the rolling base 66 in the direction of the rolling body 65, thereby causing the Wälzbasis 66 engages with the rolling elements 65 engages.

At the higher portions 107 further recesses 105 are provided, into which the locking projections 108 can engage, so that the gear position of the eccentric 27 is at least with respect to the free rotation eccentric mode 'F fixed.

Based on the springs 78 and 109, a rotational preselection of the control handle 84 is possible. When a suitable rotational position of the tool shaft 26 with respect to the associated engagement contours, namely, for example, the guide seat 83 or a matching tooth position of rolling elements 65 and rolling base 66 is reached, the respective switching action of the eccentric only mode N in the forced rotation eccentric mode Z or in the freewheeling Eccentric mode F completely completed.

The rolling base 66 and the counter link element 103 firmly connected thereto are non-rotatable with respect to the drive axle 36, but can be adjusted parallel to the drive axle 36 by means of linear guides 110. The linear guides 110 comprise guide rods 111, which are fixedly connected to the lid 77. In any case, the linear guides 110 extend parallel to the drive axle 36 and are fixed relative to the gear housing 60. The guide rods 111 penetrate guide seats 112 on the counter link member 103 and the rolling base 66 provided on respective guide projections 113. The guide projections 113 are radially outward of the Annular body 104 and the annular Wälzbasis before and are also against rotation in grooves 114 on the inner circumference of the gear housing 60, so that the combination as Wälzbasis 66 and counter link member 103 is exclusively linearly movable, but secured against rotation.

• Das Werkzeug 24 kann in mehreren Relativ-Drehwinkelstellungen an der Werkzeugaufnahme 23, insbesondere deren Bajonett 118, befestigt werden.

Because of the eccentric cam mode 'N, not only can the tool 24 having a circular pad 115 be used, but also the tool 25 having a polygonal, presently triangular, abrasive plate 116 (in plan view). Thus, therefore, the outer contour of the tool 25 is polygonal, which could lead to injury to the operator, damage to the workpiece and the like other negative consequences in the free rotation eccentric mode F and the forced rotation eccentric mode Z. Here are the following measures to remedy the situation:

• The tool 24 can be attached to the tool holder 23, in particular its bayonet 118, in a plurality of relative angular positions.

The bayonet 118 comprises a bayonet disc 119, which is spring-loaded by means of a spring arrangement, for example a spring assembly 120. A screw 121 penetrates the spring assembly 120 and the bayonet disc 119 and is screwed from below into the tool shaft 26. Thus, the spring assembly 120 loads the bayonet plate 119 in the direction of a pressure plate 122. From the bayonet disc 119 are bayonet projections 123, 124 radially outwardly from, wherein the bayonet projection 124 is narrower than the other two bayonet projections 123. The projections 123, 124 together form a rotation angle coding 125.

The bayonet projections 123, 124 can be inserted through bayonet recesses 126, 127 on bayonet receptacles 128 or 129, ie machine mounts, the tools 24, 25, wherein subsequently the tool 24 or 25 is rotated relative to the tool holder 23, so that the projections 123, 124 come with Hintergreifvorsprüngen 130 of the bayonet receptacles 128, 129 for abutment or abut against rotational stops 131.

The bayonet recesses 126 extend over larger rotational angular distances than the narrower bayonet recess 127. Only the narrower bayonet projection 124 passes through them. Thus, it is only possible that rotation-angle-sensitive tool 25, namely the delta plate to attach to the tool holder 23 when the tool holder 23 and the tool 25 are rotationally correct to each other. Thus, therefore, the recesses 126, 127 form a counter-coding 132, which cooperates with the rotation angle coding 125.

The tools 24, 25 have on their advantageous elastic bottom expediently Velcro or other fastening means 180 for attachment of a sanding sheet or a polishing element. Suction openings 181 are also advantageously arranged on the underside, which communicate via channels leading to the top of the tools 24, 25 with a suction space 117b, which is connected to the dust discharge channel 49.

The tools 24, 25 are provided with annular seals 149 which seal on the tool holder 23 in the mounted state in cooperation with the tool holder 23, the suction chamber 117b.

In the case of the round tool 24, the spring force of the spring assembly 120, which applies a contact surface 130b of the tools 24, 25 to the pressure plate 122, is sufficient to reliably hold the tool 24 on the bayonet 118 even when the drive motor 17 is switched off.

The tool 25, however, an additional twist lock is provided. The rotation lock comprises a latch 133, which is expediently actuated by a push handle 134. The latch 133 acts in its locking position in which it engages or engages behind one of the bayonet projections 123 or 124, as the second, the rotation stops 131 opposite rotational stop.

The latch 133 is advantageously spring-loaded in the locking position. Thus, the operator only has to operate the push handle 134, i. in the direction of the working surface 41 of the tool 25 to adjust the latch 133 in its release position. The locking occurs almost automatically when the delta tool 25 is rotated to its correct position, namely, when its tip 135 faces the front 20 of the machine housing 11.

Also in connection with a tool change of the tool 24, the rotation angle guide means 67 have advantages: Namely, if they are in the eccentric only mode N, the tool holder 23 can no longer rotate about the drive shaft 36. A fastening and releasing the tool 24 is thus very easy to accomplish by a simple rotational movement. The rotation angle guide means 67 functions as a so-called spindle stop.

The rotation angle guide means 67 are, which is advantageous in the tool 25, in only one angular position of the tool shaft 26 with the drive shaft 57 into engagement, so that the rotational angular position of the tool holder 23 to the operating position of the tool 25 in relation to the machine housing 11 fits (tip 135 to the front 20), but alternatively, another or more other angular positions are conceivable, so the tip 135 could protrude obliquely or laterally transversely in front of the machine housing 11.

Namely, the protrusion 82 on the rolling element 65 is configured such that it fits in the guide seat 83 only in the correct rotational angle position relative to the second guide element 71. For this purpose, guide surfaces 136, 137 have different distances from the tool axis 37 intersecting diagonals of the rolling element 65, corresponding to guide surfaces 138 and 139 on the associated guide receptacle 83. By off-center or eccentric arrangement of the guide surfaces 136-139, it is only possible, they engage with each other when the rotational angle of the projection 82, and therefore also the thus rotatably fixed tool shaft 26 and the tool holder 23 to the rotational position of the machine side rotational angle stable second guide element 71 fits. Thus, if the rotation angle guides 67 are in the cam-only mode N, i. the guide members 70, 71 are engaged also matches the rotational angular position of the rotational angle sensitive tool 25 so that the tip 135 fits forward to the front 20.

At the opposite side of the tip 135, the tool 25 has an actuating projection 140. This is suitable, for example, for gripping the tool 25 in order to rotate it. In addition, the actuating projection 140 also fulfills a blocking function in which it interacts with a blocking body 141. A the machine housing 11 in the assembled state or to be mounted state of the tool 25 facing top of the actuating projection 140, which has a rod-shaped or rod-shaped form, forms a locking contour 142, which cooperates with the locking body 141. The locking contour 142 passes through a mounting path 143 when mounted on the tool holder 23 and finally assumes an end position 144 in the mounted state. Both on the assembly path 143 and in the end position 144, the locking contour 142 cooperates with the locking body 141 and that alternately such that when located in the end position 144 tool 25, an adjustment of the eccentric 27 in one of the rotation eccentric modes F or Z not possible is and vice versa, when the eccentric 27 is adjusted in one of these modes, it is not possible to attach the tool 25 to the tool holder 23.

The blocking body 141 is guided on the outside of the transmission housing 60 linear. The transmission housing 60 is therefore closed so far. This measure is particularly advantageous because the locking body 141 projecting in front of the outer contour of the machine housing 11, namely down, at least when he has a in FIG. 10a shown, to the tools 24 or 25 vorverstellte first position assumes, so to speak, a tool locking position. Thus, thus, a passage opening 145 through which a locking projection 146 passes out of the machine housing 11, a risk that dust enters the interior of the machine housing 11. In contrast, however, the transmission housing 60 is encapsulated.

The locking projection 146 projects from an angular section 147, which in turn protrudes angularly from a rod section 148 of the locking body 141 radially outward (relative to the gear housing 60). The rod portion 148 is guided directly on the outer circumference of the transmission housing 60, ie it is adapted to the contour of the gear housing 60. With the help of the angle section 147, a radial offset between the transmission housing 60 and an outer periphery of the seal 149, which has the tool 25 to the tool holder 23 out, bridged. Thus, therefore, the locking projection 146 acts in its first position in an area outside the seal 149, namely on the locking contour 142nd

An Axialverstellweg the locking body 141 is limited by linear stops. In the first position ( FIG. 10a ), the angle section 147 strikes, for example, on the drive part 33, in particular its lower edge. In the opposite direction, ie in the direction of a tool 24 or 25 away adjusted second position (so to speak a tool release position), a circumferential projection 150 acts in the transition region between the gear housing 60 and cover 77 as a longitudinal stop, namely a step 151 of the locking body 141 on the Circumferential projection 150 strikes. Thus, therefore, the axial travel of the locking body 141 is limited.

For its actuation in the first position now acts a bevel gear 152 (other gear, for example, toothed or rope gears are conceivable). The bevel gear 152 comprises an actuator bevel 153 on the actuator 87 and a locking body inclined surface 154 at the upper, free end of the locking body 141. The actuator bevel 153 is provided on an actuating projection 155 which projects radially outward in front of the actuator 87.

When the actuator 87 is rotated counterclockwise, at least in the direction of the locking body 141, the two inclined surfaces 153, 154 slide along each other, wherein the locking body 141 in the direction of the tool holder 23rd is adjusted (see arrow in FIG. 10b ). However, when the actuator 87 is rotated in the opposite direction, the lock body 141 is exposed to the top so that it can move from its first position to the second position.

There, the blocking body 141 is advantageously loaded by a spring 156 in the second position. The spring 156 rests on the one hand on the machine housing 11, i. on the outer circumference of the passage opening 145, and on the other hand on the locking body 141, specifically the angle section 147th

However, this upward movement in the direction of the second position is not possible when the actuator 87, the in FIG. 10a shown assumes position in the free rotation eccentric mode F and the forced rotation eccentric Z mode. Then, a blocking surface 157 at the upper end face of the blocking body 141 faces a sliding surface 158 on the actuating projection 155. The sliding surface 158 slides upon rotation of the actuator 87 along the locking surface 157 along. However, since the two surfaces 157, 158 in the first position of the locking body 141 act on each other in their normal direction, the locking body 141 is no longer in the second position upwards, ie, away from the tool holder 23, adjusted. Then it is no longer possible, the actuating projection 140 past the locking projection 146, ie that the tool 25 is not mounted on the tool holder 23.

In the free rotation eccentric mode F, it would now be possible in principle for the tool 24 to rotate freely and accelerate up to the speed of the drive shaft 57. The counteracts a brake member 170, which also performs the function of a seal. The brake member 170 is an annular brake member, which with its front side on a brake plate 171, the Tool holder 23 annular surrounds, rubs. The brake plate 171, so to speak, a brake ring is, so to speak expediently a replaceable component that can be replaced when worn.

Following an innovative concept, a brake segment 172 still protrudes from the brake plate 171 at an angle, on which, due to the eccentricity 38, the tool 24 rubs along in a specific rotational angle position and thereby experiences a braking torque. It should be noted that the brake segment 172 and the brake member 170 are not constantly, but only in certain rotational angle states with each other, so that the braking effect does not take place over an entire rotation of the tool 24, but only partial movements. As a result, an advantageous braking effect can be achieved.

Claims (13)

1. Hand-operated power tool, in particular grinding machine and/or polishing machine, with a drive motor (17) for driving a tool holder (23) for a tool (24, 25), in particular a backing pad or a polishing disc, via an eccentric gear (27) which has a drive shaft (57), rotary-coupled to the drive motor (17) and rotatable around a driving axis (36), to or on which is mounted by means of a tool shaft bearing (61, 62) a tool shaft on which the tool holder (23) is mounted, to carry out eccentric movements eccentric to the driving axis (36), wherein the eccentric gear (27) has switching means (85) for switching between a positive rotation eccentric mode (Z) and a free rotation eccentric mode (F), wherein the tool shaft (26) in the free rotation eccentric mode (F), in particular owing to bearing friction of the tool shaft bearing (61, 62), executes rotation movements during rotation of the drive shaft (57) and is freely rotatable relative to the driving axis (36), and wherein the tool holder (23), by means of a positive rotation guide (64), executes in the positive rotation eccentric mode (Z) a positive rotation around the driving axis (36) which changes its rotation angle position relative to the machine housing (11) of the hand-operated power tool (10), wherein the switching means (85) are designed to switch the eccentric gear (27) into an eccentric mode only (N), in which the tool shaft (26) engages with rotation angle guide means (67) to guide the tool shaft (26), and the tool holder (23) maintains its rotation angle position relative to the machine housing (11) within a rotation angle sector bounded by the rotation angle guide means (67), characterised in that the switching means (85) include an actuating gear with a slotted link actuating element (88), which has a slotted link follower (101) working in cooperation with a mating slotted link (102) and/or a slotted link (98) working in cooperation with a mating slotted link follower (97), so that by means of an adjustment of the slotted link actuating element (88),an adjustment of the mating slotted link (102) or the mating slotted link follower (97) may be effected, that a component of the eccentric gear (27) to be switched is connected to the mating slotted link (102) and/or to the mating slotted link follower (97), and that the slotted link (98) and/or the mating slotted link (102) have or has a latching recess (105) for latching with the mating slotted link follower (97) or the slotted link follower (101).
2. Hand-operated power tool according to any of the preceding claims, characterised in that the slotted link actuating element (88) is mounted rotatably around a rotation axis and effects linear adjustment of the mating slotted link (102) or the mating slotted link follower (97) parallel or at an angle to the rotation axis.
3. Hand-operated power tool according to any of the preceding claims, characterised in that the slotted link (98) and/or the mating slotted link (102) have or has a rotation end stop for the mating slotted link follower (97) or the slotted link follower (101).
4. Hand-operated power tool according to any of the preceding claims, characterised in that the slotted link actuating element (88) is rotary-coupled by means of a universal joint (86) to a control knob (84) which is mounted rotatably round an axis at an angle to the rotation axis of the slotted link actuating element (88).
5. Hand-operated power tool according to any of the preceding claims, characterised in that the rotation axis of the slotted link actuating element (88) is parallel or coaxial to the driving axis (36).
6. Hand-operated power tool according to any of the preceding claims, characterised in that at least one of the modes of the eccentric gear (27) may be preselected by an actuating element (87) of the switching means (85), that an engagement contour including the actuating element (87) and/or a gear component or guide component of the eccentric gear (27) adjustable by the actuating element (87) is spring-loaded into an engaged position by a mating contour, so that the engagement contour and the mating contour come automatically into the engaged position through an adjustment of the eccentric gear (27) or the guide component.
7. Hand-operated power tool according to any of the preceding claims, characterised in that the positive rotation guide (64) has a rolling element (64) non-rotatable relative to the tool shaft (26) and a roller base (66) non-rotatable relative to the machine housing (11) and on which the rolling element (64) rolls in the positive rotation eccentric mode (Z).
8. Hand-operated power tool according to claim 7, characterised in that the rolling element (64) is formed by a planet gear and the roller base (66) by a ring gear, or the rolling element (64) is formed by a ring gear and the roller base (66) by a planet gear, wherein the planet gear and the ring gear engage with one another in the positive rotation eccentric mode (Z).
9. Hand-operated power tool according to one of claims 7 or 8, characterised in that the switching means (85) may be used to adjust a relative position of the roller base (66) and the rolling element (64) to one another, and/or to make and release a non-rotatable connection between the rolling element (64) and the tool shaft (26) and/or between the machine housing (11) and the roller base (66).
10. Hand-operated power tool according to any of claims 7 to 9, characterised in that the rolling element (64) and the roller base (66), in the positive rotation eccentric mode (Z), are in positive and/or frictional engagement with one another, in particular by means of teeth or friction surfaces.
11. Hand-operated power tool according to any of the preceding claims, characterised in that it has braking means for braking the rotation of the tool shaft (26) around the driving axis (36) in the free rotation eccentric mode (F).
12. Hand-operated power tool according to any of the preceding claims, characterised in that at least three, in particular all, eccentric modes (N, F, Z) may be switched by a single control knob (84), and/or that the eccentric modes (N, F, Z) may be switched only in a fixed switching sequence and/or that the switching means (85) and/or the rotation angle guide means (67) are mounted at least substantially in a gear housing (60).
13. Hand-operated power tool according to any of the preceding claims, characterised in that the drive shaft (57) comprises a hollow shaft, in which the tool shaft (26) is held eccentrically.

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