Fastening element, shredding tool, tool holder and tool system

Abstract

The invention relates to a fastening element (10) for attaching a shredding tool (90) to a tool holder (70), a shredding tool (90) for attachment to a tool holder (70) by means of a fastening element (10), a tool holder (70) for a shredding tool (90), and furthermore a tool system (120) comprising a shredding tool (90), a tool holder (70), a fastening element (10), and a counter-fastening element (60). A rotationally secure and stable fastening element is achieved by providing a profile section that has a cross-section deviating from a circular shape and that projects at least partially beyond a shaft section.A simple, stable and twist-proof fastening of a shredding tool (90) to a tool holder (70) by means of a fastening element (10) and a fastening counter-element (60) is achieved by means of a tool system (120), wherein the profile section (20) of the fastening element (10) is received at least partially in a profile area (73) of the tool holder (70) as well as in a profile receptacle (92) of the shredding tool (90).

Description

The invention relates to a fastening element for fastening a comminution tool to a tool holder, wherein the fastening element has a head portion and a shank portion, wherein the shank portion has a threaded portion for connection to a fastening counter-element at least in an end region facing away from the head portion along a central longitudinal axis of the fastening element, wherein the cross section of the head portion protrudes at least in regions beyond the cross section of the shank portion.In particular, the fastening element can serve for fastening a comminution tool for soil working, in particular in the forest and / or agricultural sector, in recycling and / or in mining. For example, the fastening element can serve for fastening a comminution tool for a tree stump milling cutter, a mulcher, a forest milling cutter, a wood comminutor, a road milling cutter or the like.The invention further relates to a comminution tool, in particular for soil working, for example in the forest and / or agricultural sector, in recycling and / or in mining, in particular for a tree stump milling cutter, a mulcher, a forest milling cutter, a wood grinder, a path milling cutter or the like, for fastening to a tool holder by means of a fastening element, wherein the comminution tool has a receiving side for receiving on the tool holder and a side facing away from the receiving side, in particular a working side, wherein a tool passage for passing through the fastening element is provided between the receiving side and the side facing away from the receiving side.The invention also relates to a tool holder for a comminution tool, in particular for soil working, for example in the forest and / or agricultural sector, in recycling and / or in mining, in particular for a tree stump milling cutter, a mulcher, a forest milling cutter, a wood comminutor, a routing milling cutter or the like, wherein the tool holder has a receiving side for receiving the comminution tool and a side facing away from the receiving side, wherein a tool holder passage for passing a fastening element is provided between the receiving side and the side facing away from the receiving side.Finally, the invention also relates to a tool system having a comminution tool, a tool holder, a fastening element and a fastening counter-element, in particular for machining the ground, for example in the forest and / or agricultural sector, in recycling and / or in mining, in particular for a tree stump milling cutter, a mulcher, a forest milling cutter, a wood comminutor, a way milling cutter or the like.US 2017 / 0079219 A1 discloses a fastening element for fastening a cutting tool to a tool holder. The fastening element is a screw with a head section and an adjoining shank section which has an external thread at its end facing away from the head section. The external thread serves for connection to an internal thread which is provided in a bore formed in a cutting tool interface of the cutting tool oriented towards the tool holder. The cross section of the head section protrudes beyond the cross section of the shank section, so that the protruding part of the head section can be supported on a tool holder passage of the tool holder, which passage is configured as a bore. The fastening element can thus be guided through the tool holder passage and screwed into the cutting tool, as a result of which the cutting tool can be braced on the tool holder.The disadvantage of the known fastening element is that it cannot provide any anti-rotation means between the tool and the tool holder. However, comminution tools are frequently subjected during operation to forces which can cause a relative rotation between comminution tool and tool holder.Furthermore, during operation of a comminution tool, in particular in the region of the interface between comminution tool and tool holder, shear forces and bending moments can act on the fastening element. These can have a main loading direction which can be aligned at least partially in or counter to a main machining direction of the comminution tool. With a known fastening element which has a circular shank cross section, disadvantages can arise here, since such a direction-dependent force ratio cannot be taken into account in an optimized manner.It is the object of the invention to provide a fastening element of the type mentioned at the beginning which reliably at least reduces unwanted rotation between the cutting tool and the tool holder and which offers improved absorption of shear forces and bending moments.It is a further object of the invention to provide a comminution tool of the type mentioned at the beginning which can be mounted on a tool holder in a simple manner in a reliable, stable and rotationally fixed manner.It is also an object of the invention to provide a tool holder of the type mentioned at the beginning which offers a simple, stable and torque-proof receptacle of a comminution tool.Finally, it is also an object of the invention to provide a tool system which is distinguished by a simple, stable and rotationally secure fastening of a comminution tool to a tool holder by means of a fastening element and a fastening counter-element.The object relating to the fastening element is achieved in that the fastening element further has a profile section which is arranged along the central longitudinal axis between the head section and the shank section, in that the cross section of the profile section protrudes at least in regions beyond the cross section of the shank section, and in that the cross section of the profile section has a shape which deviates from the circular shape.In the context of the invention, a protrusion is to be understood as a protrusion in a direction perpendicular to a central longitudinal axis in the radial direction, for example to a central longitudinal axis of the fastening element, a central longitudinal axis of a tool passage or a central longitudinal axis of a tool holder passage. With regard to the fastening element, a protrusion of the cross section of the shank section by the cross section of the profile section is thus to be understood as a protrusion in a direction perpendicular to the central longitudinal axis of the fastening element, thus in a radial direction. Furthermore, within the scope of the invention, cross sections, for example the cross section of the shank section or the cross section of the profile section, are to be understood as cross sections in a plane perpendicular to a respective central longitudinal axis, with respect to the fastening element, thus for example in a plane perpendicular to the central longitudinal axis of the fastening element.If the cross section of the shank portion along the central longitudinal axis is not constant, for example the cross section of the threaded portion deviates from that of a non-threaded portion of the shank portion, the protrusion can be related to a cross section of the shank portion which is an average value of the transverse extension of the shank portion, but preferably to a cross section which represents a maximum transverse extension of the shank portion.Because the cross section of the profile section protrudes at least in regions beyond the cross section of the shank section, a larger cross-sectional area and / or a larger area moment of inertia can be achieved in the region of the profile section compared to the region of the shank section. In particular, if the profile section is arranged in the region of the interface between the tool holder and the comminution tool, shear stresses and / or bending moments can thus be absorbed better by the fastening element.In particular, the cross section of the shank portion can be projected by the cross section of the profile portion in regions over an angular range of radial directions with respect to the central longitudinal axis. Such an angle range can be, for example, ±15°, ± 30°, ± 45°, ± 60° with respect to a radial direction. The profile section can thus have an increased area moment of inertia at least with respect to this radial direction or the angular range about this radial direction and thus absorb bending stresses better. This radial direction can preferably be oriented in the direction of the main loading direction, so that forces occurring during operation are optimally taken into account.In other radial directions, in particular in those in which transverse forces occurring during operation are lower, for example in a direction perpendicular to the main loading direction, and / or an angular range of, for example, ±15°, ± 30°, ± 45°, ± 60° about this direction perpendicular to the main loading direction, the cross section of the profile section can have a smaller extent, for example cannot project beyond the cross section of the shank section. A material-saving and weight-reduced fastening element can thus be provided, which nevertheless meets the force conditions during operation.Because the cross section of the profile section has a shape that deviates from the circular shape, the absorption of transverse forces can be optimized, for example with respect to a main loading direction, as was described above. In addition, there is the additional advantage that with such a fastening element a securing against undesired rotation between the tool holder and the comminution tool, in particular about the central longitudinal axis, can be achieved. In this case, it can be provided in particular that the comminution tool has a profile receptacle, and that the tool holder has a profile region, wherein the profile section of the fastening element is received at least partially in the profile receptacle and the profile region, and wherein the profile receptacle and profile region are formed at least partially and / or in regions corresponding to the profile section of the fastening element. If a force acts on the comminution tool which acts on a rotation with respect to the tool holder, a torque which counteracts the rotation can be transmitted between the tool holder and the comminution tool, in particular between the profile region and the profile receptacle, via the shape of the cross section of the profile section which differs from the circular cross section.The fastening element can preferably comprise a metallic material, particularly preferably consist of such a material. In particular, the fastening element can comprise a steel, preferably consist of steel.According to a preferred variant of the invention, it is proposed that the cross section of the profile section is axially symmetrical with respect to a first radial direction oriented perpendicularly to the central longitudinal axis. This results in a simple geometry of the profile section. Furthermore, in this way, it is possible to take account of the fact that alternating forces can act on the comminution tool during operation of the comminution tool, in particular forces with alternating signs and / or forces which act on a rotation of the comminution tool with respect to the tool holder with alternating direction of rotation. With a symmetrical configuration of the cross section of the profile section, such alternating forces or force directions can be counteracted in a reliable and simple manner.In this context, it can further be provided that the cross section of the profile section is axially symmetrical with respect to a second radial direction oriented perpendicularly to the central longitudinal axis, wherein the second radial direction is oriented transversely, in particular perpendicularly to the first radial direction.A possible variant of the invention can provide that the cross section of the profile section is constant along the central longitudinal axis. In this case, it is possible to facilitate the fastening element being inserted / guided into / through a tool passage of the comminution tool and / or a tool holder passage of the tool holder. In particular, an introduction of the profile section into the profile receptacle of the comminution tool and / or into the profile region of the tool holder can be facilitated. In addition, manufacturing requirements can be reduced, in particular in terms of tolerances and / or fits of the tool system (comminution tool, tool holder, fastening element, fastening counter-element). It can also be ensured via a constant cross section of the profile section that the profile section transmits no forces, or at most low forces, along the central longitudinal axis directly to the comminution tool and / or the tool holder. A statically determined force transmission between the fastening element and the remaining components of the tool system can thus be achieved, as a result of which the design of the tool system, in particular the fastening of the comminution tool to the tool holder, is facilitated.Alternatively, it can be provided that the cross section of the profile section along the central longitudinal axis is variable. Preferably, the cross-sectional area of the profile section can increase along the central longitudinal axis in the direction of the head section. However, it is also conceivable for the cross section of the profile section to be enlarged in a region which is exposed to increased loads during operation, for example in the region of the interface between comminution tool and tool holder.The variation of the cross section of the profile section can be provided continuously or discontinuously. A continuous variation can be, in particular, a variation which has a continuous and / or differentiable profile of the transverse extent of the cross section of the profile section in a radial direction, in particular in all radial directions along the central longitudinal axis. It is in particular conceivable for the course of the transverse extension of the cross section of the profile section along the central longitudinal axis to follow a straight line which encloses an opening half angle with the central longitudinal axis. The opening half angle can be, for example, between 0° and 10°, preferably between 2° and 7°, particularly preferably 4°. In this case, in particular, an opening half angle can be provided, which leads to self-locking depending on the material pairing (fastening element with comminution tool and / or fastening element with tool holder), in such a way that the profile section can be accommodated within the profile region of the tool holder and / or the profile receptacle of the comminution tool in a self-locking manner. Such a configuration can facilitate disassembly, for example, since, despite the fastening counter-element being released from the fastening element, the fastening element and preferably the comminution tool is / are held further securely on the tool holder on account of the self-locking. An unintentional dropping of the comminution tool and a risk of damage to the comminution tool caused thereby and / or damage to other components and / or injury to a person by a dropping comminution tool can thus be at least reduced.If it is provided that a maximum extent of the cross section of the profile section along the / a first radial direction corresponds to a profile height, that a maximum extent of the cross section of the profile section in the / a second radial direction corresponds to a profile width, and that the profile width is less than the profile height, the profile section can be optimally adapted to the force conditions on the tool system (comminution tool, tool holder, fastening element, fastening counter-element).In particular, the first radial direction can correspond to a main loading direction, so that the surface moment of inertia is increased by the profile height in this direction. In the second radial direction oriented transversely, in particular perpendicularly thereto, the loads to be expected can be lower, so that a profile width which is smaller than the profile height can be provided, which can contribute to a material-saving and lighter fastening element.An advantageous further development of the invention can be such that the maximum profile height is greater than a maximum transverse extension of the shank portion in the radial direction. As mentioned above, the profile height may be the maximum extension of the cross section of the profile portion along the / a first radial direction. The cross section of the shank portion can be circular in particular, so that the maximum extent of the shank portion in the radial direction can correspond to a shank diameter. Preferably, the maximum profile height can be greater than the maximum transverse extension of the shank portion by a factor of at least 1.6 and at most 2.A maximum profile height or a maximum profile width can be understood to mean a maximum value of the profile height or profile width that the profile height or profile width assumes along the central longitudinal axis. If the cross section of the profile section along the central longitudinal axis is constant, the profile height and / or the profile width along the central longitudinal axis can be constant and thus the profile height or profile width at any point along the central longitudinal axis corresponds to the maximum profile height or maximum profile width. In the case of a variable cross section, however, regions can also result in which local profile heights and / or profile widths are less than the maximum profile height or profile width, so that the maximum profile height and / or the maximum profile width are not present everywhere on the profile section along the central longitudinal axis.The profile height which is increased compared to the transverse extent of the shank portion results in an increased area moment of inertia compared to the shank portion. The shank portion can be provided in a region which is remote from the interface between comminution tool and tool holder and is exposed to no or only slight transverse forces. Accordingly, the shank portion does not have to be adapted to the force conditions in the region of the interface, since transverse forces can be absorbed in this region in an optimized manner via the design of the profile portion, in particular via the profile height which is enlarged in relation to the shank portion. Thus, the shaft section can be designed independently of the force conditions in the region of the interface, in particular in a material-saving and / or production-optimized manner.Alternatively or additionally, it can be provided that the maximum profile height corresponds to a maximum transverse extension of the head section in the radial direction. The head section can have, in particular, a round cross section. In this case, the maximum profile height may correspond to a head diameter of the head portion.According to a preferred embodiment of the invention, it can be provided that the maximum profile width corresponds to / a maximum extent of the shank portion in the radial direction. When the cross section of the shaft portion is circular, the maximum profile width may correspond to the shaft diameter of the shaft portion. In this way, possibly tension-non-favorable cross-sectional transitions can be reduced.However, it can also be provided that the maximum profile width is greater than the maximum extent of the shank portion in the radial direction, in particular greater than the shank diameter of the shank portion. Such a configuration can provide, on the one hand, a surface moment of inertia which is increased in a plurality of directions by a cross section of the profile portion which is configured to be larger in a plurality of radial directions compared to the cross section of the shank portion. This can be advantageous in particular if the profile section is arranged in the region of the interface between comminution tool and tool holder. On the other hand, this configuration can also mean a comparatively small cross-sectional area of the shank portion, which can offer advantages in the clamping between the tool holder and the comminution tool in the sense of a stretching screw (waist screw), in particular high dynamic loads.Reliable securing against unintentional rotation between the tool holder and the comminution tool can be achieved with simple means if it is provided that the cross section of the profile section substantially has the shape of a polygon. A shape which substantially corresponds to the shape of a polygon is understood within the scope of the invention to mean a shape which, although basically corresponds to a polygon, deviates from the polygon shape in particular in the corner regions by transitions such as fillets. For example, one or more corners may be severely rounded to the extent that a side surface of the polygon is completely overlaid by the rounded portion. Preferably, however, in the case of a rounded polygon, at least one straight side section of the polygon can also be obtained at least on at least one, preferably at least two, further preferably three and particularly preferably on at least four sides.The shape of a quadrilateral, preferably the shape of a rectangle or a diamond, can be considered in particular as a polygonal shape. Advantageously, at least one corner of the polygon can have a chamfer or a rounded portion.It is also conceivable for the cross section of the profile section to have the shape of an ellipse. In this case, the maximum extent of the cross section of the profile section along the first radial direction (profile height) can correspond to the length of the major axis and / or the maximum extent of the cross section of the profile section in the second radial direction (profile width) can correspond to the length of the minor axis of the ellipse.According to an advantageous development of the invention, it is proposed that a transition section is provided along the central longitudinal axis between the shank section and the profile section, wherein the transition section has a variable cross section along the central longitudinal axis, which transition section, preferably continuously, along the central longitudinal axis from the cross section of the profile section into the cross section of the shank section. A continuous transition can be, in particular, a transition which has a continuous and / or differentiable profile of the transverse extent of the cross section of the transition section in a radial direction, in particular in all radial directions along the central longitudinal axis. As a result, jumps that are disadvantageous for the stress flow and / or rough transitions between the cross sections of the profile section and of the shank section can be avoided.According to an advantageous embodiment of the invention, it can be provided that the shank portion has a threadless portion facing the profile portion. A threadless section can have, on the one hand, an increased stiffness and a lower notch effect compared to the threaded section, which can increase the stability of the fastening element overall. On the other hand, it is however also conceivable to configure the threadless section in such a way that it has a reduced cross-sectional area and thus a reduced stiffness compared to the threaded section at least in regions along the central longitudinal axis. By such a configuration, the advantages described above in the sense of a stretching screw (waist screw) can be achieved.If it is provided that the threaded section has an external thread, the fastening counter-element can be configured in a simple manner, for example as a nut. In this case, the connection between the fastening element and the fastening counter-element can be accomplished by screwing an internal thread of the fastening counter-element to the external thread of the threaded section of the fastening element.Alternatively or additionally, it can be provided that the threaded section has a bore with an internal thread. In this case, the fastening counter-element can have an external thread, wherein the connection of the fastening element to the fastening counter-element can be effected by screwing the external thread of the fastening counter-element to the internal thread of the threaded section of the fastening element. The bore can preferably be aligned along the central longitudinal axis. A screw can be used in a simple manner as a counter-fastening element.An advantageous protection of the fastening element and / or the comminution tool against wear can be achieved if the fastening element has a hard material, in particular a hard metal, in the region of the head portion. Tungsten carbide, for example, can be used as the hard metal. In particular, a hard metal layer can be provided which is applied, in particular coated, to the fastening element in the region of the head portion, or is connected, for example, in a materially bonded manner to the fastening element as an applied molded body. Particularly advantageously, a soldered-on hard material element can be provided. Preferably, the hard material can cover at least a part of an end-side head surface of the head portion facing away from the threaded portion, in particular at least 30%, preferably at least 50%, further preferably at least 70%, particularly preferably the entire end-side head surface.A simple and stable configuration of the fastening element can be achieved in that the head portion, the profile portion, the shank portion, the threaded portion and preferably the / a transition portion form a one-piece component, in particular the fastening element is formed in one piece.Alternatively, however, it can also be provided that at least one of the sections is provided on a separate component. The separate component can be designed, for example, as a sleeve which is plugged onto one or more of the remaining sections. Advantageously, in particular the profile section can be provided on a separate component. If in this case the remaining sections each have a circular cross section, this results in simple production of these remaining sections. In this case, the profile section does not have to be secured with respect to the fastening element, since during operation it preferably only has to transmit low forces, in particular no forces, to the fastening element, but only transverse forces or moments between comminution tool and tool holder.The object relating to the comminution tool is achieved in that the tool passage has a fastening receptacle for at least partially receiving a head portion of the fastening element and / or for at least partially receiving a fastening counter-element, in that the tool passage furthermore has a profile receptacle for at least partially receiving a profile portion of the fastening element, in that the cross section of the fastening receptacle protrudes beyond the cross section of the profile receptacle at least in regions, and in that the cross section of the profile receptacle has a shape which deviates from the circular shape.Because the cross section of the profile receptacle has a shape that deviates from the circular shape, the absorption of transverse forces can be optimized, for example with respect to a main loading direction. For example, the cross section of the profile receptacle can have a greater extension in a radial direction perpendicular to a central longitudinal axis of the tool passage, in particular in the main loading direction than in other radial directions. In this region, a fastening element, in particular a profile section of a fastening element, can be accommodated, which likewise has an enlarged extent in this direction. The fastening element can thus have an increased area moment of inertia in the main loading direction, as a result of which bending loads can be absorbed better. In other directions, the extent of the cross section of the profile receptacle can be smaller, so that the comminution tool is not unnecessarily weakened.In addition, there is the additional advantage that with a cross section of the profile receptacle deviating from the circular shape, a cross section of the profile section of the fastening element likewise deviating from the circular shape can be received, so that the comminution tool can be held in a rotationally fixed manner with respect to the fastening element and advantageously with respect to the tool holder.Preferably, it can be provided that the fastening receptacle, starting from the receptacle side, follows the profile receptacle indirectly or directly along the central longitudinal axis of the tool passage in the direction of the side facing away from the receptacle side. Particularly preferably, the profile receptacle can be open toward the receptacle side. In this way, the comminution tool can be accommodated on a tool holder in such a way that the profile receptacle can interact with a profile region of the tool holder in order to create a common accommodation region for a profile section of the fastening element.If it is provided that the fastening receptacle has, at its end facing the profile receptacle, a counter-contact surface which is designed for contact with a contact surface of the fastening element and / or for contact with a fastening counter-element, the comminution tool can be braced in a simple and reliable manner by means of the fastening element. A particularly favorable force transmission between fastening element and comminution tool can be achieved here if the counter-contact surface is formed at least in regions transversely, in particular perpendicularly, to the central longitudinal axis of the tool passage.The object relating to the tool holder is achieved in that the tool holder passage has a profile region for at least partially receiving a profile section of a fastening element, and in that the cross section of the profile region has a shape which deviates from the circular shape.The object relating to the tool system is achieved in that the tool system has a comminution tool according to one of Claims 13 to 15, a tool holder according to Claim 16, a fastening element according to one of Claims 1 to 12 and a fastening counter-element, wherein the comminution tool and the tool holder are braced against one another by means of the fastening element and a fastening counter-element, wherein the profile region of the tool holder and the profile receptacle of the comminution tool are formed at least partially corresponding to the profile section of the fastening element, and wherein the profile section of the fastening element is received at least in regions both in the profile receptacle and in the profile region.The invention is explained in more detail below with reference to exemplary embodiments shown in the figures. The following are shown: FIG. 1 shows a schematic side view of a fastening element ( 10), FIG. 2 shows a schematic plan view of the fastening element ( 10) from FIG. 1 , FIG. 3 shows a schematic sectional view at position III from FIG. 1, FIG. 4 shows a schematic sectional view at position IV from FIG. 1, FIG. 5 shows a schematic side view according to position V from FIG. 1, FIGS. 6, 7 to 8 show schematic views of various exemplary embodiments, FIG. 9 shows a schematic side view of a fastening element (10) of an embodiment of a fastening element (10), FIG. 10 shows a schematic side view of a fastening element (10) of a further embodiment of a fastening element (10), FIG. 11 shows a schematic partial sectional view of a fastening element (10) of a further embodiment of a fastening element (10), FIG. 12 shows a schematic front view of a tool system ( 120), FIG. 13 shows a schematic sectional view at position XIII from FIG. 12, FIG. 14 is a schematic sectional view at position XIV from FIG. 12 ; and FIG. 15 is a schematic sectional view at position XV of FIG. 12.In FIG. 1, a schematic view of a fastening element 10 can be seen. The fastening element 10 can serve for fastening a comminution tool 90 to a tool holder 70 (see FIGS. 12, 13, 14 to 15 ). The fastening element 10 has a head portion 16 and a shank portion 32. The shank portion 32 has a threaded portion 41 at least in the end region 40 facing away from a central longitudinal axis 11 of the fastening element 10. The threaded portion 41 serves for connection to a counter-fastening element 60 (see FIGS. 13 and 15 ).As can be seen from FIGS. 1, 2, 9, 10, 13, 15, the threaded section 41 can have an external thread 42. In this case, the counter-fastening element 60 can have an internal thread which is screwed onto the external thread 42 of the fastening element 10. For example, the fastening counter member 60 may be a nut (see FIGS. 13 and 15 ).As can be seen in FIG. 11, alternatively or additionally an internal thread 45 can also be provided. The internal thread 45 can preferably be provided in a bore 43 which can be introduced into an end face 40.1 of the fastening element 10 facing away from the head portion 16. Preferably, the bore 43 can be aligned along the central longitudinal axis 11 of the fastening element 10. When the threaded portion 41 has an internal thread 45, the mating fastener 60 may have an external thread that is threaded into the internal thread 45 of the fastener 10. In this case, the fastening counter element 60 can be designed, for example, as a screw.Between the shank portion 32 and the head portion 16, the fastening element 10 further has a profile portion 20. As can be seen from the figures, the profile section 20 can preferably directly adjoin the head section 16. However, it is also conceivable for the profile section 20 to be provided at a distance from the head section 16. The cross section 27 of the profile section 20 protrudes at least in regions beyond the cross section 35 of the shank section 32. Here, a protrusion is intended to mean protrusions in a radial direction 13 perpendicular to the central longitudinal axis 11. Cross sections, for example the cross section 35 of the shank section 32 or the cross section 27 of the profile section 20, are to be understood below as cross sections in a plane perpendicular to the central longitudinal axis 11 of the fastening element 10.According to the exemplary embodiment of FIGS. 1 and 2, the projecting of the cross section 27 of the profile section 20 can be provided only in regions. It can be seen from FIG. 1 in combination with FIG. 4 that the cross section 27 of the profile section 20 protrudes beyond the cross section 35 of the shank section 32 at least in a first radial direction 13.1. Accordingly, the profile section 20 is thicker in this direction than the shank section 32 In FIG. 2, the perspective of which is rotated by 90° about the central longitudinal axis 11 compared to FIG. 1, however, it becomes clear that in a second radial direction 13.2 the cross section 27 of the profile section 20 does not project beyond the cross section 35 of the shank section 32. In this direction, the profile portion 20 is not thicker than the shank portion 32.However, it is also conceivable for the cross section 27 of the profile section 20 to completely project beyond the cross section 35 of the shank section 32. Such an embodiment is schematically shown in FIG. 8. In this case, the cross section 27 of the profile section 20 is shown with a solid line. The cross section 35 of the shank portion 32 and the cross section 16.1 of the head portion 16 are illustrated with dashed lines.It is common to the exemplary embodiments shown in the figures that the cross section 27 of the profile section 20 has a shape which deviates from the circular shape. A cross-sectional shape deviating from the circular shape can achieve a rotation prevention of the components to be connected, in the present case comminution tool 90 and tool holder 70. This will be discussed in more detail below with respect to a tool system 120.As can be seen in particular on the basis of FIGS. 4, 5, 6, 7 to 8, the cross section 27 of the profile section 20 can be axially symmetrical with respect to at least one axis oriented perpendicularly to the central longitudinal axis 11. In the present case, the cross sections 27 of the profile section 20 shown each have two axes of symmetry, namely an axis along a first radial direction 13.1 and an axis along a second radial direction 13.2. Preferably, the axes of symmetry can be arranged perpendicular to one another or the second radial direction 13.2 can be aligned perpendicular to the first radial direction 13.1.A maximum extension of the cross section 27 of the profile section 20 along the first radial direction 13.1 can be referred to as profile height 21. A maximum extension of the cross section 27 of the profile section 20 along the second radial direction 13.2 can be referred to as profile width 22. Preferably, the profile height 21 and the profile width 22 can deviate from one another, in particular the profile height 21 can be greater than the profile width 22.As can be seen in particular on the basis of FIG. 2, the profile width 22 can correspond to a transverse extent of the shank portion 32. If the shank portion 32 has a circular cross section as in the present case (see FIG. 3 ), the profile width 22 can thus correspond to a shank diameter 33. The profile height 21 can then be greater than the shank diameter 33.As can be clearly seen with reference to FIGS. 1 and 5, the profile height 21 can be greater than the shank diameter 33. If the cross section 16.1 of the head section 16 is circular, as in the present case, the profile height 21 can correspond to the head diameter 17 of the head section 16.It can be seen in FIGS. 4, 5, 6, 7 to 8 that the cross section 27 of the profile section 20 can have the shape of a rounded polygon. According to FIGS. 4, 5, 7 and 8, the polygon can be a diamond.As can be seen in particular in FIG. 4, the polygon can have straight side lines 28.1, 28.2 which merge into one another via fillets 29.1, 29.2. Fillets can in principle have radii of such a size that no straight side lines of the polygon remain. Preferably, however, at least two straight side lines 28.1, 28.2 remain. It is also conceivable for the side lines to have curvatures, for example convexly or concavely curved, independently of any fillets provided.In FIG. 6, a cross section 27 of the profile section 20 can be seen, which has the shape of a rounded rectangle. In this case, the corners are each provided with a rounded portion 29.3. The radii of the rounded portion 29.3 can be selected here as being so large, as in the present case, that, for example, the narrow sides of the rectangle no longer have straight lines, but are completely accommodated in the rounded portion 29.3.As can be seen in FIG. 5, the cross section 16.1 of the head section 16 protrudes beyond the cross section 35 of the shank section 32 at least in regions, preferably completely as in the present case. Preferably, the cross section 16.1 of the head section 16 can also project at least in regions beyond the cross section 27 of the profile section 20. In this way, a contact surface 19 can be provided on the head section 16, as can be seen in FIG. 5. The contact surface 19 can preferably be formed perpendicular to the central longitudinal axis 11 and be oriented in the direction of the end region 40 facing away and / or the threaded section 41. The contact surface 19 can be designed for the contact of the head section 16 on the one counter-contact surface 94 of a comminution tool 90 (see FIG. 15 ).A transition section 30 can be provided between the profile section 20 and the shank section 32, as shown for example in FIGS. 1 and 2. The transition section 30 can be configured such that it has a variable cross section along the central longitudinal axis 11. The cross section 27 of the profile section 20 can be transformed with the transition section 30 into the cross section 35 of the shank section 32. In particular, a continuous transition between the profile section 20 and the shank section 32 can be created with the transition section 30. A continuous transition can be designed in particular to be continuous and preferably differentiable. In other words, an outer line of the transition section 30 can have a continuous and preferably differentiable contour in a sectional plane which contains the central longitudinal axis 11.As can be seen in FIGS. 1, 2 and 11, the cross section 27 of the profile section 20 can be of constant configuration along the central longitudinal axis 11. In particular, the profile height 21 and the profile width 22 can remain constant along the central longitudinal axis 11. However, it is also conceivable for the cross section 27 of the profile section 20 to be variable along the central longitudinal axis 11. Such embodiments are shown in FIGS. 9 and 10.According to FIGS. 9 and 10, the cross section 27 of the profile section 20 can increase in the direction of the head section 16. In this case, a maximum profile height 21 and or a maximum profile width 22 can be present at an end region of the profile section 20 facing the head section 16.A variation of the cross section 27 of the profile section 20 can be provided continuously or discontinuously. In FIG. 9, an example of a continuous variation is shown. According to this example, the course of the transverse extension of the cross section 27 of the profile section 20, in particular the profile height 21 and / or the profile width 22, along the central longitudinal axis 11 can follow a straight line which encloses an opening half angle 21.1 with the central longitudinal axis 11.An example of a discontinuous variation is seen in FIG. 10. Here, an enlargement of the cross section 27 of the profile section 20 can be seen in several steps. Starting from a first profile subsection 24, a second profile subsection 26, for example, having a cross section 27 of the profile section 20 that is enlarged in comparison to the first profile subsection 24 can follow via a profile transition section 25. In particular, the profile height 21 and / or the profile width 22 of the second profile subsection 26 can be greater than that / of the first profile subsection 24.As can be seen well in FIGS. 1, 2 and 9 to 11, the shank portion 32 can have a threadless portion 36. The threadless section 36 can adjoin the threaded section 41 and preferably be provided between the head section 16 and the threaded section 41. As shown herein, the cross-section 35 of the shank portion 32 may be constant across the threaded portion 41 and the non-threaded portion 36. However, it is also conceivable that the cross section 35 of the shank portion 32 is reduced at least in regions in the region of the threadless portion 36 in order to increase the flexibility of the fastening element 10 along the central longitudinal axis 11, in particular that the threadless portion 36 is designed as a stretching shank, so that the fastening element 10 is given the advantages of a stretching screw (waist screw).It can be provided in particular that a threadless length 34 of the threadless section 36 along the central longitudinal axis 11 is greater than a thread length 47 of the thread section 41, preferably by a factor of at least 1.5, in particular of at least 2.It can also be provided that a profile length 23 of the profile section 20 along the central longitudinal axis 11 is greater than a head length 18 of the head section 16, preferably by a factor of at least 1.5, in particular of at least 2.It can also be provided that the profile length 23 is greater than a transition length 31 of the transition section 30 along the central longitudinal axis 11, preferably by a factor of at least 1.5, in particular of at least 2.The fastening element 10 can preferably be formed in one piece. As can be seen from the figures, the fastening element 10 can comprise the head section 16, the profile section 20, the transition section 30 and the shank section 32 in one piece.It can particularly preferably be provided that the fastening element 10 comprises a hard material, in particular a hard metal, in the region of the head section 16. As is indicated in FIGS. 1, 13 and 15 with dotted lines, a hard material 50 can be provided as a hard metal layer which is applied, in particular coated, to the fastening element 10 in the region of the head section 16. A soldered-on hard material element is also conceivable. As illustrated, the hard material 50 can preferably cover at least a part of an end-side head surface 16.2 of the head portion 16 facing away from the threaded portion 41, in particular as per FIGS. 1, 13 and 15 the entire end-side head surface 16.2.FIGS. 12, 13, 14 to 15 show a tool system 120 which can be used for machining the ground, in the present case for example for machining the ground by means of a tree stump milling machine. The tool system 120 comprises a comminution tool 90 and a tool holder 70, wherein the comminution tool 90 and the tool holder 70 are clamped to one another by means of a fastening element 10 and a fastening counter-element 60.The comminution tool 90 has a receiving side 95 which can serve for receiving on the tool holder 70. In particular, the receiving side 95 can have a tool contact surface 96, which can be designed for contact with a tool holder contact surface 72. Facing away from the receiving side 95, the comminution tool 90 has a side 91 facing away from the receiving side 95.The side 91 facing away from the receiving side 95 can correspond to a working side of the comminution tool 90. In particular, in the region of the side 91 facing away from the receiving side 95, a cutting region 99 for crushing material to be processed can be provided.The cutting region 99 can be formed so as to taper substantially in the feed direction 121. In particular, the comminution tool 90 can have, in the region of the side 91 facing away from the receiving side 95, a deflection surface 99.2, which is formed at an acute angle to a clearance surface 100. As shown in FIG. 13, the comminution tool 90 can have a cutting edge 99.1 in the cutting region 99, which cutting edge can form a transition between the deflection surface 99.2 and the clearance surface 100. The discharge surface 99.2 can serve to discharge comminuted material, in particular chips of comminuted wood or the like, from the machining region and thus act as a chip surface.As can be further seen from FIG. 13, the cutting region 99 and / or the discharge surface 99.2 can merge into a fastening region 104. The fastening region 104 is preferably provided in the region of the side 91 facing away from the receiving side 95. The fastening region 104 can, for example, as in the present case be substantially planar and have a surface normal which is aligned at least predominantly in the feed direction 121. Between the cutting region 99 and the fastening region 104, in particular between the deflection surface 99.2 and the fastening region 104, a transition region 105 can be provided, which can preferably provide a rounded transition between the cutting region 99 or deflection surface 99.2 and fastening region 104.The comminution tool 90 can furthermore have a tool supporting surface 103. As can be seen in FIG. 13, the tool supporting surface 103 can be designed for at least regional contact with a tool holder supporting surface 80. The tool supporting surface 103 and the tool holder supporting surface 80 can preferably be formed at least partially, in particular predominantly, perpendicular to the main loading direction 124. Thus, forces can be reliably transmitted between the comminution tool 90 and the tool holder 70, in particular in the main loading direction 124.The tool supporting surface 103 and / or the clearance surface 100 can merge into the receiving side 95, in particular into the tool contact surface 96.In the region of the receiving side 95, the comminution tool 90 can furthermore have one or more protrusions 101. The protrusions 101 can preferably protrude beyond the tool contact surface 96 and be provided spaced apart from one another on both sides of the tool passage 98. As can be seen in particular in FIG. 15, the protrusions 101 with the tool contact surface 96 can form a receiving region 106, in which the tool holder 70 can be at least partially received in the region of its receiving side 71. The protrusions 101 can preferably be spaced apart from one another along the axis of rotation of a rotor of the comminution machine and, in their longitudinal extent, be directed at least partially in the direction of the tool supporting surface 103 and / or in the direction of the axis of rotation of the rotor. In particular, the protrusions can extend from the clearance surface 100 to the tool supporting surface 103. The protrusions 101 can provide additional securement against unintentional rotation of the comminution tool 90 relative to the tool holder 70 and / or provide improved transmission of transverse forces.The comminution tool 90 can have a metallic material, preferably consist of a metallic tool, in particular of steel, preferably a hardened steel. It is conceivable for the comminution tool 90 to have a hard material, in particular a hard metal, at least in regions. Tungsten carbide, for example, can be used as the hard metal. In particular, a hard metal layer can be provided which is applied to the comminution tool 90, in particular is coated thereon, or is connected to the comminution tool 90 in a materially bonded manner, for example, as a molded body applied. Particularly advantageously, a soldered-on hard material element can be provided. Preferably, the hard material can be provided in particularly wear-loaded regions of the comminution tool 90, in particular in the cutting region 99, preferably in the region of the cutting edge 99.1 and / or the discharge surface 99.2 and / or the clearance surface 100. It is also conceivable for a hard material to be provided in the region of the transition region 105 and / or of the fastening region 104.Between the receiving side 95 and the side 91 facing away from the receiving side 95, preferably the fastening region 104, the comminution tool 90 has a tool passage 98. As can be seen from FIGS. 13 and 15, the fastening element 10 can be guided through the tool passage 98.The tool passage 98 can have a fastening receptacle 93 which can at least partially, preferably completely, receive the head section 16 of the fastening element 10. The fastening receptacle 93 can be oriented toward the side 91 facing away from the receptacle side 95, and thus in particular toward the working side of the comminution tool 90, and in particular can be open in this direction, preferably toward the fastening region 104. If the head section 16, as in the present case, has a hard material 50, the head section is well protected in this wear-loaded region.As can be further seen from FIGS. 13, 14 and 15, the tool passage 98 has a profile receptacle 92. The profile receptacle 92 is designed to partially receive the profile section 20 of the fastening element 10. For this purpose, the profile receptacle 92 is preferably at least partially, particularly preferably predominantly, formed corresponding to the profile section 20, in particular to the part of the profile section 20 which is received within the profile receptacle 92.Preferably, the fastening receptacle 93 can have a counter-contact surface 94 for contact with the contact surface 19 of the fastening element 10. As can be seen in particular in FIG. 15, the fastening receptacle 93 projects beyond the profile receptacle 92 at least in a radial direction with respect to a central longitudinal axis 98.1 of the tool passage 98, such that the contact surface 19 can be formed as a transition between the fastening receptacle 93 and the profile receptacle 92.Preferably, the fastening receptacle 93 follows the profile receptacle 92 along the central longitudinal axis 98.1 of the tool passage 98, starting from the receptacle side 95, particularly preferably directly as shown.As can be further seen from FIGS. 13 and 15, the profile receptacle 92 can be open in the direction of the receptacle side 95, in particular open into the tool contact surface 96.The tool holder 70 can, as illustrated in the present case, be designed for coupling to a driven element of a comminution machine. In the present case, the tool holder 70 has a concavely curved connecting surface 75, by means of which it can be applied to a driven rotor. There, it can be fastened, for example, in a materially integral manner, in particular by welding, or in another manner, for example by screwing.The tool holder 70 has a receiving side 71 for receiving the comminution tool 90. In particular, a tool holder contact surface 72 for contact with the tool contact surface 96 can be provided on the receiving side 71. Opposite the receiving side 71, the tool holder 70 has a side 76 facing away from the receiving side 71. A tool holder passage 78 is provided between the receiving side 71 and the side 76 facing away from the receiving side 71.As can be seen from FIGS. 13 and 15, the tool holder passage 78 is designed to allow the fastening element 10 to be passed through. Preferably, the central longitudinal axis 78.1 of the tool holder passage 78 is aligned with the central longitudinal axis 98.1 of the tool passage 98, in particular aligned along a common straight line.The tool holder passage 78 has a profile region 73 in which the profile section 20 of the fastening element 10 is partially accommodated. For this purpose, the profile region 73 is preferably at least partially, particularly preferably predominantly, formed to correspond to the profile portion 20, in particular to the part of the profile portion 20 which is accommodated within the profile region 73.The profile region 73 can be open toward the receiving side 71, in particular open into the tool holder contact surface 72. Preferably, the profile region 73 of the tool holder 70 and the profile receptacle 92 of the comminution tool 90 can thus be aligned with one another, in particular form a common receptacle region for the profile section 20 of the fastening element 10.The tool system 120 can thus be configured such that the comminution tool 90 is braced with the tool holder 70 by the fastening element 10 and the fastening counter-element 60. The fastening element 10 can be aligned with its central longitudinal axis 11 with the central longitudinal axis 98.1 of the tool passage 98 and the central longitudinal axis 78.1 of the tool holder passage 78. It can be supported with its contact surface 19 on the counter-contact surface 94 of the comminution tool 90. At its end region 40 facing away from the tool holder 70, the fastening element 10 can be supported on the sides 76 facing away from the receiving side 71 by a counter fastening element 60, in the present case a nut. This results in a secure clamping between comminution tool 90 and tool holder 70.As can be seen clearly in FIG. 13 in particular, the profile section 20 of the fastening element 10 can be accommodated both in the profile region 73 and in the profile receptacle 92. For this purpose, the profile receptacle 92 of the tool passage 98 can have a profile receptacle length 92.1 along the central longitudinal axis 98.1 of the tool passage 98, which is preferably less than the profile length 23 of the profile section 20 of the fastening element 10. This protruding partial length can be at least partially accommodated in the profile region 73 of the tool holder passage 78.In this case, the profile section 20 can be accommodated in the profile region 73 and / or profile receptacle 92 with a certain clearance perpendicular to the central longitudinal axis 11. In this way, it can be ensured that directly no axial forces are transmitted between the tool holder 70 and the comminution tool 90 from the profile section 20, so that axial forces within the fastening element 10 are introduced only or at least predominantly at the contact surface 19 and the threaded section 41. A statically determined system can thereby be achieved. However, transitional or interference fits are also conceivable.As can be further seen in FIG. 13, the one length 73.2 of the profile region 73 of the tool holder passage 78 along the central longitudinal axis 78.1 of the tool holder passage 78 can be less than the partial length of the profile section 20 of the fastening element 10 accommodated in the profile region 73. Furthermore, it can be prevented in this way that the profile section 20 is in axial contact with an end region of the profile region 73 facing away from the receiving side 71, in particular that axial forces are transmitted in this region between the profile region 73 and the profile section 20.Due to the mutually corresponding cross sections, which deviate from circular cross sections, a moment about the central longitudinal axis 11 of the fastening element 10 can be transmitted between the tool holder 70 and the comminution tool 90 via the contact surfaces, in particular via the side surfaces which contain the side lines 28.1, 28.2. Thus, an undesired rotation of these two components relative to each other can be prevented. Such a moment is schematically indicated by the force pair F 4, F 5 in FIG. 14.FIG. 13 shows a feed direction 121 of the tool system 120 during operation. This feed direction 121 corresponds to rotation during operation of the tool system 120 when mounted on a driven rotor. By the rotation, a centrifugal force F z can act on the comminution tool 90. Furthermore, by engagement in the material to be machined, a cutting force F s can act on the comminution tool 90. Both forces together act in such a way as to produce a resulting force which acts on the comminution tool 90 predominantly outwards in the radial direction with respect to the axis of rotation of the rotor. The direction of the resulting force may correspond to a main load direction 124.This resulting force can be transmitted at least partially from the comminution tool 90 to the profile section 20 of the fastening element 10, as is indicated schematically in FIG. 13 by the force F 1. The force F 1 is then supported on the tool holder 70 by the profile section 20 resting on the profile region 73, as is symbolically represented by the force F 2. By arranging the profile section 20 in such a way that it has an increased area moment of inertia in the direction of the main loading direction 124, a greater load-bearing capacity with respect to bending loads is achieved. The cross-sectional area of the profile section 20 that is enlarged compared to the shank section 32 additionally leads to a higher load-bearing capacity to shear.Thus, an increased load-bearing capacity during operation is obtained for the tool system 120, in particular an increased reliability of the fastening of the comminution tool 90 to the tool holder 70. Additional elements, for example projections and corresponding receptacles on comminution tool 90 and / or tool holder 70, which can be associated with increased manufacturing complexity, can also be dispensed with, since shear, bending and rotational loads can be reliably transmitted from fastening element 10 between comminution tool 90 and tool holder 70, in particular via profile section 20.As can be seen in particular in FIG. 15, due to the configuration according to the invention of fastening element 10, comminution tool 90 and tool holder 70, tool systems 120 with comparatively narrow tool holders 70 can also benefit from the advantages described. As illustrated in the present case, for example, a tool holder 70 can be used which is not or only insignificantly wider (in particular in a direction along the axis of rotation of the rotor) than the head section 16 of the fastening element 10, for example corresponds to the head diameter 17 or is larger by a factor than the head diameter 17, for example 1.5 or 2.To mount the comminution tool 90 on the tool holder 70, the comminution tool 90 can be brought with its receiving side 95 into the region of the receiving side 71 of the tool holder 70, in particular the tool contact surface 96 can be placed against the tool holder contact surface 72. Preferably, the central longitudinal axis 98.1 of the tool passage 98 and the central longitudinal axis 78.1 of the tool holder passage 78 can be aligned with one another, in particular aligned along a common straight line. The fastening element 10, preferably with its end region 40 facing away from the head section 16, can now be introduced from the side 91 facing away from the receiving side 95 into the tool passage 98 and the tool holder passage 78, until the contact surface 19 of the fastening element 10 comes to bear against the counter-contact surface 94 of the tool passage 98. The central longitudinal axis 11 of the fastening element 10 is preferably aligned with the central longitudinal axis 98.1 of the tool passage 98 and / or the central longitudinal axis 78.1 of the tool holder passage 78, preferably aligned along a common straight line.In particular, if the threaded section 41 has an external thread 42, the dimensions of the tool system 120 are preferably matched such that in the region of the side 76 of the tool holder 70 facing away from the receiving side 71 the facing end region 40 of the fastening element 10 protrudes, in particular at least partially the threaded section 41. Now, the fastening counter element 60, in particular a nut, can be screwed onto the threaded section 41 and first brought into contact with the side 76 of the tool holder 70 facing away from the receiving side 71 and then, for example, further tightened by means of a torque wrench in order to clamp the tool system 120 by means of the fastening element 10.If the threaded section 41 has an internal thread 45, the dimensions of the tool system 120 can be matched in such a way that the fastening element 10 does not protrude with its end region 40 facing away from the side 76 facing away from the receiving side ( 71), but instead remains set back with respect to the latter. The fastening counter-element 60, for example in the form of a screw, can then be inserted from this side into the tool holder passage 78 and finally screwed into the internal thread 45. A screw head of the fastening counter-element 60 can thus first be brought to bear against the side 76 of the tool holder 70 facing away from the receiving side 71 and then be tightened further, for example by means of a torque wrench, in order to clamp the tool system 120 by means of the fastening element 10.References included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedUS 2017 / 0079219 A1

[0006]

Claims

Fastening element (10) for fastening a comminution tool (90) to a tool holder (70), wherein the fastening element (10) has a head portion (16) and a shank portion (32), wherein the shank portion (32) has, at least in an end region (40) facing away from the head portion (16) along a central longitudinal axis (11) of the fastening element (10), a threaded portion (41) for connection to a fastening counter-element (60), wherein the cross section (16.1) of the head portion (16) protrudes beyond the cross section (35) of the shank portion (32) at least in regions, characterized in that the fastening element (10) further has a profile portion (20) which is arranged along the central longitudinal axis (11) between the head portion (16) and the shank portion (32), in that the cross section (27) of the profile portion (20) protrudes beyond the cross section (35) of the shank portion (32) at least in regions, and that the cross section (27) of the profile section (20) has a shape which deviates from the circular shape.Fastening element (10) according to Claim 1, characterized in that the cross section (27) of the profile section (20) is axially symmetrical with respect to a first radial direction (13.1) aligned perpendicularly to the central longitudinal axis (11), preferably in that the cross section (27) of the profile section (20) is axially symmetrical with respect to a second radial direction (13.2) aligned perpendicularly to the central longitudinal axis (11), wherein the second radial direction (13.2) is aligned transversely, in particular perpendicularly to the first radial direction (13.1).Fastening element (10) according to Claim 1 or 2, characterized in that the cross section (27) of the profile section (20) is constant along the central longitudinal axis (11), or in that the cross section (27) of the profile section (20) is variable along the central longitudinal axis (11), wherein the variation is provided continuously or discontinuously, wherein preferably the cross-sectional area of the profile section (20) increases along the central longitudinal axis (11) in the direction of the head section (16).Fastening element (10) according to one of Claims 1 to 3, characterized in that a maximum extent of the cross section (27) of the profile section (20) along the / a first radial direction (13.1) corresponds to a profile height (21), in that a maximum extent of the cross section (27) of the profile section (20) in the / a second radial direction (13.2) corresponds to a profile width (22), and in that the profile width (22) is less than the profile height (21).Fastening element (10) according to one of Claims 1 to 4, characterized in that a maximum extent of the cross section (27) of the profile section (20) along the / a first radial direction (13.1) corresponds to a profile height (21), in that the maximum profile height (21) is greater than a maximum transverse extent of the shank section (32) in the radial direction (13), preferably by a factor of at least 1.6 and / or at most 2, and / or in that the maximum profile height (21) corresponds to a maximum transverse extent of the head section (16) in the radial direction (13).Fastening element (10) according to one of Claims 1 to 5, characterized in that a maximum extent of the cross section (27) of the profile section (20) in the / a second radial direction (13.2) corresponds to a profile width (22), and in that the maximum profile width (22) corresponds to the / a maximum extent of the shank section (32) in the radial direction (13), or in that the maximum profile width (22) is greater than the / a maximum extent of the shank section (32) in the radial direction (13).Fastening element (10) according to one of Claims 1 to 6, characterized in that the cross section (27) of the profile section (20) substantially has the shape of a polygon, preferably the shape of a quadrilateral, in particular the shape of a rectangle or a diamond, wherein preferably at least one corner of the polygon has a chamfer or rounded portion.Fastening element (10) according to one of Claims 1 to 7, characterized in that a transition section (30) is provided along the central longitudinal axis (11) between the shank section (32) and the profile section (20), wherein the transition section (30) has a variable cross section along the central longitudinal axis (11), which transition, preferably continuously, from the cross section (27) of the profile section (20) into the cross section (35) of the shank section (32) along the central longitudinal axis (11).Fastening element (10) according to one of Claims 1 to 8, characterized in that the shank portion (32) has a threadless portion (36) facing the profile portion (20).Fastening element (10) according to one of Claims 1 to 9, characterized in that the threaded section (41) has an external thread (42), or in that the threaded section (41) has a bore (43) with an internal thread (45), the bore (43) preferably being aligned along the central longitudinal axis (11).Fastening element (10) according to one of Claims 1 to 10, characterized in that the fastening element (10) has a hard material, in particular a hard metal, in the region of the head section (16).Fastening element (10) according to one of Claims 1 to 11, characterized in that the head portion (16), the profile portion (20), the shank portion (32), the threaded portion (41) and preferably the / a transition portion (30) form a one-piece component, in particular the fastening element (10) is formed in one piece, or in that at least one of the portions (16, 20, 32, 41, 30), preferably the profile portion (20), is provided on at least one separate component, in particular a sleeve.Comminution tool (90) for fastening to a tool holder (70) by means of a fastening element (10), wherein the comminution tool (90) has a receiving side (95) for receiving on the tool holder (70) and a side (91), in particular a working side, facing away from the receiving side (95), wherein a tool passage (98) for passing through the fastening element (10) is provided between the receiving side (95) and the side (91) facing away from the receiving side (95), characterized in that the tool passage (98) has a fastening receptacle (93) for at least partially receiving a head portion (16) of the fastening element (10) and / or for at least partially receiving a fastening counter-element (60), the tool passage (98) further has a profile receptacle (92) for at least partially receiving a profile section (20) of the fastening element (10), the cross section (93.2) of the fastening receptacle (93) protrudes at least in regions beyond the cross section (92.2) of the profile receptacle (92), and the cross section (92.2) of the profile receptacle (92) has a shape which deviates from the circular shape.Comminution tool (90) according to Claim 13, characterized in that the fastening receptacle (93), starting from the receptacle side (95), follows the profile receptacle (92) indirectly or directly along the central longitudinal axis (98.1) of the tool passage (98) in the direction of the side (91) facing away from the receptacle side (95).Comminution tool (90) according to Claim 13 or 14, characterized in that the fastening receptacle (93) has, at its end facing the profile receptacle (92), a counter-contact surface (94) which is designed for contact with a contact surface (19) of the fastening element (10) and / or for contact with a fastening counter-element (60), the counter-contact surface (94) being designed at least in regions transversely, in particular perpendicularly, to the central longitudinal axis (98.1) of the tool passage (98).Tool holder (70) for a comminution tool (90), wherein the tool holder (70) has a receiving side (71) for receiving the comminution tool (90) and a side (76) facing away from the receiving side (71), wherein a tool holder passage (78) for passing through a fastening element (10) is provided between the receiving side (71) and the side (76) facing away from the receiving side (71), characterized in that the tool holder passage (78) has a profile region (73) for at least partially receiving a profile section (20) of the fastening element (10), and in that the cross section of the profile region (73) has a shape which deviates from the circular shape.Tool system (120) having a comminution tool (90) according to one of Claims 12 to 14, a tool holder (70) according to Claim 15, a fastening element (10) according to one of Claims 1 to 11 and a fastening counter-element (60), wherein the comminution tool (90) and the tool holder (70) are braced against one another by means of the fastening element (10) and a fastening counter-element (60), wherein the profile region (73) of the tool holder (70) and the profile receptacle (92) of the comminution tool (90) are formed at least partially corresponding to the profile section (20) of the fastening element (10), and wherein the profile section (20) of the fastening element (10) is received at least in regions both in the profile receptacle (92) and in the profile region (73).

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