Gear arrangement for a driven machine tool

Abstract

Gear arrangement (10) for a driven machine tool with a rotary and / or percussive driven tool that can be attached to the machine tool, comprising:- a driven shaft (12);- a drive spindle (14) for rotary driving an attached tool, wherein the drive spindle (14) has a coaxial gear ring (28), and- an intermediate shaft (20) which can transmit a drive torque from the driven shaft (12) to the drive spindle (14);and- a countershaft (30) with a coaxial gear (26) and a wobble drive device (32) connected thereto in a rotationally fixed manner, wherein the wobble drive device (32) is capable of converting a rotational movement of the countershaft (30) into a translational movement (T) and transmitting it to the drive spindle (14) for the percussive drive of the tool, characterized in that the intermediate shaft (20) has a first gear (24) which can be brought into engagement with the coaxial gear ring (28) of the drive spindle (14), and a second gear (42) which can be brought into engagement with the coaxial gear (26) of the countershaft (30), wherein the first and the second gear (24, 42) are arranged so as to be displaceable in the axial direction relative to the drive spindle (14) and the countershaft (30).

Description

[0001] The present invention relates to a gear arrangement for a driven machine tool with a rotary and / or percussive tool. Such a machine tool can, in particular, comprise a drill or impact drill or a hammer drill with or without a chisel function.

[0002] In known machine tools of this type, particularly hammer drills, a shaft (motor shaft) driven by a drive unit of the machine tool extends with its front end into the gear assembly and drives an intermediate shaft via a drive pinion. For example, German Offenlegungsschrift DE 196 51 828 A1 discloses such a hammer drill whose intermediate shaft is arranged parallel to the drilling tool axis, but at a distance from it. The hammer drill further comprises an air cushion impact mechanism and a wobble drive device that reciprocates in the direction of the drilling tool axis, the wobble bearing or wobble plate of which is mounted on the rotatably driven intermediate shaft.

[0003] The term wobble drive device refers to a rotation / translation converter device in which the rotational movement of a drive-side element is converted into a linear translational movement of an output-side element. In this case, a rotational element acts on a wobble element, referred to below as a wobble bearing, in such a way that it is driven to tilt back and forth, thereby causing another element to move linearly.

[0004] For example, as disclosed in DE 196 51 828 A1, a translational movement is transmitted to a striker pin of the air cushion impact mechanism, which in turn causes a percussive movement of the tool. Additionally, the intermediate shaft serves to transmit the drive torque from the driven shaft to the tool. For this purpose, a drive spindle of the machine tool, on which the tool to be rotated can be mounted, comprises a drill sleeve, which, via an external gear ring, engages the external toothing of a spur gear mounted on the intermediate shaft.

[0005] The overall length of the gear assembly is therefore significantly influenced by the length and position of the impact mechanism. It must be ensured that the wobble bearing does not collide with the driven shaft and / or the spur gear of the intermediate shaft. The distance required for this purpose between the driven shaft, the wobble bearing, and the spur gear of the intermediate shaft results in the gear assembly taking up a relatively large amount of space, which cannot be fully utilized.

[0006] DE 10 2008 054 458 A1 further describes a hammer drill comprising a drive motor with a motor shaft and a tool spindle operatively connected to the motor shaft. A percussion mechanism, also operatively connected to the motor shaft, is connected to the tool spindle via a single-stage gear. The single-stage gear comprises a percussion mechanism drive gear, which drives the tool spindle via a crown gear. The motor shaft of the drive motor, in turn, comprises a motor pinion, the teeth of which are operatively engaged with a spur gear of the percussion mechanism drive gear.

[0007] As further prior art, US 4,158,313 A discloses a machine tool comprising a drive spindle for rotating a tool, a coaxial gear ring that can be coupled to the drive spindle, and an intermediate shaft that can transmit drive torque from a driven shaft to the drive spindle. For this purpose, the intermediate shaft has a gear that meshes with the coaxial gear ring of the drive spindle. Furthermore, a transmission arrangement is provided, which additionally comprises a further countershaft with a gear.

[0008] These state-of-the-art gear arrangements also require a comparatively large installation space that cannot be fully utilized.

[0009] Finally, from the document EP 2 700 477 A1, a gear arrangement is known in which a particularly advantageous utilization of the available installation space is provided by the fact that the gear arrangement additionally comprises a countershaft with a gear wheel which, depending on the operating mode of the machine tool, can be brought into engagement with or out of engagement with the coaxial gear ring of the drive spindle.

[0010] Although this solution has proven itself in practice, the solution described therein cannot be applied to machine tools that, for example, have an L-shaped housing, in which, in particular, the motor axis is not parallel to the gearbox axis. Rotary hammers, in particular, have such a housing shape or such an arrangement of the gearbox and motor drive unit.

[0011] In order to provide a solution for such machines in particular, in which the available installation space can be used optimally and the installation length can thus be shortened, the present invention proposes a gear arrangement with the features of claim 1.

[0012] Accordingly, the gear assembly comprises a driven shaft, a drive spindle for rotary driving an attached tool, the drive spindle having a coaxial gear ring, and an intermediate shaft capable of transmitting drive torque from the driven shaft to the drive spindle. Furthermore, a countershaft with a coaxial gear and a wobble drive device connected thereto in a rotationally fixed manner is provided, the wobble drive device capable of converting a rotational movement of the countershaft into a translational movement and transmitting it to the drive spindle for the percussive drive of the tool.The intermediate shaft has a first gear that can be brought into engagement with the coaxial gear ring of the drive spindle, and a second gear that can be brought into engagement with the coaxial gear of the countershaft, wherein the first and second gears are arranged to be displaceable in the axial direction relative to the drive spindle and the countershaft.

[0013] The solution according to the invention also achieves that the entire gear arrangement can be shorter in the direction of the drilling tool axis because the wobble drive device and the torque transmission to the drive spindle can be spatially separated from one another due to the provision of an intermediate shaft and a countershaft.

[0014] In contrast to the solution of EP 2 700 477 A1, the solution according to the invention does not have a single coaxial gear circle which is rotatably mounted on the drive spindle and coaxial with the drill sleeve in order to engage with a gear ring of the intermediate shaft, and which, depending on its position, may or may not also be engaged with the countershaft.

[0015] A further advantage of the solution according to the invention compared to known arrangements is that the torque transmission is significantly facilitated via a non-parallel arrangement of driven shaft and output shaft, as can be provided, for example, in an L-shaped hammer drill.

[0016] Of course, the tool can be detachably attached to the machine tool. Alternatively, the invention can also be implemented in a machine tool in which the tool is not detachably attached but is permanently attached to the machine tool.

[0017] The driven shaft is driven by a drive unit, for example an electric motor or a pneumatic drive unit, and transmits the drive torque in the usual way to the intermediate shaft of the gear arrangement. The drive spindle serves to rotary drive a tool that can be mounted on the machine tool, wherein the intermediate shaft can be brought into engagement with the coaxial gear ring of the drive spindle via a first gear and can thereby transmit the drive torque from the driven shaft to the drive spindle. Because this engagement is also releasable, i.e. the first gear of the intermediate shaft can also be brought out of engagement with the coaxial gear ring of the drive spindle, it is also possible to operate the machine tool in which no torque is transmitted, as is desired, for example, when chiseling with a flat chisel.

[0018] Via the second gear of the intermediate shaft, which can be brought into engagement with the coaxial gear of the countershaft, the torque can also be transmitted to the countershaft, thereby driving the wobble drive device connected to it in a rotationally fixed manner. This can convert a rotational movement of the countershaft into a translational movement and transmit this translational movement to the drive spindle for the percussive drive of the tool. Both the first and second gears of the intermediate shaft are arranged so that they can be displaced in the axial direction (relative to the longitudinal axis of the intermediate shaft) relative to the drive spindle and the countershaft.

[0019] According to a further development of the invention, it can be provided that the intermediate shaft comprises a sliding block which is arranged on the intermediate shaft so as to be displaceable in the axial direction between at least two positions and which has the first gear and the second gear. In this embodiment, the first gear and the second gear of the intermediate shaft are therefore displaced axially together relative to the intermediate shaft and, as a result of this displacement movement, are also displaced accordingly relative to the drive spindle and the countershaft. The displacement can be released between two maximum positions, i.e. between at least two positions. Of course, one or more intermediate positions can be selected between these maximum positions, as will be described in more detail below.

[0020] It can further be provided that the gear arrangement further comprises an actuator which can be connected to an actuating element of the machine tool and is designed, in the connected state, to convert a switching movement of the actuating element into a displacement of the sliding block.

[0021] By shifting the first gear and / or the second gear, switching between different operating modes of the machine tool can be achieved. Thus, the two gears of the intermediate shaft serve not only to transmit torque, but also to switch between different operating modes of the machine tool.

[0022] A first operating mode, in which the coaxial gear ring of the drive spindle is in engagement with the first gear of the intermediate shaft and the second gear of the intermediate shaft is out of engagement with the coaxial gear of the countershaft, describes an operating mode in which the drive spindle is only driven in rotation (pure drilling operation).

[0023] In a second operating mode of the machine tool, the first gear and the second gear of the intermediate shaft are each in mesh with the corresponding coaxial gear ring of the drive spindle and the coaxial gear of the countershaft, respectively. In this operating mode, the drive spindle is thus driven not only in rotation but also in impact mode. This corresponds to the percussive drilling mode of the machine tool.

[0024] In a third operating mode, the first gear of the intermediate shaft can be disengaged from the coaxial gear ring of the drive spindle, while the second gear is engaged with the coaxial gear of the countershaft. Consequently, in this operating mode, no torque is transmitted to the drive spindle, but only a translational movement generated by the wobble drive device for the percussive drive of the tool (chiseling operation).

[0025] Using the machine tool's actuating element, the user can select between the machine tool's different operating modes. The actuating element can, for example, comprise a rotary knob, the rotary movement of which, in a known manner, causes a translational movement of the associated actuator, which in turn displaces the sliding block in the axial direction. However, alternative designs are also conceivable, such as an axially displaceable actuating element.

[0026] Because the two gears of the intermediate shaft are assigned to the sliding block and move together with it, switching between the three described operating modes can be achieved by simply moving the sliding block. This results in a comparatively simple switching mechanism, which can also save space and weight.

[0027] In particular, it can be provided that the actuator is firmly connected to the sliding block in the axial direction.

[0028] Furthermore, it can be provided that the actuator is arranged in a rotationally fixed manner within the gear arrangement and in particular has a toothed projection which can be brought into locking engagement with the coaxial gear ring of the drive spindle in a switching position of the actuator.

[0029] This additional function solves another problem known in practice, namely that during pure chiseling operation, the drive spindle should not only not be driven in rotation by the drive unit, but also be held non-rotatably, in order to ensure a defined orientation of the tool, particularly when using a flat chisel. The toothed projection can have at least one or more teeth, the outer contour of which forms a countercontour to the contour of the gear circle of the drive spindle. In this way, a reliable locking of the drive spindle is achieved by engaging the countercontour of the toothed attachment with the outer contour of the gear circle of the drive spindle.

[0030] In particular, the actuator can be arranged on the sliding block in such a way that an intermediate position is provided in which the projection of the actuator is not yet in engagement with the coaxial gear ring of the drive spindle and fixes it in a rotationally fixed manner, but in which torque is no longer transmitted from the intermediate shaft to the drive spindle because the first gear is already disengaged from the coaxial gear ring of the drive spindle. This intermediate position enables, for example, a flat chisel to be set in its desired orientation. If the actuator is then moved further and the toothed projection engages with the coaxial gear ring of the drive spindle, the flat chisel remains in its desired orientation because the drive spindle is now held in a rotationally fixed manner by the actuator, which is also arranged in a rotationally fixed manner, thus enabling defined machining with a flat chisel.

[0031] It can further be provided that the actuator, for its non-rotatable arrangement within the transmission assembly, has a first receiving area for receiving an end section of the countershaft and a second receiving area for receiving an end section of the intermediate shaft. Thus, the two receiving areas of the actuator form bearing points and enable a non-rotatable arrangement of the actuator within the transmission assembly. Components that are already required are used for this non-rotatable arrangement, which in turn saves space and weight.

[0032] In particular, it can be provided that the first receiving portion of the actuator comprises a circular recess whose inner diameter essentially corresponds to the outer diameter of the end portion of the countershaft. The recess is designed, in particular, as a through-bore to enable axial displacement of the actuator relative to the intermediate shaft.

[0033] Independently of this specific design of the first receiving section, the second receiving section of the actuator can comprise a laterally open circular recess whose inner diameter corresponds substantially to the outer diameter of the end section of the intermediate shaft and whose lateral opening encloses less than 180 angular degrees, in particular less than 160 angular degrees, for example 150 angular degrees. This laterally open circular recess can also be designed as a through-hole in order to provide the axial displaceability of the actuator in a simple manner. The lateral opening, i.e. the fact that no circumferential inner circumferential surface is provided, makes assembly easier. The end section to be received can thus be inserted laterally through this opening.In a configuration in which the lateral opening encloses an angle of less than 180 degrees, a flattened portion can also be provided on the end section to be accommodated. If the actuator is then rotated in the assembled state relative to the accommodated end section, in particular relative to the flattened portion, a release movement of the accommodated end section from the lateral opening can be prevented.

[0034] Additionally or alternatively, a preferred orientation of the lateral opening in the installed state of the actuator can ensure that rotation of the actuator about the axis of rotation of the countershaft and thus about the bearing point formed by the first receiving section of the actuator is prevented. Thus, the lateral opening is oriented such that the end section of the intermediate shaft is engaged behind by the actuator in the installed state, thus counteracting such undesired rotational movement.

[0035] Furthermore, it can be provided that the gear arrangement further comprises an air cushion impact mechanism which is connected to the drive spindle. The air cushion impact mechanism can be partially formed integrally with the drive spindle or formed separately and firmly connected to it in the assembled state. Such an air cushion impact mechanism can conventionally comprise a percussion piston, a beater, an exciter sleeve and a drill sleeve, wherein the exciter sleeve can be slidably received within the drill sleeve and is capable of forming a space with the drill sleeve which accommodates the air cushion. In a known manner, the percussion piston can be set in a reciprocating movement within the space by means of the exciter sleeve, which movement is transmitted via the beater to a tool received in the tool holder of the drive spindle.One or more parts of the striking mechanism can be formed integrally with the drive spindle or be firmly connected to it.

[0036] As already mentioned above, the driven shaft can be arranged at an angle, particularly at a right angle, to the drive spindle. This allows for a compact hammer drill with an L-shaped housing with optimal use of housing space.

[0037] Furthermore, the intermediate shaft may be provided with a ring gear connected to it in a rotationally fixed manner, which meshes with a pinion of the driven shaft. This enables a right-angled arrangement of the intermediate shaft and the driven shaft.

[0038] Finally, the present invention also relates to a machine tool with a housing, in particular of L-shaped construction, in which the housing can comprise at least a first housing part with a first longitudinal axis and a second housing with a second longitudinal axis, and in which the first and second longitudinal axes are not arranged parallel to one another, and with a gear arrangement with one or more of the features described above.

[0039] Further features and advantages of the invention will become apparent from the following description of an embodiment of the invention and from the subclaims.

[0040] The invention is described in more detail below with reference to the accompanying figures. The figures show several features of the invention in combination with one another. However, a person skilled in the art will naturally be able to consider these features separately and, if necessary, combine them into further useful sub-combinations without requiring inventive activity.

[0041] They show schematically: Fig. 1 shows a transmission arrangement according to the invention in a side view; Fig. 2 a front view of the gear arrangement according to Fig. 1; Fig. 3 a schematic representation of the gear arrangement according to the invention of the Fig. 1 and Fig. 2 in one of several different operating positions; and Fig. 4 a switching block of the transmission arrangement according to Fig. 2.

[0042] The Fig. 1 shows a gear assembly according to the invention, generally designated by reference numeral 10. The gear assembly 10 comprises a driven shaft 12, which is driven by a drive unit embodied as an electric motor M, a drive spindle 14, an intermediate shaft 20, and a countershaft 30 embodied as a wobble drive shaft. The drive spindle 14 has, at its free end 16 facing away from the driven shaft 12, a tool holder (not shown) for receiving a tool, for example a drill or chisel. Furthermore, the drive spindle 14 comprises a drill sleeve 18, which partially encompasses it. The drive spindle 14 extends in a longitudinal direction L, which coincides with a tool axis (drilling tool axis).

[0043] The intermediate shaft 20 and the wobble drive shaft 30 extend parallel to the drive spindle 14. The respective axes of rotation are arranged parallel to the longitudinal direction L and are not designated in more detail.

[0044] The intermediate shaft 20 serves in the present gear arrangement 10 to transmit a drive torque from the driven shaft 12 to the drive spindle 14. For this purpose, the intermediate shaft 20 has a ring gear 22 with a front-end toothing 22a, which engages with an external toothing 12a of the driven shaft 12. The drive torque of the electric motor M is transmitted to the intermediate shaft 20 via the external toothing 12a and the toothing 22a of the ring gear 22 (see also Fig. 3). The intermediate shaft 20 further comprises a switching block or sliding block 44, which engages positively with a spline toothing 46 on the outer circumference of the intermediate shaft 20 and is thus displaceable along the intermediate shaft 20, but is mounted on it in a rotationally fixed manner. The displacement direction of the sliding block 44 is in the Fig. 1 and Fig. 3 by the double arrow S. The sliding block 44 has a first gear ring 24 that engages with a gear ring 28 that is non-rotatably connected to the drive spindle 14. In this way, the drive torque is transmitted from the intermediate shaft 20 via the first gear ring 24 of the sliding block 44 to the gear ring 28 of the drive spindle 14.

[0045] Because the sliding block 44 is designed to be displaceable along the longitudinal axis of the intermediate shaft 20, which coincides with its axis of rotation and is thus parallel to the longitudinal axis L of the drive spindle 14, the first gear ring 24 can be brought into or out of engagement with the gear ring 28 of the drive spindle 14.

[0046] The sliding block 44 further comprises a second gear ring 42, which, depending on the position of the sliding block 44, can be brought into engagement with a gear ring 26 of the wobble drive shaft 30. Thus, with a corresponding operating position of the sliding block 44, the torque of the intermediate shaft 20 can be used not only to drive the drive spindle 14 by transmitting it via the first gear ring 24 to the gear ring 28 of the drive spindle 14, but also to drive the wobble drive shaft 30 by transmitting the torque via the second gear ring 42 to the gear ring 26 of the wobble drive shaft 30.

[0047] On the wobble drive shaft 30, which extends parallel to the intermediate shaft 20 and is arranged at a predetermined distance from it (see also Fig. 2), a wobble drive device 32 is arranged. This comprises a wobble bearing 34, which is connected in a rotationally fixed manner to the wobble drive shaft 30, as well as a connecting means 36, which is accommodated in the manner of a ball joint in a corresponding receptacle 38a of a reciprocating piston or an excitation sleeve 38. The wobble drive device 32 serves in a known manner to convert a rotational movement of the wobble drive shaft 30 into a translational movement T (cf. Fig. 3) and, if necessary, transfer this to the excitation sleeve 38 via an air spring.

[0048] Finally, the gear assembly 10 comprises a percussion mechanism 40, which can be designed, for example, as an air cushion percussion mechanism and can comprise a percussion piston, a striker, as well as the exciter sleeve 38 and a drill sleeve, wherein the exciter sleeve 38 can be slidably received within the drill sleeve and can form a space with the drill sleeve that accommodates the air cushion. In a known manner, within this space that accommodates the air cushion, the percussion piston is set into a reciprocating movement by means of the exciter sleeve 38, which is transmitted via the striker (not shown) to a tool received in the tool holder of the drive spindle 14. If the wobble drive shaft 30 is consequently driven via the gear ring 28, the wobble drive device 32 converts this rotary movement into a translatory movement T, which, with the aid of the percussion mechanism 40, generates a percussive movement of the received tool.

[0049] The following will describe the different operating modes of the gear arrangement according to the invention with particular reference to the Fig. 3. The Fig. 3 shows, in particular, an operating position in which the sliding block 44 is shown in an operating position in which the first gear ring 24 is in engagement with the gear ring 28 of the drive spindle 14, while the second gear ring 42 is in rotationally fixed engagement with the gear ring 26 of the wobble drive shaft 30. This operating position shows a percussive drilling operation (hammer drilling position), in which the tool, on the one hand, executes a rotary movement and, on the other hand, in addition to the rotary movement, also experiences a percussive movement (hammer drilling operation).

[0050] If the switching block 44 is now removed from the Fig. 3 shown position along the longitudinal axis of the intermediate shaft 20 (indicated by the double arrow S in the Fig. 3) is shifted to the right, the second gear ring 42 can be disengaged from the gear ring 26 of the wobble drive shaft 30. In this position, the wobble drive shaft 30 is no longer driven in rotation; the wobble drive device 32 is consequently stationary, so that no more translational movement is transmitted to the drive spindle 14. This operating position thus describes an operating mode in which the drive spindle 14 is only driven in rotation by means of the intermediate shaft 20 and the first gear ring 24 of the sliding block 44 (drilling position), so that a tool held in the tool holder is only driven in rotation (drilling mode).

[0051] Based on the Fig. In the operating position shown in Figure 3, however, the sliding block 44 can also be moved to the left in direction S, so that the first gear ring 24 disengages from the gear ring 28 of the drive spindle 14. In this third operating position, the second gear ring 42 remains in rotating engagement 26 with the wobble drive shaft 30, whereby the wobble drive device 32 continues to be driven and transmits a translational movement T to the drive spindle 14 (chisel position). In this position, a tool mounted on the tool holder thus only experiences a purely percussive movement, since no more torque is transmitted to the drive spindle 14 via the gear ring 28 (hammer operation or chisel operation).

[0052] In order to provide easy handling for the user and a simplified switching process, an actuator 50 designed as a switching fork 50 is additionally provided, which is displaceably mounted on the wobble drive shaft 30 at a first bearing point 52 (first receiving section of the actuator).

[0053] In order to avoid undesired rotation of the drive spindle 14 during hammer or chisel operation, the shift fork 50 also has on its outer circumference (see also Fig. 4) has a toothed section 54, the toothing of which corresponds to the external toothing of the gear ring 28. Thus, if the sliding block 44 is moved to the left for hammer or chisel operation, the shift fork 50 can be brought into rotationally fixed engagement with the gear ring 28 of the drive spindle 14.

[0054] Because the shift fork 50 is slidably mounted on the intermediate shaft 20 in a second bearing point 56 (second receiving section of the actuator), an undesired pivoting movement of the shift fork 50 about the first bearing point 52 as a result of an undesired rotational movement of the gear ring 28 is reliably prevented. As shown in the Fig. As can also be seen in Figure 4, the second bearing point 56 is provided with a lateral opening 58 that encloses an angle of less than 180 degrees. This ensures simple assembly and, at the same time, secure mounting of the shift fork 50.

[0055] As in the Fig.2, an operating element 60 is also provided, which is designed in the form of a rotary handle. If the user now turns the rotary handle 60, which in the assembled state is attached to the outside of the machine tool housing (not shown) and projects through it, the rotary movement of the rotary handle 60 is converted in a known manner via an adjusting wire 62 into a translatory movement (operating movement B) of the shift fork 50 and, connected thereto, of the sliding block 44. For this purpose, the switching wire 62 is connected in a known manner via holding structures 70, 72 to the shift fork 50 and mounted thereon.

Claims

[1] Gear arrangement (10) for a driven machine tool with a rotating and / or percussive driven tool which can be attached to the machine tool, comprising: - a driven shaft (12); - a drive spindle (14) for rotating an attached tool, the drive spindle (14) having a coaxial gear ring (28), and - an intermediate shaft (20) which is capable of transmitting a drive torque from the driven shaft (12) to the drive spindle (14); and - a countershaft (30) with a coaxial gear (26) and a wobble drive device (32) connected thereto in a rotationally fixed manner, wherein the wobble drive device (32) is capable of converting a rotational movement of the countershaft (30) into a translational movement (T) and transmitting it to the drive spindle (14) for the percussive drive of the tool, characterized byin that the intermediate shaft (20) has a first gear (24) which can be brought into engagement with the coaxial gear ring (28) of the drive spindle (14), and a second gear (42) which can be brought into engagement with the coaxial gear (26) of the countershaft (30), wherein the first and the second gear (24, 42) are arranged so as to be displaceable in the axial direction relative to the drive spindle (14) and the countershaft (30). [2] Gear arrangement (10) according to claim 1, characterized by that the intermediate shaft (20) comprises a sliding block (44) which is arranged on the intermediate shaft (20) so as to be displaceable in the axial direction between at least two positions and has the first gear (24) and the second gear (42). [3] Gear arrangement (10) according to claim 1 or 2, characterized bythat it further comprises an actuator (50) which can be connected to an actuating element (60) of the machine tool and is designed, in the connected state, to convert a switching movement of the actuating element (60) into a displacement of the sliding block (44). [4] Gear arrangement (10) according to claims 2 and 3, characterized by that the actuator (50) is firmly connected to the sliding block (44) in the axial direction. [5] Gear arrangement (10) according to claim 3 or 4, characterized by that the actuator (50) is further arranged in a rotationally fixed manner within the gear arrangement (10) and in particular has a toothed projection (54) which, in a switching position of the actuator (50), can be brought into locking engagement with the coaxial gear ring (28) of the drive spindle (14). [6] Gear arrangement (10) according to one of claims 3 to 5, characterized bythat the actuator (50) for rotationally fixed arrangement within the transmission arrangement (10) has a first receiving area for receiving an end section of the countershaft (30) and a second receiving area for receiving an end section of the intermediate shaft (20). [7] Gear arrangement (10) according to claim 6, characterized by in that the first receiving section of the actuator (50) comprises a circular recess, the inner diameter of which corresponds substantially to the outer diameter of the end section of the countershaft (30), and / or the second receiving section of the actuator (50) comprises a laterally open circular recess, the inner diameter of which corresponds substantially to the outer diameter of the end section of the intermediate shaft (20) and the lateral opening (58) of which encloses an angle of less than or equal to 180 angular degrees, in particular of less than or equal to 160 angular degrees, for example 150 angular degrees. [8] Gear arrangement (10) according to one of the preceding claims, characterized by that the lateral opening is oriented such that the end section of the intermediate shaft (20) is engaged behind by the actuator (50) in the assembled state, so that an undesired rotational movement of the actuator (50) is counteracted. [9] Gear arrangement (10) according to one of the preceding claims, characterized by that it further comprises an air cushion impact mechanism (40) which is firmly connected to the drive spindle (14). [10] Gear arrangement (10) according to one of the preceding claims, characterized by that the driven shaft (12) is arranged at an angle, in particular at a right angle, to the drive spindle (14). [11] Gear arrangement (10) according to one of the preceding claims, characterized bythat the intermediate shaft (20) has a ring gear connected thereto in a rotationally fixed manner, which is in meshing engagement with a pinion of the driven shaft (12). [12] Machine tool with a housing, in particular of L-shaped construction, in which the housing comprises at least a first housing part with a first longitudinal axis and a second housing part with a second longitudinal axis and the first and second longitudinal axes are not arranged parallel to one another, and with a gear arrangement (10) according to one of claims 1 to 11.

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