Hand-held power tool

A manual machine tool having a drive motor, a gearbox arranged on a gearbox housing and a tool holder, wherein a motor drive of the drive motor with a gearbox drive of the gearbox and a gearbox output of the drive that is rotatable about an axis of rotation are coupled to the tool holder in a manner which permits rotation, wherein the gearbox can be switched between at least two switch positions in which the speed ratios between the gearbox drive and the gearbox output are different from one another, wherein the gearbox comprises a first wheel arrangement and at least a second wheel arrangement, each of which have at least one gear wheel and a switching gear element, wherein in both gear wheel arrangements the at least one gear wheel on the switching gear element and/or the switching gear element on at least one gear wheel can roll and the respective switching gear element is mounted in a locally adjustable manner to adjust the switch settings of the gearbox on the gearbox holding structure between the at least two setting positions and/or can be adjusted relative to the gearbox holding structure (44A) between an immobile position and a mobile position.

This application claims priority based on an International Application filed under the Patent Cooperation Treaty, PCT/EP2018/072958, filed Aug. 27, 2018, which claims priority to DE 102017119807.5, filed Aug. 29, 2017.

BACKGROUND OF THE INVENTION

The invention relates to a manual machine tool having a drive motor, a gearbox arranged on a gearbox holding structure, in particular a gearbox housing and a tool holder, wherein a motor drive of the drive motor with a gearbox drive of the gearbox and a gearbox output of the drive that is rotatable about an axis of rotation are coupled in a manner which permits rotation to the tool holder, wherein the gearbox can be switched between at least two switch positions in which the speed ratios between the gearbox drive and the gearbox output are different from one another, wherein the gearbox comprises a first gear arrangement and at least a second gear arrangement, each of which have at least one gear wheel and a switching gear element, wherein in both gear wheel arrangements the at least one gear wheel on the switching gear element of the gear wheel arrangement and/or the switching gear element on at least one gear wheel of the gear wheel arrangement can roll and the respective switching gear element is mounted in a locally adjustable manner to adjust the switch settings of the gearbox on the gearbox holding structure between the at least two setting positions and/or can be adjusted relative to the gearbox holding structure between an immobile position and a mobile position.

A manual machine tool of this type is for example described in EP 1 886 769 A1. The manual machine tool has a four-speed gearbox with two hollow wheels as switching gear elements. Each hollow wheel or switching gear element can be switched by means of an actuating device in the manual machine tool, wherein both hollow wheels are adjusted in a linear manner in the gearbox housing. A complicated actuating device is needed for the individual actuation of the hollow wheels.

EP 2 551 063 B1 also discloses a manual machine tool having a four-speed gearbox. The four-speed gearbox can be switched by means of an actuating device that is rotatable and can be adjusted in a linear direction. A deflection gear is needed to deflect a rotational movement of the actuating device in a linear movement of a switching gear element. Both switching gear elements must be controlled individually by the actuating device.

SUMMARY OF THE INVENTION

The object of the present invention is therefore to provide a manual machine tool with an improved operating concept.

In order to achieve this object, in a manual machine tool of the type mentioned at the outset there is a provision for the switching gear element of the first gear wheel arrangement to form a switch actuator for the second gear wheel arrangement to switch the gearbox between at least two of the switch positions, which switch actuator can be switched between a first setting position and at least a second switch position in which a movement of the switching gear element of the second gear wheel arrangement is different relative to the gearbox holding structure and/or the switch actuator is disengaged and engaged with the at least one gear wheel of the second gear wheel arrangement.

In order to achieve the object, a manual tool machine having a drive motor, a gearbox and a tool holder is also provided, wherein a motor drive of the drive motor with a gearbox drive of the gearbox and a gearbox output of the drive that is rotatable about an axis of rotation are coupled in a manner which permits rotation to the tool holder, wherein the gearbox can be switched between at least two switch positions in which the speed ratios between the gearbox drive and the gearbox output are different from one another, wherein the gearbox comprises a first gear arrangement and at least a second gear arrangement, each of which have at least one gear wheel and a switching gear element, wherein in both gear wheel arrangements the at least one gear wheel on the switching gear element of the gear wheel arrangement and/or the switching gear element on at least one gear wheel of the gear wheel arrangement can roll, wherein the gear wheel arrangements are arranged on a gearbox holding structure that is locally fixed related to a machine housing of the manual tool machine, in particular a gearbox housing. In this manual machine tool, it is provided that the switching gear element of the first gear wheel arrangement forms a switch actuator for the switching gear element of the at least one second gear wheel arrangement in order to switch the gearbox between at least two switch positions, wherein the switch actuator can be switched between a first setting position and at least a second setting position, in which a movement of the other switching gear element relative to the gearbox holding structure is different.

The basic idea is for the switching gear element of the direst gear wheel arrangement on the one hand to act as a switching element directly for the first gear wheel arrangement but on the other hand also to directly or indirectly influence the rotational behaviour of the second gear wheel arrangement, which in and of itself can be switched by means of its own switching gear element. The switch actuator can be directly engaged with one or more gear wheels of the second gear wheel arrangement, for example a planetary gear set with the second gear arrangement is tightly coupled to or engaged with the first gear arrangement, which forms or comprises the at least one gear wheel of the first gear wheel arrangements. The planetary gear sets can no longer be rotated relative to one another and are coupled to one another such that they cannot rotate by means of the switching gear element, for example a hollow wheel.

Another or an additional possible embodiment provides for the switch actuator, in other words the switching gear element of the first gear wheel arrangement, having an influence on the switching gear element of the second gear wheel arrangement, such that it can, for example, no longer rotate relative to the gearbox housing, but in the second setting position of the switching gear element the switching gear element of the second gear arrangement can be rotated relative to the gearbox housing. The second switching gear element can therefore be a roller base for the at least one gear wheel of the second gear wheel arrangement, which roller base can roll the second switching gear element accordingly.

The switching gear elements and the gear wheels of the gear wheel arrangement are preferably toothed wheels. Of course, the invention would also be easily possible in a rolling wheel drive or friction wheel drive.

In any case, the invention means that only the switching gear element of the first gear wheel arrangement needs to be adjusted in order to switch not only the first gear wheel arrangement but also the second gear wheel arrangement. This makes actuation significantly easier. For example, it is easier to construct an actuation device that only needs to be connected to or to control the switching gear element of the first gear wheel arrangement in order to act not only on the first gear wheel arrangement but also on the second gear wheel arrangement. For example, this can mean that a housing opening on a gearbox housing of the gearbox is not necessary that would otherwise have been necessary to control or actuate the switching gear element of the second gear wheel arrangement.

A configuration can provide for the switching gear element of the second gear wheel arrangement being tightly fixed in the first setting position of the switch actuator relative to the gearbox holding structure, in other words for example the gearbox housing, and to be rotatable in the second setting position relative to the gearbox holding structure. In the fixed position of the switching gear element of the second gear wheel arrangement, planetary gears, in other words the at least one gear wheel of the second gear wheel arrangement, can roll the switching gear element. In the rotatable position of the switching gear element of the second gear wheel arrangement, the at least one gear wheel, for example a planetary gear, can take the second gear wheel arrangement of the switching gear element with it, or rotate it simultaneously.

The switching gear element of the second gear wheel arrangement advantageously has at least one anti-rotation contour to engage in a positive-locking counter-contour of the gearbox holding structure and/or of the switching gear element that forms the switch actuator for the fixed regulation of the gearbox holding structure, for example the gearbox housing. The anti-rotation contour and the positive-locking counter-contour can for example be a pairing of teeth and spaces between the teeth or teeth recesses, a pairing of an anti-rotation projection and an anti-rotation recess, a groove structure or the like. It is possible for the switching gear element of the second gear arrangement to have several anti-rotation contours or to have anti-rotation contours on various sides, such that it can be fixed in a positive-locking manner on several components, for example on a positive-locking counter-contour of the gearbox housing that is fixed to the housing and/or on the switch actuator.

For example, the anti-rotation contour is arranged on a radial outer circumference on one front face or both of the switching gear element that can be switched by the switch actuator. Tooth structures may for example be provided there.

The switching gear element which forms the switch actuator can have arch-shaped teeth on its inner circumference as a positive-locking counter-contour, by means of which teeth in the first setting position the anti-rotation contour engages with the switching gear element which can be switched by the switch actuator and in the second setting position is engaged with the at least one gear wheel of the first gear wheel arrangement, for example the radial outer teeth. For example, this gear wheel meshes with the switching gear element or switch actuator.

In the first setting position it is advantageous if the switching gear element which forms the switch actuator is fully disengaged from the at least one gear wheel of the first gear wheel arrangement, in particular is out of direct engagement with the at least one gear wheel of the first gear wheel arrangement or all gear wheels of the first gear wheel arrangement. Consequently the switching gear element only then fulfils the function of a switch actuator for the other switching gear element, the switching gear element in the second gear wheel arrangement.

A configuration in which the switching gear element of the first gear wheel arrangement engages with the at least one gear wheel of the first gear wheel arrangement, for example a planetary gear set or at least two planetary gears of the first gear wheel arrangement if the switch actuator is in the first switch position is also possible. This is a possible configuration in the case of a coupling of planetary gear sets, with the components of the first gear wheel arrangement and the second gear wheel arrangement making up the configuration.

In the second setting position of the switch gear element which forms the switch actuator, the switching gear element of the at least one second gear wheel arrangement, in other words the switched switching gear element, can be rotated relative to the gearbox holding structure such that it can be moved along by the at least one gear wheel of the at least one second gear wheel arrangement. Consequently the switching gear element of the second gear wheel arrangement can rotate into the second setting position of the switch actuator and therefore be moved along by the one or more gear wheels of the second gear wheel arrangement.

The switching gear element which can be switched by the switch actuator is expediently mounted in a rotatable manner relative to the gearbox holding structure. It can also, in addition or alternatively to this, be received onto or into the gearbox holding structure in a linear, fixed manner. This is advantageous in particular if the switching gear element of the second gear wheel arrangement is fixed relative to a rotational axis of the gearbox output or its own rotational axis.

A bearing can be arranged on the gearbox housing or the gearbox holding structure for the rotatable mounting of the switching gear element which can be switched by the switch actuator of the second gear wheel arrangement, for example a bearing groove and a bearing projection, a roller bearing, in particular a needle bearing, ball bearing or the like. A supporting body is preferably arranged in a locally fixed manner relative to the gearbox holding structure, on the outer circumference and/or inner circumference of which the switching gear element of the second gear wheel arrangement is rotatably mounted. The at least one gear wheel of the second gear wheel arrangement is also provided for the rotatable mounting of the switching gear element. Consequently, the switching gear element of the second gear wheel arrangement can be rotatably mounted on one or more gear wheels of the second gear wheel arrangement or using the gear wheels. This is possible for example if the switching gear element of the second gear wheel arrangement is designed as a hollow wheel which surrounds the planetary gear set in a ring and is mounted on the planetary gear set.

It is further advantageous if the switching gear element of the second gear wheel arrangement can only be switched or actuated by the switching gear element which forms the switch actuator or the switching gear element of the first gear wheel arrangement. An actuating device which for example can be actuated directly by the operator from outside of the machine housing is therefore only linked to the switching gear element of the second gear wheel arrangement by means of the switching gear element of the first gear wheel arrangement and/or not directly.

The switching gear element which forms the switch actuator is expediently displaceably mounted in a linear manner relative to the gearbox holding structure, for example parallel to a rotational axis of the gearbox drive and/or the gearbox output or its own rotational axis, between the first setting position and the second setting position. The switching gear element which forms the switch actuator is expediently in one, two or more in particular settings positions relative to the gearbox holding structure pivot point. It is possible for as it were the switching gear element of the first gear wheel arrangement to be rotatable in a setting position, for example in an intermediate setting position that is between two further setting positions. The operator can then as it were move the switch actuator from a fixed setting position into a rotatable setting position relative to the gearbox housing or the gearbox holding structure by for example adjusting it in a linear manner, rotating it or the like.

It is further advantageous if one or more, in particular all, of the switching gear elements is/are spring-loaded in a respective switch position. In this way, for example, the switching gear element of the second gear wheel arrangement can be spring-loaded by means or a spring arrangement in one or both of the first and second setting positions. If the teeth of one of the switching gear elements do not fit with the respective gear wheel of the first or second gear wheel arrangement to be switched or meshed, the spring loading ensures that where the teeth do match the matching teeth glide into the respective places.

The gear wheels of the first gear wheel arrangement which are or can be in rolling engagement and the at least one second gear wheel arrangement are expediently different from one another in terms of their diameter and/or they have different roller circumferences from one another in terms of their diameter for the rolling engagement with the respective assigned switching gear element. This means that different speed ratios can expediently be set between the gearbox drive and the gearbox output.

The gear wheels of the first gear wheel arrangement which are or can be in rolling engagement and the at least one second gear wheel arrangement are expediently fixed to one another in a manner that prevents rotation and/or are designed on at least one stepped planetary gear. A planetary gear set preferably has at least two stepped planetary gears. A stepped planetary gear has for example a smaller and a larger roller circumference, between which there is a step.

Expediently there is a provision for a radial outer circumference of the switching gear element of the second gear wheel arrangement to align with the radial outer circumference of the at least one gear wheel of the first gear wheel arrangement such that the switching gear element which forms the switch actuator can be adjusted between the outer circumferences of the switching gear element of the second gear wheel arrangement and the at least one gear wheel of the first gear wheel arrangement in a linear manner, in particular parallel to a rotational axis of the gear wheel. The switching gear element of the second gear wheel arrangement therefore does not protrude in a radial outer direction in front of the at least one gear wheel of the first gear wheel arrangement, it is instead aligned with it. This alignment should be understood, however, as meaning that an angular offset can be present between positive-locking contours, for example teeth, of the switching gear element that can be adjusted in a linear direction and the switching gear element of the second gear wheel arrangement or the at least one gear wheel of the first gear wheel arrangement, which angular offset is then cancelled out in the event of a further movement of the gearbox such that the linear adjustment of the switching gear element is possible. For example the switching gear element of the second gear wheel arrangement is a hollow wheel which is arranged on the outer circumference of one or more planetary gears of the second gear wheel arrangement and on its outer circumference has teeth that have the same tooth geometry as the at least one gear wheel, in particular planetary gear, of the first gear wheel arrangement and is aligned with the gear wheel of the first fear wheel arrangement such that the switching gear element designed as a hollow wheel and serving as a switch actuator can be adjusted in a linear manner between the outer circumferences of the hollow wheel of the second gear wheel arrangement and the at least one gear wheel of the first gear wheel arrangement.

The gear wheels which are or can be in rolling engagement with the switching gear elements of the first gear wheel arrangement and the at least one second gear wheel arrangement are for example connected to one another in a fixed manner or in one piece. They can also form stepped gears or stepped planetary gears.

It is also possible for the gear wheels which are or can be in rolling engagement with the switching gear elements of the first gear wheel arrangement and the at least one second gear wheel arrangement to be separate from one another but arranged on a common planetary gear support or bar.

A further embodiment of the invention provides for the gearbox drive to be connected to a sun wheel in a fixed manner or coupled in a manner which permits rotation, which sun wheel is in a rolling engagement with the at least one gear wheel of the first gear wheel arrangement. It would also be conceivable, however, for the sun wheel to be engaged with one or more gear wheels, for example planetary gears, of the second gear wheel arrangement.

The gear wheels of the first gear wheel arrangement and the second gear wheel arrangement can be arranged on a common planetary gear support or bar, but can also be arranged on separate, in particular rotatable or movable relative to one another planetary gear supports or bars.

The first gear wheel arrangement and the second gear wheel arrangement expediently form a first gearbox step, wherein the gearbox has at least a second gearbox step, for example a planetary step. The first gearbox step is upstream or downstream of the gearbox output of the second gearbox step. In particular, the gearbox steps are therefore arranged sequentially one behind the other.

The second gear wheel step can be a gearbox step providing a fixed speed ratio, in other words merely a gearbox step that decreases or increases speed and cannot be switched. A switchable configuration is, however, preferred. The second gearbox step can expediently be switched between at least two switch positions in which a speed ratio between a drive of the first gearbox step and an output of the second gearbox step is different. This means, for example, a four-speed gearbox can be achieved.

The switching gear element of the first gear wheel arrangement and/or the switching gear element of the second gear wheel arrangement, in particular both, are preferably hollow wheels or have hollow wheels.

An advantageous embodiment provides for the gearbox to have a first switching gear element and a second switching gear element, one of which is the switch actuator, in other words the switching gear element of the first gearbox arrangement and the other switching gear element is a further, separate switching gear element switched by the switching gear element of the second gearbox arrangement. In total, the gearbox therefore has three switching gear elements, of which the first and second switching gear elements described below can advantageously be actuated by means of the actuation concept described below. The first and the second switching gear elements can be adjusted in a linear manner using an actuating device between a first setting position and a second setting position in each case relative to the gearbox holding structure which in this case is designed as a gearbox housing, wherein the actuating device is coupled to the switching gear elements and has an actuating part that is rotatably mounted about an actuating pivot axis relative to a machine housing of the manual machine tool, wherein the first switching gear element can be adjusted by a pivoting movement of the actuating part amount the actuating pivot axis in a linear manner along its setting axis using a deflecting gear, wherein the deflecting gear comprises a carrier ring which extends in a ring shape about the gearbox housing and rotatably mounted about the actuating pivot axis, which carrier ring is coupled to the first switching gear element in order to adjust this in a linear manner using a first coupling element. In this configuration, there is a provision for the actuating part to be displaceably mounted on the carrier ring in a linear manner along an actuating longitudinal axis and coupled to the at least second switching gear element using a second coupling element to achieve linear displacement of the second switching gear element.

The fundamental idea of this is that in principle the carrier ring forms a rotating body or a pivot bearing for the actuating part. The actuating part can therefore pivot about the gearbox housing with the carrier ring in order to switch the first switching gear element. In turn, the actuating part is displaceably mounted in a linear manner on this carrier ring, such that it can carry out the linear movement to adjust the second switching gear element directly. A further slide or support for the actuating part or the second coupling element is not necessary. It is also possible in this arrangement to carry out the two actuating movements, namely about the actuating longitudinal axis and actuating pivot axis, which can occur in parallel to one another, in an overlaid manner such that the first switching gear element and the second witching gear element can be switched simultaneously and the gearbox can be switched for example from a first switch position or a first gear directly into a third gear or a third switch position without the second or an intermediate switch position or a gear arranged in between needing to be controlled.

Compared to the embodiment of a gearbox according to EP 1 886 769 A1 mentioned at the outset, this therefore results in simpler operation.

Compared to EP 2 551 063 B1, the actuating device and the coupling between the actuating device and the switching gear element is simpler in structure. In particular, a single coupling element, the second coupling element, is sufficient between the actuating part and the second switching gear element. This can even be arranged in one piece on the actuating part if there is a corresponding degree of rotational freedom between the second coupling element and the second switching gear element.

A spring arrangement is expediently arranged between the actuating part and the first switching gear element or the second switching gear element or both. The spring arrangement places a load on the switching gear element in its respective setting position or a setting position assigned to the position of the actuating part during and/or after an actuation of the actuating part. If the switching gear element cannot reach its setting position, for example because its teeth are not aligned with the teeth of a gear wheel that works with the switching gear element, the spring loading ensures that in the event of a relative rotational adjustment of the switching gear element and gear wheel, the two components can mesh together in a positive-locking manner.

The spring arrangement between the second switching gear element and the actuating part can in particular be provided by the second coupling element, for example exclusively by the second coupling element. It is also possible, however, for a spring or spring arrangement which is separate to this to be provided. A spring arrangement and the elastic coupling element can also be provided. The spring arrangement can however easily be provided between the first switching gear element and the actuating part by the first coupling element.

The first coupling element or the second coupling element or both can for example comprise or be a spring element. In particular, a spring bow or the like is suitable as an elastic, flexible coupling element, for example as described in EP 1 886 769 B1.

The first coupling element and/or the second coupling element expediently comprises a spring bow or is formed by a spring bow. The spring bow expediently extends in a ring shape about the first switching gear element or the second switching gear element. The spring bow can for example have bow arms, which are elastic and flexible. The longitudinal ends of the spring bow expediently engage in corresponding recesses, for example bores, grooves, guides, in particular longitudinal guides or the like, on the respective first or second switching gear element.

A preferred and simple embodiment provides for the actuating part to be coupled to the second switching gear element exclusively by means of the second coupling element or by means of a single component. Consequently no further component is necessary between the switching gear element and the actuating part. In particular, the spring bow which has already been mentioned is suitable as a second coupling element and extends as a single component to make the connection between the actuating part and the second switching gear element.

A for example ring-shaped, rod-shaped or otherwise similarly designed transmission part is arranged between the carrier ring and the first coupling element, which transmission part can be moved about the actuating pivot axis together with the carrier ring. The transmission part and the carrier ring can be moved relative to one another, for example they are rotatable and/or displaceable relative to one another. A spring arrangement is arranged between the transmission part and the carrier ring which can be actuating by means of a relative movement of the transmission part and the carrier ring in order to achieve spring-loading of the first setting gear element in at least one switch position. Consequently, the carrier ring can reach a final rotation position while the transmission part has not yet reached this final position and is spring-loaded in the final position by the spring element or the spring arrangement. If the first setting gear element has a suitable position with respect to a component to be switched, for example a gear wheel, it is pushed or adjusted into this final position by the spring arrangement.

At least one guide cam is expediently arranged on the carrier ring or a transmission part that can be moved together with the carrier ring about the actuating pivot axis, for example the above-mentioned protruding part which can be adjusted relative to the carrier ring in order to deflect the movement of the actuating part about the actuating pivot axis into a linear movement of the first setting gear element. The first coupling element or a body associated with this or coupled to this engages with the guide cam. Two guide cams are preferably provided which are arranged on opposite sides of the gearbox housing or the gearbox holding structure.

The second coupling element is expediently pivotably and/or displaceably mounted relative to the gearbox housing. Consequently it is possible for the second coupling element, which is adjusted in a linear manner, to transfer the linear movement to the second setting gear element on the basis of a displacement relative to the gearbox housing. However, a pivot bearing or a combined pivot and thrust bearing of the second coupling element is also possible.

The second coupling element is expediently pivotably mounted on a pivot bearing provided on a gearbox housing, for example a bearing pin which protrudes from the circumference wall of the gearbox housing or a bearing recess arranged in the circumference wall of the gearbox housing. The second coupling element can also alternatively or additionally be pivotably mounted on the actuating part. The bearing recess can for example be achieved by a longitudinal groove. This longitudinal groove can also be the arch-shaped guide recess described below. If bearing pins or bearing recesses are provided on the gearbox housing, these are expediently provided on opposite sides of the gearbox housing and/or on an area of the gearbox housing which is largest in size. Consequently, the bearing pins protrude for example in a radial direction in front of the circumference wall of the gearbox housing.

The actuating part expediently has a guide recess which extends in an arch shape about the actuating pivot axis and engages in the second coupling element. In particular, the second coupling element has a straight or curved section which engages in the above-mentioned guide recess. It is possible for the guide recess to be of a sufficient depth for an arch-shaped moving space to be present in which the second coupling element can engage when it pivots about the actuating pivot axis.

A grid arrangement is preferably provided which is used to lock the actuating part in at least one actuating position. The grid arrangement has for example a locking recess or an arrangement of several locking recesses on the actuating part. The locking arrangement is preferably arranged in a hidden manner. The locking arrangement is preferably arranged on a lower side of the actuating part and/or between the actuating part and the gearbox housing. One or more locking recesses can be provided on the actuating part in which a locking part, in particular a sprung or elastic locking part engages, which locking part is arranged on the gearbox housing. The elastic locking part can, however, also be arranged on the actuating part and engage in the locking recesses on the gearbox housing. The actuating part can therefore be locked in a respective switch position, for example in the respective longitudinal end position relative to the actuating longitudinal axis and/or a pivot position relative to the actuating pivot axis.

The actuating part is expediently displaceably mounted in a linear manner on a linear guide of the carrier ring. Consequently, the carrier ring has a linear guide with one or more guide grooves or other linear guide elements of the like. Linear guide projections can also be provided, for example longitudinal ribs or the like, which stick out from the carrier ring and engage in corresponding longitudinal guide grooves on the actuating part. Consequently, linear guide components are present on the carrier ring and on the actuating part.

A further embodiment provides for the actuating part to be guided on a machine housing of the manual machine tool. For example, a wall of the machine tool has a slot or recess in which the actuating part is arranged. Guide recesses, in particular guide grooves, pockets or the like can be provided on one or more edge areas of the recess to guide the actuating part.

The second coupling element expediently engages in a slot of the linear guide. For example, the linear guide has linear guide sections, between which the slot is arranged. The linear guide sections are expediently connected by means of connection sections. The second coupling element engages between the connection sections and the actuating part.

The linear guide expediently comprises two linear guide sections arranged at an angular distance from one another relative to the actuating pivot axis. Consequently, the actuating part can be guided on two or more linear guide sections, which can also be interrupted, for example by the above-mentioned slot.

The actuating part expediently has at least one support section to support the gearbox housing. Consequently the actuating part is supported on one side by the carrier ring and on the other side on the gearbox housing.

It is preferable for the actuating part to have an arch-shaped or barrel-shaped wall design. Consequently, it is advantageous for the actuating part to cover the components and/or the locking arrangement to be actuated by it.

A further embodiment can provide for the actuating part to connect longitudinal end areas of the carrier ring that are at a distance from one another to one another. The carrier ring has a distance between its longitudinal end areas that is bridged by the actuating part. For example, the actuating part engages in linear guide sections arranged on the longitudinal end area such that these linear guide sections are connected to one another relative to the actuating pivot axis. The actuating part therefore closes the carrier ring as it were.

At this point it should be noted that the carrier ring can be a closed ring, in other words it fully surrounds the gearbox housing. It is also possible, however, for the carrier ring to only be a partial ring. Consequently, the carrier ring can be designed as a ring segment. The carrier ring preferably extends around at least half of the outer circumference area of the gearbox housing, in other words around at least 180 degrees. It is preferable for the carrier ring to extend around at least 270 to 300 degrees of the outer circumference of the gearbox housing.

The gearbox is expediently a planetary gear. Other types of gear are, however, also easily possible.

The first and/or the second setting gear element expediently comprises a hollow wheel or is formed by a hollow wheel. In particular, there is a provision for one of the hollow wheels to be arranged on the outer circumference of the other hollow wheel.

Advantageously there is a provision for a radial outer circumference of the switching gear element of the second gear wheel arrangement and a radial outer circumference of the at least one gear wheel of the first gear wheel arrangement to be aligned with one another such that the switching gear element of the first gear wheel arrangement can be brought into engagement, in particular meshing engagement, with the radial outer circumference of the at least one gear wheel of the first gear wheel arrangement or the switching gear element of the second gear arrangement. For example, the at least one gear wheel of the first gear wheel arrangement is a planetary gear or comprises a planetary gear. It is preferable for a radial outer circumference of a planetary gear set to which the gear wheel of the first gear wheel arrangement belongs and a radial outer circumference of the switching gear element of the second gear wheel arrangement to be aligned with one another. In particular, teeth with the same teeth distances or teeth geometries are present on the respective radial outer circumferences of the switching gear element of the second gear wheel arrangement and the gear wheel of the first gear wheel arrangement such that the switching gear element of the first gear wheel arrangement can be brought into meshing engagement with both sets of teeth.

It is preferable for the switching gear element of the first gear wheel arrangement, in other words the switch actuator for the second gear wheel arrangement to engage with either the switching gear element of the second gear wheel arrangement or the at least one gear wheel of the first gear wheel arrangement, in particular to mesh with the at least one gear wheel.

The embodiment of the invention described below in greater detail in the drawing shows a screwing machine or drilling machine. Of course the invention can also be used in other manual machine tools, for example milling machines, cutting machines, saws, grinding machines, polishing machines and the like. The gears and/or the actuating device can, however, also be used in manual machine tools, for example, which have a tool holder that is driven in an oscillatory manner, for example moved backwards and forwards in a linear manner.

The manual machine tool expediently has a tool holder for a tool and/or a tool, for example a drilling tool, screwing tool or the like. A cutting tool, milling tool or the like can, however, also be provided.

The gearbox output of the gearbox is expediently directly rotationally coupled to a tool holder on the manual machine tool. A recess for a screw bit, drill chuck, screw chuck or a tool chuck of the like can be provided, for example. It is also advantageous if a striking mechanism is arranged on the gearbox output, for example an axial striking mechanism.

It is also possible for an angle gear to be present between the gearbox and a tool holder, for example an angular gearbox or a conversion gearbox, which converts the rotating output movement of the gearbox output into an oscillatory linear movement or a hypercycloid and/or eccentric movement of the tool holder.

DETAILED DESCRIPTION

A manual machine tool10, for example a screwing device, has a machine housing11which is preferably pistol-like in shape. An operator can grip the machine housing11and therefore the manual machine tool10using a handle section12which protrudes from a motor section13of the machine housing11. An energy storage interface14is provided on a foot area or a free end area of the handle section12which faces away from the motor section13, to which energy storage interface an energy storage device25such as a battery pack can be attached. Consequently the manual machine tool10can be operated in a self-sufficient and wireless manner, but it does not have to do so. A manual machine tool having a mains connection14B for an AC network, in particular a connection cable with a plug and/or a socket for a connection cable, in particular a power cable, or a manual machine tool with an energy storage interface and a mains connection would easily also be possible.

The energy storage interface14supplies a power supply device15with electrical energy. The power supply device15can be actuated by means of a switch16which is preferably arranged on the handle section12to supply power to a drive motor17that is received in the motor section13of the machine housing11, in particular to set its speed and/or torque.

The drive motor17has a motor shaft18which extends in a longitudinal direction of the motor section13. The motor shaft18is rotatably mounted on motor bearings19. The drive motor17has for example an exciter coil arrangement20which is penetrated by the motor shaft18and which is rotatably received in a rotor, in particular a permanent magnet rotor, a squirrel-cage rotor or the like.

The drive motor17is arranged in the machine housing11in a fixed position. Its motor shaft18extends from a rear wall21in the direction of a front face22of the motor section13. An upper side wall23of the machine housing11is provided on the side of the motor section13which faces away from the handle section12. A rotation direction alternator24is preferably arranged between the handle section12and the motor section13, by means of which the direction of rotation of the drive motor17can be set or changed.

A hook element26is preferably provided on a free end area or another point in the machine housing11to hang up the manual machine tool, for example on a user's belt.

A motor output27of the drive motor17drives a gearbox40of the manual machine tool.

The gearbox40has a gearbox drive41designed as a drive wheel and/or drive shaft or having a drive wheel and/or a drive shaft, which gearbox drive is connected to the motor drive27in a fixed manner.

A gearbox drive42of the gearbox drives a tool shaft28, for example, which protrudes from the front face22of the machine housing11.

The tool shaft28has a tool holder29for example for a tool30, for example a drilling tool, a screwing tool or the like. The tool shaft28is for example rotatably mounted by means of a bearing31on the machine housing11. The tool shaft28can also be mounted directly by the gearbox40or on the gearbox40, for example using a bearing43.

It is also advantageous if in a manual machine tool according to the invention a striking mechanism for example an axial striking mechanism and/or rotational striking mechanism is arranged on the output of the gearbox. A striking mechanism of this kind can also easily be integrated into the gearbox. A striking mechanism200is provided in the specific embodiment.

An impact body201of the striking mechanism200is for example formed by the tool shaft28or fixed to this. The impact body201is for example a ring which is penetrated by the tool shaft28and is connected to the tool shaft28in a manner that prevents it from rotating and that is fixed in an axial direction.

The impact body201is force-actuated by means of a spring202in a forwards direction SW1, in other words towards the tool holder29.

The striking mechanism200can be switched between a described striking operation and a non-striking operation, for example by means of an actuation of an actuating element206that can be gripped by the operator. The actuating element206comprises, for example, a slider or a rotary element. The actuating element206can be adjusted as a setting body207between the switch position shown inFIG. 2and assigned to the striking operation in which the tool shaft28including the bearing31can be displaced in a linear manner relative to the rotational axis D, in other words has an end clearance and therefore teeth203,204can engage with one another, and a further switch position that is not shown in the drawing which represents a non-striking operation and in which the teeth203,204are kept apart from one another. The bearing31is held on the setting body207. The tool shaft28is displaceably mounted on bearing43relative to the rotational axis.

The teeth203are arranged on an abutment body205which is arranged between the bearing43and the impact body201and is fixed in position (prevented from rotating and fixed to prevent displacement) relative to the machine housing11. The teeth203are opposite the teeth204arranged on the impact body201. The teeth203,204are arranged on the respective front faces of the abutment body205and the impact body201. The teeth203,204are preferably angular teeth. The teeth203,204preferably extend in a ring-shaped or partially ring-shaped manner about the rotational axis D of the tool shaft28.

If there is pressure in a direction of force SW2on the tool shaft28, for example if the tool30is loaded against the machine housing11by means of a screw or a workpiece, the teeth203,204glide along one another, wherein they adjust the impact body201in the direction of force SW2such that a spring202force-actuated with a direction of force SW1is tensioned. If the teeth203,204are further rotated from one pair of teeth into the next pair of teeth, they can immerse into one another suddenly when loaded by the spring202, such that a strike occurs in the direction of force SW1on the tool shaft28and consequently the tool holder29.

An embodiment that is only partially indicated inFIG. 4provides for a recess chuck32, for example a drill chuck, instead of the tool shaft28, which recess chuck is suitable for holding for example the tool30.

The gearbox40is a four-speed gearbox. The gearbox40can therefore be switched between four gears or switch positions S1, S2, S3and S4which are showing inFIGS. 12, 13, 14 and 15.

The gearbox is received in a gearbox housing44. The gearbox housing44has a circumference wall45which delimits an essentially cylindrical inner space in which the gearbox components, pinions and the like of the gearbox are essentially received. On the front face the gearbox housing44is covered by front walls46,47, for example covers. The front walls46,47have openings48through which the motor drive27can be connected to the gearbox drive41and the tool shaft28or the recess chuck32to the gearbox drive42of the gearbox40. The openings48are for example penetration openings.

The gearbox housing44is received in the machine housing of the manual machine tool10in a manner that prevents it from rotating, which is why for example teeth49and/or an anti-rotation projection49A are provided on the front wall47which faces aware from the tool holder29and/or a circumference contour50designed in the manner of anti-rotation protection are provided on the front wall, which faces away from the drive motor17.

Consequently the gearbox housing44which forms a base gearbox housing (the circumference wall45) and the front walls46,47which form the covers essentially tightly enclose the gearbox components of the gearbox40described below, which is which sealing elements, in particular textile seals, plastic seals, O-rings, labyrinth seals etc. can be provided.

The gearbox40has a first gear step G1and a second gear step G2. The first gear step G1forms an initial gear step and can be driven by the gearbox drive41. The second gear step G2forms an output gear step and drives the gearbox output42of the gearbox40.

The gear steps G1and G2are planetary gear steps. Overall, the gearbox40is designed as a planetary gearbox.

The gear step G1comprises a sun wheel51which is arranged on the drive wheel or gearbox drive41or is in one piece with the gearbox drive41. The sun wheel51meshes with the planetary gears51which are rotatably mounted on a bar or planetary gear support53. For example the planetary gears52are rotatably mounted on axis elements55which protrude in front of a carrier body54. The planetary gears52can be mounted directly onto the axis elements55or as preferred in the embodiment by means of roller bearings56, in particular ball bearings or needle bearings, which improves the rotatability and the bearing. On the one hand the axis elements are on opposite sides of the carrier body54and on the other hand there is an output57on the carrier body which forms a sun wheel58for the second gear step G2. Teeth59are provided on a radial outer circumference of the planetary gear support53or the carrier body54.

The planetary gears52form a planetary gear set60, to which a first hollow wheel61and a second hollow wheel62are assigned.

The planetary gears52are step planetary gears as it were. The planetary gears52have roller circumferences63,64with different diameters which are assigned to the first and the second hollow wheels or mesh with these when a corresponding switch position of the gearbox40is set.

The hollow wheel61is mounted in a rotatable manner in the gearbox housing44but cannot be displaced in an axial direction.

In the embodiment the hollow wheel61is received between the front wall46and the steps65of the planetary gears52in a sandwich-like manner.

The hollow wheel61is for example supported on its opposite front faces directly or indirectly on the front wall, and opposite this on the other front face on a step65provided between the roller circumferences63,64. A bearing plate66is preferably provided between the hollow wheel61and the front wall46, which bearing plate is received inside the circumference wall65in rotatable manner or preferably in a fixed manner to prevent rotation as shown inFIG. 4by means of corresponding outer circumference contours or rotation positive-locking contours.

It is also possible for the hollow wheel61to be held in a non-displaceable manner relative to a rotational axis D of the gearbox output42of the gearbox, for example by means of ring contours which are engaged with a support body61described in greater detail below. A ring projection can for example protrude in a radial, outwards direction in front of the support body61and engages in a ring groove on the inner circumference of the hollow wheel.

In the sense of a stabilisation or a mechanically resilient structure, it is also possible for the axis element55to be supported on a support body67on the free ends which face away from the carrier body54. The support body67has recesses68for at least one of the axis elements55. Support projections69are also provided which as it were delimit recess chambers or recess spaces for the planetary gears62. It is possible but not essential for part of the axis element55, in particular an axis element55which does not support any planetary gears to engage in the support projections69in a positive-locking manner, which is why the support projections69have recesses69A for example. The planetary gears52are as it were received between the planetary gear support53and the support body57in a sandwich-like manner and rotatably mounted on the planetary gear support53, namely the axis elements55of this.

It is understood that the support body67and the carrier body54can also be in one piece. The support body67is also optional, in other words the carrier body54would be sufficient to rotatably mount the planetary gears such that the support body67is not present in this case.

While the first hollow wheel61is mounted in the gearbox housing44in a rotatable but non-displaceable manner, the second hollow wheel61is mounted in the gearbox housing in a displaceable but non-rotatable manner relative to a setting axis SA. Anti-rotation projections70are provided on the radial outer circumference of the second hollow wheel62and engage in the anti-rotation recesses71of the gearbox housing44. The anti-rotation projections70are preferably designed in the manner of slot grooves, cam followers or the like. They engage in the anti-rotation recesses71. The anti-rotation recesses71are for example designed as longitudinal grooves72which run in parallel to the setting axis SA. The anti-rotation recesses71or longitudinal grooves72extend for example on the inside or on the inner circumference of the circumference wall. The anti-rotation projections70and/or the anti-rotation recesses may have different cross-sectional contours, for example have a wider or narrower design in the peripheral direction. It is not specifically about ensuring fundamental functionality that the hollow wheel62can be adjusted along the setting axis SA or in parallel to the setting axis SA on the gearbox housing40and/or relative to the planetary gear set60.

In the switch position shown inFIG. 12andFIG. 14, namely the first switch position S1and the third switch position S3, the second hollow wheel52is in a setting position P1relative to the setting axis SA in which the second hollow wheel holds the first hollow wheel61in the gearbox housing in a manner which prevents it from rotating such that the planetary gears52mesh with inner teeth75of the first hollow wheel61with their smaller roller circumferences63and roll on the inner teeth75. The second hollow wheel62, which is received in the gearbox housing in a manner which prevents it from rotating, has anti-rotation contour on its inner circumference to hold the first hollow wheel61which has corresponding complementary rotational positive-locking contours on its outer circumference in a manner which prevents it from rotating. These rotational positive-locking contours and complementary rotational positive-locking contours are provided by inner teeth73of the second hollow wheel62and outer teeth74of the first hollow wheel61, which can engage with one another in a positive-locking manner. Consequently the inner teeth73of the second hollow wheel62have on the one hand the function that the planetary gears52can roll on them and on the other hand the function of holding the first hollow wheel61in a manner which prevents rotation relative to the gearbox housing44and consequently also the machine housing11of the manual machine tool10.

If the second hollow wheel takes the setting position P2shown inFIGS. 13 and 15relative to the setting axis SA, the first hollow wheel61is released for rotation. Consequently, the planetary gears52and the planetary gear set60can take the first hollow wheel61along with the rotation and experience no or minimal resistance as a result of the hollow wheel. In this situation, the planetary gears52roll with their larger roller circumferences64on the inner circumference, and consequently the inner teeth73of the second hollow wheel, which is essential for the switch positions shown inFIGS. 13 and 15, the second switch position S2and the fourth switch position S4, of the gearbox40. The output57of the first gearbox step G1rotates into the second and fourth switch position at a high speed and with a lower torque than in the first and third switch position S1, S3.

The gear step G2comprises planetary gears76of a planetary gear set77which engage on the one hand with the sun wheel58, in other words the output of the first gear step G1, and on the other hand with a third hollow wheel78. The third hollow wheel78is received in the gearbox housing44in a manner that is displaceable along a setting axis SB. The setting axis SA can be coaxial or parallel to the setting axis SB. The setting axes SA, SB are shown inFIGS. 12 and 13by way of an example.

The setting axes SA, SB can also, for example, be coaxial with or concur with a rotational axis D of the gearbox40and/or the gearbox drive41and/or the gearbox output42. The rotational axis D of the gearbox40is simultaneously the rotational axis of the drive motor17such that ultimately the gearbox40, the drive motor17and the gearbox output42are coaxial. The tool holder23also rotates about the rotational axis D.

The planetary gears76are rotatably mounted on a planetary gear support79, in other words a bar. The planetary gear support79has a carrier body80with the axis element81arranged on one side and the gearbox output42arranged on the opposite side. The axis elements81protrude from the sun wheel58and consequently the output57of the first gear step G1such that the planetary gears76rotatably mounted on the axis elements81or rotatably mounted by the axis elements81are engaged with the output57or can be driven by this. The planetary gears76can be directly or indirectly rotatably mounted on the axis elements81, for example by means of roller bearings, in particular needle bearings.

The planetary gear set77comprises for example four planetary gears76while the planetary gear set60comprises three planetary gears52. These figures should not, however, be understood as restrictive. One planetary gear set can very much also comprise two planetary gears, five planetary gears or another number of planetary gears.

The radial outer circumference of the hollow wheel78has anti-rotation projections83which are engaged with the anti-rotation recesses84on the gearbox housing44, for example these can be applied to the cover or the front wall47. In the switch positions S1and S2of the gearbox40shown inFIGS. 12 and 13, the third hollow wheel78takes on a setting position P3relative to the setting axis SB in which the third hollow wheel78is fixed in a manner which prevents rotation relative to the rotational axis D or the gearbox housing44. The anti-rotation projections83then engage in the anti-rotation recesses84.

In a setting position P4relative to the setting axis SB, however, the anti-rotation projections83of the third hollow wheel78are arranged free from or beyond the anti-rotation recesses84such that the hollow wheel78can rotate about the rotational axis D.

In setting position P3, the fixed position of the third hollow wheel78to prevent against rotation, the outer circumferences of the planetary gears78roll on inner teeth85of the hollow wheel78. The second gear step G2causes a reduction and speed and therefore an increase in torque from its input side to its output side or from its drive to its gearbox output42.

In the setting position P4of the hollowing wheel78, however, the wheels76continue to be engaged with the inner teeth85. The inner teeth85of the hollow wheel78, however, continue to be engaged with the outer and radially outer teeth59or the planetary gear support53. The hollow wheel78is therefore fixed in a manner which prevents rotation relative to the planetary gear support73. In addition to this, the planetary gears76are mounted in a manner which prevents rotation between the teeth of the sun wheel78and the inner teeth85of the third hollow wheel78. Consequently, in this situation the second gearbox step D2has a speed ration of i=1 between an input side and an output side and therefore does not cause either a change in speed or a change in torque.

The gearbox output42is provided on the planetary gear support79. The planetary gear support79has support projections86which protrude from the carrier body80, between which for example the tool shaft28can be arranged or by which the tool shaft28can be held. For example the tool shaft28is held by support elements87which in turn are supported on the support projections86.

The gearbox drive41, which can also be called a drive shaft, is rotatably mounted on a pivot bearing88, in particular on a roller bearing, in the embodiments shown inFIGS. 12 to 14. The pivot bearing88is supported on an inner circumference of an opening of the support body67and is for example axially secured relative to the rotational axis D by means of a snap ring89.

In the bearing concept shown inFIG. 15, however, the support body67is rotatably mounted on the cover or the front wall46of the gearbox housing44by means of a pivot bearing90. The pivot bearing90, for example a ball bearing, needle bearing or other roller bearing (a slide bearing is also possible) is for example arranged and supported in the opening48.

An actuating device100is used to switch and actuate the gearbox40. The hollow wheel78can be adjusted in a linear manner between the setting positions P3, P4using the actuating device100. The hollow wheel78forms a first switching gear element101. The hollow wheel62can also be adjusted in a linear manner between the setting positions P1and P2using the actuating device100and is coupled to the actuating device100in order to do this. The hollow wheel62forms a second switching gear element102.

A third switching gear element103is not switched directly by the actuating device100but instead by the switching gear element102in between. The switching gear element103is provided by the hollow wheel78.

The planetary gear set60forms a components of a first and a second gear wheel arrangement104,105, seeFIG. 14. The first gear wheel arrangement104is assigned to the first switching gear element102and comprises for example the roller circumferences64of the planetary gears52. The second gear wheel arrangement105is as it were coupled or connected tightly to the first gear wheel arrangement at least in terms of the planetary gears52. Each planetary gear52has various roller circumferences63,64and therefore forms two partial planetary gears. The partial planetary gear with the roller circumference63is assigned to the hollow wheel61and therefore to the switching gear element103and the gear wheel arrangement105as a gear wheel105A. The partial planetary gear with the roller circumference64is assigned to the hollow wheel62and therefore to the switching gear element102and the gear wheel arrangement104as a gear wheel104A. The partial planetary gears are in one piece or coupled tightly to one another as a result of their design as stepped planetary gears. It is easy to imagine, however, that the partial planetary gears can also be individual planetary gears that are connected to one another in a manner which prevents rotation or are rotatable relative to one another in a different embodiment.

The switching gear element102acts on the one hand as an active switching element relative to the gear wheel arrangement104by being directly engaged with the larger roller circumferences64of the planetary gears52in the setting position P2. In the setting position P1, however, the hollow wheel62is adjusted away from the planetary gears52, in other words the inner teeth73no longer mesh with the roller circumferences64.

In the setting position P1, however, the hollow wheel62is a switch actuator for the other hollow wheel61which is held in a manner which prevents rotation by the hollow wheel62or the switching gear element102relative to the gearbox housing44which forms a gearbox holding structure44A by means of the interlocking teeth, namely the outer teeth74and therefore an anti-rotation contour93and the inner teeth73and therefore a positive-locking counter-contour94. Consequently, the switching gear element103is as it were switched by the switching gear element102.

At this point it should be noted that teeth are not absolutely essential between the switching gear elements102,103or the hollow wheels61,62. For example the switching gear element102can only adjust the switching gear element103in the direction of a positive-locking counter-contour that is fixed in the housing or locally fixed, in particular on the front wall, such that an anti-rotation contour92of the switching gear element103with the positive-locking counter-contour91can be adjusted into a hold that prevents the switching gear element103from rotating relative to the gearbox holding structure, in other words the gearbox housing44(FIG. 13). The anti-rotation contour92is for example a positive-locking projection that runs in parallel to the setting axis SA; the positive-locking counter-contour91is a corresponding positive-locking recess, for example a blind hole. Teeth as anti-rotation contours and positive-locking counter-contours are, however, advantageous.

No direct coupling between the actuating device100and in particular the actuating part110of this and the switching gear element103therefore needs to be provided to switch the gear wheel arrangement. The structure of the actuating device is therefore simpler. The gearbox40is built shorter. The actuating device100is also simpler and more comfortable to handle, as will become clearer below.

The actuating device100comprises the actuating part110with an actuating handle111. The actuating handle111is an opening33arranged on an upper side wall34of the housing11of the manual machine tool10and therefore easily accessible for a user.

Numbers1,2,3and4or other markings35can be arranged on the housing11, for example on the edge areas of the opening33, which markings are assigned to the respective switch positions S1, S2, S3and S4. The actuating handle111can be displaced and/or pivoted within the opening33. The actuating handle111can be adjusted into the region of a respective marking35, in this case therefore into a corner region of the opening33to set the switch positions S1, S2, S3and S4. Direct switching or setting of the actuating handle111from each of the switch positions S1, S2, S3and S4into each of the other switch positions S1, S2, S3and S4without setting an intermediate switch position is possible. The gearbox40can for example be adjusted directly from the switch position S1(actuating handle111is shown as a dashed line inFIG. 7) into the switch position S4(actuating handle111is shown as a solid line inFIG. 7) without stopping at the intermediate switch positions S2or S3.

The actuating handle110is provided on an upper side114of an in particular barrel-shaped or curved wall body112, the lower side113of which faces towards the gearbox housing44. A curvature of the wall body112corresponds approximately to a curvature of the circumference wall45of the gearbox housing44such that the wall body112can be moved along the circumference wall45in the manner of a cover or a cover part or wall section.

The actuating part110is arranged on a traction tine120, which in turn is pivotably mounted on the gearbox housing44in a pivotable or rotatable manner, in particular on the outer circumference of the circumference wall45about a pivot axis MA which preferably concurs with the rotational axis D of the gearbox output42. This means the actuating part110can pivot about the pivot axis MA and therefore an actuating pivot axis BS between actuating positions D1and D2.

The carrier ring120has a ring body121which is rotatably mounted in a ring guide145of the gearbox housing44. The narrow sides of the ring body121are for example guided by circumference projections146which protrude from the circumference wall45.

A linear guide123for the actuating part110is provided in the free longitudinal end areas122of the carrier ring120such that this is rotatably mounted on the carrier ring120along an actuating longitudinal axis BL between actuating positions L1and L2.

The linear guide123comprises linear guide sections124arranged directly on the longitudinal end areas122, which longitudinal guide sections are arranged at an angular distance from one another corresponding to the angular distance between the longitudinal end areas122. Consequently the actuating part110is as it were a connecting link or a binding link which connects the longitudinal end areas122of the carrier ring120to one another.

Linear guide projections115are provided on the lower side113of the actuating part110, which linear guide projections engage in the linear guide sections.

The longitudinal end areas122of the carrier ring120already have a width or a length corresponding to the actuating longitudinal axis BL such that they are in principle sufficient for the linear guidance of the actuating part110. Furthermore, the actuating part110can be guided into guide recesses, for example grooves, on the outer circumference, for example longitudinal sides and/or transverse sides, or the slot or opening33of the upper side wall34.

There is additional and improved support, however, in the form of support projections129which protrude in front of the longitudinal end areas122of the carrier ring120relative to the actuating longitudinal axis BL or the rotational axis. Further linear guide sections125are provided on the support projections122in which the linear guide projections115engage and by means of which the linear guide projections115are guided relative to the actuating longitudinal axis BL. The linear guide sections124,125are for example longitudinal grooves, the transverse width of which roughly corresponds to a transverse width of the linear guide projections115relative to the actuating longitudinal axis BL.

An embodiment could provide for guide cams to be provided on the longitudinal end areas122of the carrier ring120in the manner of the guide cams133described below in greater detail, with which a first coupling element140which in turn is connected to the switching gear element101and therefore the hollow wheel78can be driven.

The guide cams133are, however, provided on a transmission part130, which in turn can be rotated relative to the actuating pivot axis BS or a rotational axis of the carrier ring120. The transmission part130has a ring body131, on the longitudinal end areas132of which the guide cams133are provided. The longitudinal end areas132are for example designed in the manner of plate bodies. A ring slot137is provided between the longitudinal end areas on the ring body131, in other words an intermediate space between ring sections138which extend between the longitudinal end areas132.

The transmission part130is arranged in an inner space of the carrier ring120. A carrier136protrudes from a radial outer circumference of the ring body132, which carrier is coupled to a carrier126of the carrier ring120in a manner which permits movement. Fixed coupling would also be possible here. The carrier126is, however, displaceably or rotatably mounted on the carrier ring120. The carrier127is movably mounted in a cam127of the carrier ring120. The cam127extends on the carrier ring in a ring-like manner. It is provided on the ring body121. The carrier protrudes in a radial direction inwards in front of the ring body such that it can engage with the carrier136. A plug connection between the carriers126,127[sic—136] is provided, for example. The cam127is therefore arch-shaped or ring-shaped and extends about the pivot axis MA of the carrier ring120in order to pivot the carrier ring120relative to the gearbox housing44.

The carrier is spring-loaded by means of a spring arrangement128, for example a coil spring. If the carrier ring120is pivoted about the pivot axis MA, the carrier126is also moved such that supported by the spring arrangement128this rotational movement or rotational force is applied to the transmission part130which ultimately converts the rotational movement into a linear movement for the coupling element140and the switching gear element101.

The coupling element140is for example formed by a spring bow141. Longitudinal ends142of the coupling element140protrude in front of a ring section of the coupling element140in a radial direction and engage in the guide cams133in the manner of cam followers. The guide cams133are for example angular cams. A coupling part recess143, for example a ring groove, is provided on the switching gear element101in the radial direction, in which coupling part recess the coupling element140engages, in particular with the ring section144. A certain spring property also brings the elastic longitudinal ends142of the coupling element140with it such that ultimately the spring arrangement128would not be necessary.

An indentation147can be provided on the ring guide145in which the ring body131and consequently the transmission part130engage for the longitudinal end areas132of the transmission part130, resulting in a certain locking effect.

The longitudinal ends142of the coupling element140which is arranged inside the gearbox housing144protrude through slots or longitudinal grooves in front of the circumference wall45and engage in the guide cams133. If, therefore, the actuating part pivots about the actuating pivot axis BS, the carrier ring120also pivots about the pivot axis MA at the same time, wherein this pivot movement is deflected by a deflection gear135which among other things comprises the guide cams133and the coupling element140and in particular its longitudinal ends142into a linear setting movement for the setting element101between setting positions P3and P4.

Unlike in the embodiment, in principle the transfer of the linear movement of the transmission part110relative to the actuating longitudinal axis BL could be transferred directly into a linear actuating movement of a second coupling element150which is arranged between the actuating part110and the switching gear element102. In this case, however, the coupling element150is pivotably mounted about a pivot axis S such that a linear adjustment of the actuating part110along the actuating longitudinal axis BL in a direction in a linear adjustment of the setting gear element102is deflected into an opposite direction.

The coupling element150comprises a spring bow159. The coupling element150comprises an actuating section151which engages in a guide recess116on the lower side113of the actuating part110. Furthermore the actuating section151is received in a slot124A between the linear guide sections124,125of the carrier ring120.

The spring bow159or the coupling element140is pivotably mounted on the gearbox housing44about the pivot axis S. The pivot axis S is between the actuating section151and the carrier projections154on the free end areas of the coupling element150. Bearing recesses157are formed on the coupling element150between the carrier projections153in which the bearing pins156which protrude in a radial outer direction in front of the gearbox housing44or the circumference wall45engage. The bearing recesses157can be found between the actuating sections152and the carrier sections153of the coupling element150. The actuating sections152,153are as it were levers which stick out from the pivot axis S.

The carrier projections154which are for example thin wire ends engage in carrier indentations155of the switching gear element102, and consequently therefore the hollow wheel62. For example, holes or as in the embodiment grooves are provided as carrier indentations155.

The second coupling element150extends in an arch shape about the switching gear element102but is only in contact with the switching gear element102in the region of the carrier recesses154. In contrast to this, the coupling element140is ring-shaped as a result of its ring section144and engaged with the switching gear element101over a larger length.

In contrast to the coupling element140, the coupling element150is arranged outside of the gearbox housing44. Its carrier projections154stretch in an inner radial direction relative to the actuating pivot axis BS or the pivot axis MA in front of the carrier sections153and penetrate slots158on the gearbox housing44or circumference wall45such that they are engaged with the carrier indentations155of the hollow wheel62or the switching gear element102.

The actuating device100can also be locked by means of a locking arrangement160. The locking arrangement160comprises a locking part161which can engage in locking indentations164on the actuating part110, for example on the lower side113of the wall body112. The locking part161is spring-loaded by a spring162into its locking positive which engages in the locking indentations164. The spring162and preferably the locking part161are received and/or guided in a recess or on a recess163of the gearbox housing, for example a cylindrical recess. Each locking indentation164is assigned to one of the switch positions S1, S2, S3and S4of the gearbox40.

The operator can move the actuating part110into the actuating positions assigned to the respective switch positions relative to the actuating longitudinal axis BL and the actuating pivot axis BS, in which locking is expediently possible. The actuating part110can for example be locked and/or positioned in the actuating positions L1, D1to set the switch position1; in actuating positions L2, D2to set switch position S2; in actuating positions L1, D2to set the switch position S3and finally in actuating positions D2, L2to set the switch position S4.

The carrier ring120follows the movement of the actuating part110about the actuating pivot axis BS. The spring arrangement128thereby uncouples the actuating movement from the actual setting movement.

A spring system is also provided in connection with the coupling element150. For example, the carrier sections153can spring or bend in an elastic manner relative to the actuating sections151and/or152. This is achieved on the one hand by the design of the coupling element150as a spring bow159. It is also, however, facilitated or improved by the fact that the bearing recess157is formed by a turning of the spring bow159such that the carrier sections153are elastic relative to the carrier actuating sections152relative to the pivot axis S.

FIG. 15indicates that the switching gear element102can in principle also be used to couple the gear wheel arrangements104and105to one another in a manner which prevents them from rotating. For example, the switching gear element102in a setting position P2B is simultaneously engaged in both gear wheel arrangements104and105in a manner which prevents rotation and can rotate within the gearbox holding structure44A or the gearbox housing44. The switching gear element102which forms the switch actuator is therefore simultaneously engaged with both gear wheel arrangements104and105. A ring groove or another slot of the like can for example be provided in the gearbox housing to ensure rotational freedom of the switching gear element102.

The spring bow159or the coupling element150is pivotably mounted on the gearbox housing44about the pivot axis S such that a respective slide actuation of the actuating part110in a first direction is deflected into an opposite linear movement of the switching gear element102. It would be possible, however for the coupling element150for example to be coupled to the actuating part110in a fixed manner such that the above-mentioned reversal of movement does not occur or in other words the movement directions of the actuating part110, the coupling element150and the switching gear element102run in parallel.