Fastening element, comminution tool, tool holder and tool system

Abstract

The invention relates to a fastening element (10) for fastening a comminution tool (90) to a tool holder (70), to a comminution tool (90) for being fastened to a tool holder (70) by means of a fastening element (10), to a tool holder (70) for a comminution tool (90), and to a tool system (120) having a comminution tool (90), a comminution tool holder (70), a fastening element (10) and a fastening counter-element (60). An anti-rotational and stable fastening element is achieved in that a profile portion is provided which has a non-circular cross-section deviating and which protrudes beyond a shaft portion at least in regions. Simple, stable and anti-rotational fastening of a comminution 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 portion (20) of the fastening element (10) is received at least in regions both in a profile region (73) of the tool holder (70) and in a profile receptacle (92) of the comminution tool (90).

Description

[0001] Fastening element, shredding tool, tool holder and tool system

[0002] The invention relates to a fastening element for attaching a shredding tool to a tool holder, wherein the fastening element has a head section and a shaft section, wherein the shaft section has at least in an end region facing away from the head section along a central longitudinal axis of the fastening element a threaded section for connection with a fastening counter-element, wherein the cross-section of the head section projects beyond the cross-section of the shaft section at least in certain areas.

[0003] In particular, the fastening element can be used to attach a shredding tool for soil cultivation, especially in forestry and / or agriculture, recycling, and / or road construction. For example, the fastening element can be used to attach a shredding tool for a stump grinder, mulcher, forestry mulcher, wood chipper, road milling machine, or the like.

[0004] The invention further relates to a shredding tool, in particular for soil cultivation, for example in forestry and / or agriculture, in recycling and / or road construction, in particular for a stump grinder, a mulcher, a forestry grinder, a wood chipper, a road grinder or the like, for attachment to a tool holder by means of a fastening element, wherein the shredding 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 the fastening element is provided between the receiving side and the side facing away from the receiving side.

[0005] The invention also relates to a tool holder for a shredding tool, in particular for soil cultivation, for example in forestry and / or agriculture, in recycling and / or road construction, in particular for a stump grinder, a mulcher, a forestry grinder, a wood chipper, a road grinder or the like, wherein the tool holder has a receiving side for receiving the shredding 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.

[0006] Ultimately, the invention also relates to a tool system comprising a shredding tool, a tool holder, a fastening element and a fastening counter-element, in particular for soil cultivation, for example in forestry and / or agriculture, in recycling and / or road construction, in particular for a stump grinder, a mulcher, a forestry milling machine, a wood chipper, a road milling machine or the like.

[0007] US Patent 2017 / 0079219 A1 discloses a fastening element for securing a cutting tool to a tool holder. The fastening element is a screw with a head section and an adjoining shank section, the shank section having an external thread at its end opposite the head section. This external thread connects to an internal thread formed in a bore oriented towards the cutting tool interface of the cutting tool. The cross-section of the head section extends beyond the cross-section of the shank section, allowing the protruding portion of the head section to bear against a bore in the tool holder. The fastening element can thus be inserted through the tool holder bore and screwed into the cutting tool, thereby clamping the cutting tool to the tool holder.

[0008] A disadvantage of the known fastening element is that it cannot provide anti-rotation protection between the tool and the tool holder. However, shredding tools are frequently subjected to forces during operation that can cause relative rotation between the shredding tool and the tool holder.

[0009] Furthermore, during the operation of a shredding tool, shear forces and bending moments can act on the fastening element, particularly in the area of ​​the interface between the shredding tool and the tool holder. These forces can have a primary load direction, which may be at least partially aligned with or against a primary machining direction of the shredding tool. Using a known fastening element with a circular shaft cross-section can present disadvantages here, as it cannot optimally accommodate such direction-dependent force relationships.

[0010] The object of the invention is to provide a fastening element of the type mentioned above that reliably reduces, at least to some extent, unwanted rotation between the cutting tool and the tool holder, and offers improved absorption of shear forces and bending moments. A further object of the invention is to provide a shredding tool of the type mentioned above that can be easily, reliably, stably, and securely mounted to a tool holder.

[0011] The object of the invention is also to provide a tool holder of the type mentioned above which offers a simple, stable and twist-proof mounting of a shredding tool.

[0012] Ultimately, the object of the invention is also to provide a tool system characterized by a simple, stable and rotationally secure fastening of a shredding tool to a tool holder by means of a fastening element and a fastening counter-element.

[0013] The problem relating to the fastening element is solved by the fastening element further comprising a profile section which is arranged along the central longitudinal axis between the head section and the shaft section, the cross-section of the profile section which at least partially exceeds the cross-section of the shaft section, and the cross-section of the profile section having a shape which deviates from the circular shape.

[0014] Within the scope of the invention, a projection is to be understood as a projection in a direction perpendicular to a central longitudinal axis in a 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 projection of the cross-section of the shank section through the cross-section of the profile section is thus to be understood, for example, as a projection in a direction perpendicular to the central longitudinal axis of the fastening element, i.e., in a radial direction.Furthermore, within the scope of the invention, cross-sections, for example the cross-section of the shaft 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, and thus, with respect to the fastening element, for example, in a plane perpendicular to the central longitudinal axis of the fastening element. If the cross-section of the shaft section is not constant along the central longitudinal axis, for example, if the cross-section of the threaded section differs from that of an unthreaded section of the shaft section, the projection can refer to a cross-section of the shaft section that represents an average value of the transverse extent of the shaft section, but preferably to a cross-section that represents a maximum transverse extent of the shaft section.

[0015] Because the cross-section of the profile section at least partially exceeds the cross-section of the shaft section, a larger cross-sectional area and / or a greater area moment of inertia can be achieved in the profile section compared to the shaft section. In particular, when the profile section is located at the interface between the tool holder and the shredding tool, shear stresses and / or bending moments can thus be better absorbed by the fastener.

[0016] In particular, the cross-section of the shaft section can be projected beyond the cross-section of the profile section over a range of radial angles with respect to the central longitudinal axis. Such an angular range can be, for example, ± 15°, ± 30°, ± 45°, or ± 60° with respect to a radial direction. Thus, the profile section can exhibit an increased area moment of inertia, at least with respect to this radial direction or the angular range around this radial direction, and therefore better absorb bending stresses. Preferably, this radial direction can be aligned with the main load direction, so that forces occurring during operation are optimally accommodated.

[0017] In other radial directions, particularly those where transverse forces occurring during operation are lower, for example, in a direction perpendicular to the main load direction, and / or within an angular range of, for example, ±15°, ±30°, ±45°, ±60° around this direction perpendicular to the main load direction, the cross-section of the profile section can have a smaller extent, for example, not exceeding the cross-section of the shaft section. This allows for a material-saving and weight-reduced fastening element that still meets the force conditions encountered during operation.

[0018] Because the cross-section of the profile section has a shape that deviates from a circle, the absorption of lateral forces can be optimized, for example, with regard to a main load direction, as described previously. Furthermore, such a fastening element offers the additional advantage of preventing unintentional rotation between the tool holder and the shredding tool, particularly around the central longitudinal axis. Specifically, the shredding tool can be provided with a profile receptacle, and the tool holder with a profile section, wherein the profile section of the fastening element is at least partially enclosed in the profile receptacle and the profile section, and wherein the profile receptacle and profile section are at least partially and / or partially corresponding to the profile section of the fastening element.If a force acts on the shredding tool that causes a rotation relative to the tool holder, a moment can be transmitted between the tool holder and the shredding tool, in particular between the profile area and the profile mount, via the shape of the cross-section of the profile section which deviates from a circular cross-section, which counteracts the rotation.

[0019] The fastening element may preferably be made of a metallic material, and more preferably consist of such a material. In particular, the fastening element may be made of steel, and more preferably consist of steel.

[0020] According to a preferred embodiment of the invention, it is proposed that the cross-section of the profile section be axially symmetric with respect to a first radial direction oriented perpendicular to the central longitudinal axis. This results in a simple geometry of the profile section. Furthermore, this design takes into account the fact that alternating forces can act on the shredding tool during operation, in particular forces with alternating signs and / or forces that cause the shredding tool to rotate relative to the tool holder in alternating directions. A symmetrical cross-section of the profile section reliably and simply counteracts such alternating forces or force directions.

[0021] In this context, it may further be provided that the cross-section of the profile section is axially symmetric with respect to a second radial direction oriented perpendicular to the central longitudinal axis, wherein the second radial direction is oriented transversely, in particular perpendicularly, to the first radial direction.

[0022] One possible embodiment of the invention provides that the cross-section of the profile section is constant along its central longitudinal axis. In this case, inserting / passing the fastening element into / through a tool passage of the shredding tool and / or a tool holder passage of the tool holder can be facilitated. In particular, inserting the profile section into the profile receptacle of the shredding tool and / or into the profile area of ​​the tool holder can be made easier. Furthermore, manufacturing requirements can be reduced, especially regarding tolerances and / or fits of the tool system (shredding tool, tool holder, fastening element, fastening counter-element).Furthermore, a constant cross-section of the profile section ensures that the profile section transmits no or only minimal forces along the central longitudinal axis directly to the shredding tool and / or the tool holder. This allows for a statically determinate force transmission between the fastening element and the other components of the tool system, thereby simplifying the design of the tool system, particularly the fastening of the shredding tool to the tool holder.

[0023] Alternatively, the cross-section of the profile section can be variable along its central longitudinal axis. Preferably, the cross-sectional area of ​​the profile section increases along its central longitudinal axis towards the head section. However, it is also conceivable that the cross-section of the profile section is enlarged in an area subject to increased loads during operation, for example, in the area of ​​the interface between the shredding tool and the tool holder.

[0024] The variation in the cross-section of the profile section can be continuous or discontinuous. A continuous variation can, in particular, be a variation that exhibits a steady and / or differentiable progression of the transverse extent of the profile section's cross-section in a radial direction, especially in all radial directions along the central longitudinal axis. It is particularly conceivable that the progression of the transverse extent of the profile section's cross-section along the central longitudinal axis follows a straight line that forms a semi-opening angle with the central longitudinal axis. The semi-opening angle can, for example, be between 0° and 10°, preferably between 2° and 7°, and most preferably 4°.In particular, an opening half-angle can be provided which, depending on the material pairing (fastening element with shredding tool and / or fastening element with tool holder), leads to a self-locking effect, such that the profile section can be self-locking within the profile area of ​​the tool holder and / or the profile receptacle of the shredding tool. Such a design can, for example, facilitate disassembly, since, despite the fastening counterpart being detached from the fastening element, the fastening element and preferably the shredding tool remain securely held on the tool holder due to the self-locking mechanism.This can at least reduce the risk of the shredding tool unintentionally falling and the resulting risk of damage to the shredding tool and / or damage to other components and / or injury to a person caused by a falling shredding tool.

[0025] 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 adapted in an optimized way to the force conditions on the tool system (crushing tool, tool holder, fastening element, fastening counter-element).

[0026] In particular, the first radial direction can correspond to a main load direction, so that the area moment of inertia is increased by the profile height in this direction. In the second radial direction, which is transverse, especially perpendicular to this, the expected loads may be lower, so that a smaller profile width compared to the profile height can be provided, which can contribute to a material-saving and lighter fastening element.

[0027] An advantageous embodiment of the invention is such that the maximum profile height is greater than the maximum transverse extent of the shaft section in the radial direction. As mentioned previously, the profile height can be the maximum extent of the cross-section of the profile section along a first radial direction. The cross-section of the shaft section can, in particular, be circular, so that the maximum extent of the shaft section in the radial direction can correspond to a shaft diameter. Preferably, the maximum profile height can be greater than the maximum transverse extent of the shaft section by a factor of at least 1.6 and at most 2.

[0028] A maximum profile height or maximum profile width can be understood as the maximum value of the profile height or width that the profile assumes along the central longitudinal axis. If the cross-section of the profile segment is constant along the central longitudinal axis, the profile height and / or the profile width can be constant along the central longitudinal axis, and thus the profile height or the profile width corresponds to the maximum profile height or maximum profile width at every point along the central longitudinal axis. In the case of a variable cross-section, however, there may be areas where 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 is not present everywhere along the profile segment along the central longitudinal axis.The increased profile height compared to the transverse extent of the shaft section results in a higher area moment of inertia relative to the shaft section. The shaft section can be positioned in an area located away from the interface between the shredding tool and the tool holder, where it is subject to no or only minimal transverse forces. Therefore, the shaft section does not need to be adapted to the force conditions in the interface area, as transverse forces in this area can be optimally absorbed through the design of the profile section, particularly through its increased profile height compared to the shaft section. Thus, the shaft section can be designed independently of the force conditions in the interface area, and in particular, designed to save material and / or optimize manufacturing.

[0029] Alternatively or additionally, it can be stipulated that the maximum profile height corresponds to the maximum transverse extent of the head section in the radial direction. The head section can, in particular, have a circular cross-section. In this case, the maximum profile height can correspond to the head diameter of the head section.

[0030] According to a preferred embodiment of the invention, the maximum profile width can correspond to the maximum radial extent of the shaft section. If the cross-section of the shaft section is circular, the maximum profile width can correspond to the shaft diameter of the shaft section. In this way, potentially stress-unfavorable cross-sectional transitions can be reduced.

[0031] However, it is also possible for the maximum profile width to be greater than the maximum radial extent of the shaft section, and in particular greater than the shaft diameter of the shaft section. Such a design can, on the one hand, offer a multi-directionally increased moment of inertia due to the profile section having a cross-section that is larger in several radial directions compared to the shaft section. This can be particularly advantageous when the profile section is located in the interface between the shredding tool and the tool holder. On the other hand, this design can also result in a comparatively small cross-sectional area for the shaft section, which, in the sense of a tension bolt (waisted bolt), can offer advantages in terms of clamping between the tool holder and the shredding tool, especially under high dynamic loads.

[0032] Reliable protection against unintentional rotation between the tool holder and the shredding tool can be achieved simply by providing that the cross-section of the profile section essentially has the shape of a polygon. Within the scope of the invention, a shape that essentially corresponds to the shape of a polygon is understood to be one that, while fundamentally a polygon, deviates from the polygonal shape, particularly in the corner regions, due to transitions such as rounding. For example, one or more corners can be highly rounded, to the extent that a side face of the polygon is completely covered by the rounding. Preferably, according to the invention, even with a rounded polygon, at least one straight side segment of the polygon can be retained on at least one, preferably at least two, more preferably three, and particularly preferably at least four sides.

[0033] Suitable polygon shapes include, in particular, quadrilaterals, preferably rectangles or rhombuses. Advantageously, at least one corner of the polygon may have a chamfer or a rounded edge.

[0034] It is also conceivable that the cross-section of the profile section has 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) to the length of the minor axis of the ellipse.

[0035] According to an advantageous embodiment of the invention, it is proposed that a transition section be provided along the central longitudinal axis between the shaft section and the profile section, wherein the transition section has a variable cross-section along the central longitudinal axis, which transitions from the cross-section of the profile section to the cross-section of the shaft section, preferably continuously. A continuous transition can, in particular, be a transition that exhibits a steady and / or differentiable progression of the transverse extent of the cross-section of the transition section in a radial direction, especially in all radial directions along the central longitudinal axis. This avoids abrupt changes and / or abrupt transitions between the cross-sections of the profile section and the shaft section that are unfavorable for the stress flow.

[0036] According to an advantageous embodiment of the invention, the shaft section can have a threadless section facing the profile section. A threadless section can, on the one hand, exhibit increased stiffness and reduced stress concentration compared to the threaded section, which can increase the overall stability of the fastening element. On the other hand, it is also conceivable to design the threadless section such that, at least in certain areas along the central longitudinal axis, it has a reduced cross-sectional area and thus reduced stiffness compared to the threaded section. Such a design can achieve the advantages described above, similar to those of a stretch bolt (waisted bolt).

[0037] If the threaded section is designed to have an external thread, the counter-fastening element can be designed simply, for example, as a nut. In this case, the connection between the fastener and the counter-fastening element can be achieved by screwing an internal thread of the counter-fastening element onto the external thread of the threaded section of the fastener.

[0038] Alternatively or additionally, the threaded section can be provided with a bore with an internal thread. In this case, the fastening element can have an external thread, and the connection between the fastening element and the fastening element can be achieved by screwing the external thread of the fastening element into 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 as the fastening element.

[0039] Advantageous protection of the fastener and / or the grinding tool against wear can be achieved if the fastener has a hard material, in particular a cemented carbide, in the head section. Tungsten carbide, for example, can be used as the cemented carbide. In particular, a cemented carbide layer can be provided, which is applied to the fastener in the head section, in particular as a coating, or is bonded to the fastener as an applied molded element, for example, by a metallurgical bond. A brazed-on hard material element can be particularly advantageous. Preferably, the hard material can cover at least a portion of an end surface of the head section facing away from the threaded section, in particular at least 30%, preferably at least 50%, more preferably at least 70%, and most preferably the entire end surface of the head.

[0040] A simple and stable design of the fastening element can be achieved by making the head section, the profile section, the shaft section, the threaded section and preferably the transition section a single component, in particular by making the fastening element a single piece.

[0041] Alternatively, at least one of the sections can be provided on a separate component. This separate component can, for example, be designed as a sleeve that is fitted onto one or more of the other sections. It is particularly advantageous for the profile section to be provided on a separate component. If, in this case, the other sections each have a circular cross-section, their manufacture is simplified. The profile section does not need to be secured against the fastening element in this case, since during operation it preferably only has to transmit minor forces, and in particular no forces to the fastening element, but only transverse forces or moments between the shredding tool and the tool holder.The problem relating to the comminution tool is solved by the tool passage having a mounting receptacle for at least partial reception of a head section of the fastening element and / or for at least partial reception of a fastening counter-element, by the tool passage further having a profile receptacle for at least partial reception of a profile section of the fastening element, by the cross-section of the mounting receptacle projecting at least partially beyond the cross-section of the profile receptacle, and by the cross-section of the profile receptacle having a shape that deviates from the circular shape.

[0042] Because the cross-section of the profile receptacle has a shape that deviates from a circle, the absorption of shear forces can be optimized, for example, with respect to a principal load direction. For instance, the cross-section of the profile receptacle can have a greater extent in a radial direction perpendicular to a central longitudinal axis of the tool passage, particularly in the principal load direction, than in other radial directions. A fastener, especially a profile section of a fastener, can be accommodated in this area, which also has a greater extent in this direction. Thus, the fastener can have a greater area moment of inertia in the principal load direction, which allows it to better absorb bending loads.In other directions, the extent of the cross-section of the profile holder can be smaller, so that the shredding tool is not unnecessarily weakened.

[0043] Furthermore, there is the additional advantage that a profile receptacle with a cross-section that deviates from the circular shape can accommodate a profile section of the fastening element that also deviates from the circular shape, so that the shredding tool can be held securely against rotation relative to the fastening element and, advantageously, relative to the tool holder.

[0044] Preferably, the mounting receptacle extends from the receiving side along the central longitudinal axis of the tool passage towards the side opposite the receiving side, either directly or indirectly, onto the profile receptacle. Particularly preferably, the profile receptacle can be open towards the receiving side. In this way, the shredding tool can be mounted on a tool holder such that the profile receptacle can interact with a profile section of the tool holder to create a common receiving area for a profile section of the mounting element.

[0045] If the mounting receptacle is designed to have a counter-contact surface at its end facing the profile receptacle, which is configured to engage a contact surface of the mounting element and / or a counter-mounting element, the shredding tool can be clamped in a simple and reliable manner using the mounting element. Particularly favorable force transmission between the mounting element and the shredding tool can be achieved if the counter-contact surface is configured at least partially transversely, and especially perpendicularly, to the central longitudinal axis of the tool passage.

[0046] The problem relating to the tool holder is solved by the fact that the tool holder passage has a profile area for at least partially receiving a profile section of a fastening element, and that the cross-section of the profile area has a shape that deviates from the circular shape.

[0047] The problem relating to the tool system is solved by the tool system comprising a shredding 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 shredding tool and the tool holder are clamped against each other by means of the fastening element and a fastening counter-element, wherein the profile area of ​​the tool holder and the profile receptacle of the

[0048] The shredding tool is designed at least partially corresponding to the profile section of the fastening element, and wherein the

[0049] The profile section of the fastening element is received both in the profile recess and at least partially in the profile area. The invention is explained in more detail below with reference to exemplary embodiments shown in the figures. The figures show:

[0050] Figure 1 shows a schematic side view of a fastening element (10),

[0051] Figure 2 shows a schematic top view of the fastening element (10) made of

[0052] Figure 1 ,

[0053] Figure 3 shows a schematic sectional view at position III from Figure 1.

[0054] Figure 4 shows a schematic sectional view at position IV from Figure 1.

[0055] Figure 5 is a schematic side view according to position V from Figure 1.

[0056] Figures 6 to 8 show schematic views of various embodiments.

[0057] Figure 9 shows a schematic side view of a fastening element (10) of an embodiment of a fastening element (10),

[0058] Figure 10 shows a schematic side view of a fastening element (10) of another embodiment of a fastening element (10),

[0059] Figure 11 shows a schematic partial sectional view of a fastening element (10) of another embodiment of a fastening element (10),

[0060] Figure 12 shows a schematic frontal view of a tool system (120),

[0061] Figure 13 shows a schematic sectional view at position XIII from Figure 12.

[0062] Figure 14 is a schematic sectional view at position XIV from Figure 12, and Figure 15 is a schematic sectional view at position XV from Figure 12.

[0063] Figure 1 shows a schematic view of a fastening element 10. The fastening element 10 can be used to attach a shredding tool 90 to a tool holder 70 (see Figures 12 to 15). The fastening element 10 has a head section 16 and a shaft section 32. The shaft section 32 has a threaded section 41 at least in the end region 40 facing away from a central longitudinal axis 11 of the fastening element 10, at least in the head section 16. The threaded section 41 serves for connection with a counter-fastening element 60 (see Figures 13 and 15).

[0064] As can be seen in Figures 1, 2, 9, 10, 13, and 15, the threaded section 41 can have an external thread 42. In this case, the fastening counterpart 60 can have an internal thread that is screwed onto the external thread 42 of the fastening element 10. For example, the fastening counterpart 60 can be a nut (see Figures 13 and 15).

[0065] As shown in Figure 11, an internal thread 45 can alternatively or additionally be provided. The internal thread 45 can preferably be provided in a bore 43, which can be formed in an end face 40.1 of the fastening element 10 facing away from the head section 16. Preferably, the bore 43 can be aligned along the central longitudinal axis 11 of the fastening element 10. If the threaded section 41 has an internal thread 45, the fastening counterpart 60 can have an external thread that is screwed into the internal thread 45 of the fastening element 10. In this case, the fastening counterpart 60 can, for example, be designed as a screw.

[0066] Between the shaft section 32 and the head section 16, the fastening element 10 also has a profile section 20. As can be seen in the figures, the profile section 20 can preferably connect directly to the head section 16. However, it is also conceivable that the profile section 20 is spaced apart from the head section 16. The cross-section 27 of the profile section 20 projects beyond the cross-section 35 of the shaft section 32, at least partially. Projection here refers to a projection in a radial direction 13 perpendicular to the central longitudinal axis 11. Cross-sections, for example, the cross-section 35 of the shaft section 32 or the cross-section 27 of the profile section 20, are to be understood in the following as cross-sections in a plane perpendicular to the central longitudinal axis 11 of the fastening element 10.

[0067] According to the embodiment shown in Figures 1 and 2, the projection of the cross-section 27 of the profile section 20 can only be provided in certain areas. Figure 1, in combination with Figure 4, shows that the cross-section 27 of the profile section 20 projects beyond the cross-section 35 of the shaft section 32 at least in a first radial direction 13.1. Therefore, the profile section 20 is thicker than the shaft section 32 in this direction. However, in Figure 2, whose perspective is rotated 90° around the central longitudinal axis 11 relative to Figure 1, 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 shaft section 32. In this direction, the profile section 20 is not thicker than the shaft section 32.

[0068] However, it is also conceivable that the cross-section 27 of the profile section 20 completely overlaps the cross-section 35 of the shaft section 32. Such an embodiment is shown schematically in Figure 8. Here, the cross-section 27 of the profile section 20 is shown with a solid line. The cross-section 35 of the shaft section 32 and the cross-section 16.1 of the head section 16 are shown with dashed lines.

[0069] The embodiments shown in the figures have in common that the cross-section 27 of the profile section 20 has a shape that deviates from a circular form. A cross-sectional shape that deviates from a circular form can prevent the components to be joined, in this case the shredding tool 90 and the tool holder 70, from rotating. This will be discussed in more detail below with regard to a tool system 120. As can be seen particularly from Figures 4 to 8, the cross-section 27 of the profile section 20 can be axially symmetrical with respect to at least one axis oriented perpendicular to the central longitudinal axis 11. In this 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 each other, or the second radial direction 13.1 can be oriented in a different direction.2 be aligned perpendicular to the first radial direction 13.1.

[0070] The maximum extent of the cross-section 27 of the profile section 20 along the first radial direction 13.1 can be referred to as the profile height 21. The maximum extent of the cross-section 27 of the profile section 20 along the second radial direction 13.2 can be referred to as the profile width 22. Preferably, the profile height 21 and the profile width 22 can differ from each other, in particular, the profile height 21 can be greater than the profile width 22.

[0071] As can be seen particularly from Figure 2, the profile width 22 can correspond to a transverse extent of the shaft section 32. If the shaft section 32 has a circular cross-section as in the present case (see Figure 3), the profile width 22 can thus correspond to a shaft diameter 33. The profile height 21 can then be larger than the shaft diameter 33.

[0072] As can be clearly seen from Figures 1 and 5, the profile height 21 can be greater than the shaft diameter 33. In particular, the profile height 21 can correspond to a transverse extent of the cross-section 16.1 of the head section 16. 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.

[0073] Figures 4 to 8 show that the cross-section 27 of the profile section 20 can have the shape of a rounded polygon. According to Figures 4, 5, 7, and 8, the polygon can be a rhombus. As can be seen particularly in Figure 4, the polygon can have straight sides 28.1, 28.2 that transition into each other via radii 29.1, 29.2. In principle, the radii can be so large that no straight sides of the polygon remain. Preferably, however, at least two straight sides 28.1, 28.2 remain. It is also conceivable that the sides have curvatures, for example, convex or concave, regardless of any radii provided.

[0074] Figure 6 shows a cross-section 27 of the profile section 20, which has the shape of a rounded rectangle. The corners are each provided with a radius 29.3. The radii of the radius 29.3 can be chosen to be so large, as in the present case, that, for example, the narrow sides of the rectangle no longer have straight lines, but are completely enclosed within the radius 29.3.

[0075] As can be seen in Figure 5, the cross-section 16.1 of the head section 16 projects beyond the cross-section 35 of the shaft section 32, at least partially, and preferably completely as shown here. Preferably, the cross-section 16.1 of the head section 16 can also project beyond the cross-section 27 of the profile section 20, at least partially. In this way, a contact surface 19 can be provided on the head section 16, as can be seen in Figure 5. The contact surface 19 can preferably be formed perpendicular to the central longitudinal axis 11 and oriented towards the opposite end region 40 and / or the threaded section 41. The contact surface 19 can be designed to allow the head section 16 to abut a counter-contact surface 94 of a shredding tool 90 (see Figure 15).

[0076] A transition section 30 can be provided between the profile section 20 and the shaft section 32, as shown, for example, in Figures 1 and 2. The transition section 30 can be designed such that it has a variable cross-section along the central longitudinal axis 11. The transition section 30 allows the cross-section 27 of the profile section 20 to be transformed into the cross-section 35 of the shaft section 32. In particular, the transition section 30 can create a continuous transition between the profile section 20 and the shaft section 32. A continuous transition can be designed to be continuous and preferably differentiable. In other words, an outer line of the transition section 30 in a section plane that includes the central longitudinal axis 11 can have a continuous and preferably differentiable contour.

[0077] As can be seen in Figures 1, 2, and 11, the cross-section 27 of the profile section 20 can be constant along the central longitudinal axis 11. In particular, the profile height 21 and profile width 22 can remain constant along the central longitudinal axis 11. However, it is also conceivable that the cross-section 27 of the profile section 20 is variable along the central longitudinal axis 11. Such configurations are shown in Figures 9 and 10.

[0078] According to Figures 9 and 10, the cross-section 27 of the profile section 20 can increase in the direction towards 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.

[0079] A variation of the cross-section 27 of the profile section 20 can be continuous or discontinuous. Figure 9 shows an example of a continuous variation. According to this example, the course of the transverse extent of the cross-section 27 of the profile section 20, in particular the profile height 21 and / or the profile width 22, can follow a straight line along the central longitudinal axis 11, which forms an opening semi-angle 21.1 with the central longitudinal axis 11.

[0080] An example of discontinuous variation is shown in Figure 10. Here, the cross-section 27 of the profile section 20 is enlarged in several stages. Starting from a first profile subsection 24, a second profile subsection 26 with a larger cross-section 27 of the profile section 20 compared 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 those of the first profile subsection 24.

[0081] As can be clearly seen in Figures 1, 2, and 9 to 11, the shank section 32 can have an unthreaded section 36. The unthreaded section 36 can adjoin the threaded section 41 and is preferably located between the head section 16 and the threaded section 41. As shown here, the cross-section 35 of the shank section 32 can be constant over the threaded section 41 and the unthreaded section 36. However, it is also conceivable that the cross-section 35 of the shank section 32 is reduced, at least partially, in the area of ​​the unthreaded section 36 in order to increase the flexibility of the fastener 10 along the central longitudinal axis 11, in particular that the unthreaded section 36 is designed as an expansion shank, so that the fastener 10 has the advantages of an expansion bolt (waisted bolt).

[0082] 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 threaded length 47 of the threaded section 41, preferably by a factor of at least 1.5, in particular by at least 2.

[0083] 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 by at least 2.

[0084] 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 by at least 2.

[0085] 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 is particularly preferred that the fastening element 10 has a hard material, in particular a cemented carbide, in the area of ​​the head section 16. As indicated by dotted lines in Figures 1, 13, and 15, a hard material 50 can be provided as a cemented carbide layer applied, in particular coated, to the fastening element 10 in the area of ​​the head section 16. A brazed-on hard material element is also conceivable. Preferably, the hard material 50 can cover at least a part of an end surface 16.2 of the head section 16 facing away from the threaded section 41, in particular, as shown in Figures 1, 13, and 15, the entire end surface 16.2.

[0086] Figures 12 to 15 show a tool system 120 that can be used for soil cultivation, in this case, for example, for soil cultivation using a stump grinder. The tool system 120 comprises a shredding tool 90 and a tool holder 70, wherein the shredding tool 90 and the tool holder 70 are clamped together by means of a fastening element 10 and a counter-fastening element 60.

[0087] The shredding tool 90 has a receiving side 95 which can be used for mounting on the tool holder 70. In particular, the receiving side 95 can have a tool contact surface 96 which can be designed to abut a tool holder contact surface 72. Away from the receiving side 95, the shredding tool 90 has a side 91 facing away from the receiving side 95.

[0088] The side 91 facing away from the receiving side 95 can correspond to a working side of the shredding tool 90. In particular, a cutting area 99 for shredding material to be processed can be provided in the area of ​​the side 91 facing away from the receiving side 95.

[0089] The cutting area 99 can be essentially tapered in the feed direction 121. In particular, the shredding tool 90 can have a deflecting surface 99.2 on the side 91 facing away from the receiving side 95, which is formed at an acute angle to a clearance surface 100. As shown in Figure 13, the shredding tool 90 can have a cutting edge 99.1 in the cutting area 99, which can form a transition between the deflecting surface 99.2 and the clearance surface 100. The deflecting surface 99.2 can serve to deflect shredded material, in particular chips from shredded wood or the like, from the processing area and thus act as a chipping surface.

[0090] As can be further seen in Figure 13, the cutting area 99 and / or the deflecting surface 99.2 can transition into a mounting area 104. Preferably, the mounting area 104 is provided in the area of ​​the side 91 facing away from the receiving side 95. The mounting area 104 can, for example, be substantially planar as shown here and have a surface normal that is oriented at least predominantly in the feed direction 121. A transition area 105 can be provided between the cutting area 99 and the mounting area 104, in particular between the deflecting surface 99.2 and the mounting area 104, which preferably provides a rounded transition between the cutting area 99 or deflecting surface 99.2 and the mounting area 104.

[0091] The shredding tool 90 can further comprise a tool support surface 103. As can be seen in Figure 13, the tool support surface 103 can be designed to bear at least partially against a tool holder support surface 80. Preferably, the tool support surface 103 and the tool holder support surface 80 can be configured at least partially, and in particular predominantly, perpendicular to the main load direction 124. Thus, forces, especially in the main load direction 124, can be reliably transmitted between the shredding tool 90 and the tool holder 70.

[0092] The tool support surface 103 and / or the clearance surface 100 can transition into the receiving surface 95, in particular into the tool contact surface 96. In the area of ​​the receiving surface 95, the shredding tool 90 can further have one or more projections 101. The projections 101 can preferably extend beyond the tool contact surface 96 and be spaced apart from each other on both sides of the tool passage 98. As can be seen particularly in Figure 15, the projections 101 can form a receiving area 106 with the tool contact surface 96, in which the tool holder 70 can be at least partially received in the area of ​​its receiving surface 71. The projections 101 can preferably be spaced apart from each other along the axis of rotation of a rotor of the shredding machine and, in their longitudinal extent, be directed at least partially towards the tool support surface 103 and / or towards the axis of rotation of the rotor.In particular, the projections can extend from the clearance surface 100 to the tool support surface 103. The projections 101 can provide additional protection against unintentional rotation of the shredding tool 90 relative to the tool holder 70 and / or provide improved transmission of lateral forces.

[0093] The comminution tool 90 can be made of a metallic material, preferably consisting of a metallic tool, in particular of steel, preferably hardened steel. It is conceivable that the comminution tool 90 comprises a hard material, in particular a cemented carbide, at least in certain areas. Tungsten carbide, for example, can be used as the cemented carbide. In particular, a cemented carbide layer can be provided, which is applied to the comminution tool 90, in particular as a coating, or which is bonded to the comminution tool 90 as an applied shaped element, for example, by a material bond. A brazed-on hard material element can be particularly advantageous. Preferably, the hard material can be provided in areas of the comminution tool 90 that are subject to particularly high wear, in particular in the cutting area 99, preferably in the area of ​​the cutting edge 99.1 and / or the deflecting surface 99.2 and / or the clearance surface 100.It is also conceivable that a hard material is provided in the area of ​​the transition zone 105 and / or the fastening zone 104.

[0094] Between the receiving side 95 and the side 91 facing away from the receiving side 95, preferably the mounting area 104, the shredding tool 90 has a tool passage 98. As can be seen in Figures 13 and 15, the mounting element 10 can be guided through the tool passage 98.

[0095] The tool passage 98 can have a mounting receptacle 93 that can at least partially, and preferably completely as in the present case, receive the head section 16 of the fastening element 10. The mounting receptacle 93 can be oriented towards the side 91 facing away from the receiving side 95, and thus in particular towards the working side of the shredding tool 90, and in particular be open in this direction, preferably towards the fastening area 104. If the head section 16 has a hard material 50, as in the present case, the head area is well protected in this wear-prone area.

[0096] As can be seen in Figures 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, and particularly preferably predominantly, designed to correspond to the profile section 20, especially to the part of the profile section 20 that is received within the profile receptacle 92.

[0097] Preferably, the mounting receptacle 93 can have a counter-bearing surface 94 for contact with the bearing surface 19 of the fastening element 10. As can be seen particularly in Figure 15, the mounting 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, so that the bearing surface 19 can be designed as a transition between the mounting receptacle 93 and the profile receptacle 92.

[0098] Preferably, the mounting receptacle 93 follows the profile receptacle 92 along the central longitudinal axis 98.1 of the tool passage 98, starting from the receiving side 95, particularly preferably directly as shown. As can be further seen in Figures 13 and 15, the profile receptacle 92 can be open in the direction of the receiving side 95, in particular leading into the tool contact surface 96.

[0099] The tool holder 70 can be designed, as shown here, for coupling to a driven element of a comminution machine. In this case, the tool holder 70 has a concavely curved mounting surface 75 by means of which it can be mounted on a driven rotor. There, it can be fastened, for example, by welding, or in another way, for example, by bolting.

[0100] The tool holder 70 has a receiving side 71 for receiving the shredding tool 90. In particular, a tool holder contact surface 72 for 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.

[0101] As can be seen in Figures 13 and 15, the tool holder passage 78 is designed to allow the fastening element 10 to pass through it. 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 along a common straight line.

[0102] The tool holder passage 78 has a profile area 73 in which the profile section 20 of the fastening element 10 is partially received. For this purpose, the profile area 73 is preferably at least partially, and particularly preferably predominantly, formed to correspond to the profile section 20, especially to the part of the profile section 20 that is received within the profile area 73. The profile area 73 can be open towards the receiving side 71, in particular leading into the tool holder contact surface 72. Preferably, the profile area 73 of the tool holder 70 and the profile receptacle 92 of the shredding tool 90 can thus be aligned with each other, in particular forming a common receiving area for the profile section 20 of the fastening element 10.

[0103] The tool system 120 can therefore be designed such that the shredding tool 90 is clamped to the tool holder 70 by the fastening element 10 and the counter-fastening 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 bear against the counter-bearing surface 94 of the shredding tool 90 with its contact surface 19. At its far end 40, the fastening element 10 can be supported against the tool holder 70 by a counter-fastening element 60, in this case a nut, on the side 76 facing away from the receiving side 71. This results in a secure clamping between the shredding tool 90 and the tool holder 70.

[0104] As can be clearly seen in Figure 13, the profile section 20 of the fastening element 10 can be received in both the profile area 73 and the profile receptacle 92. For this purpose, the profile receptacle 92 of the tool passage 98 can have a profile receiving 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. In particular, a partial length of the profile section 20 can project beyond the receiving side 95 of the shredding tool 90 in this way. This projecting partial length can be received at least partially in the profile area 73 of the tool holder passage 78.

[0105] The profile section 20 can be received in profile area 73 and / or profile receptacle 92 with a certain amount of play perpendicular to the central longitudinal axis 11. This ensures that no axial forces are directly transmitted between the tool holder 70 and the shredding tool 90 by 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. This allows for a statically determinate system. However, transition or interference fits are also conceivable.

[0106] As can be further seen in Figure 13, the length 73.2 of the profile area 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 area 73. This additional length 73.2 of the profile area 73 can, for example, serve to accommodate the transition section 30. Furthermore, this prevents the profile section 20 from being in axial contact with an end region of the profile area 73 facing away from the receiving side 71, and in particular prevents axial forces from being transmitted between the profile area 73 and the profile section 20 in this region.

[0107] Due to the 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 shredding tool 90 via the contact surfaces, in particular via the side surfaces that include the side lines 28.1, 28.2. This prevents unintentional rotation of these two components relative to each other. Such a moment is schematically indicated by the force couple F4, F5 in Figure 14.

[0108] Figure 13 shows a feed direction 121 of the tool system 120 during operation. This feed direction 121 corresponds to a rotation during operation of the tool system 120 when it is mounted on a driven rotor. The rotation can exert a centrifugal force Fz on the shredding tool 90. Furthermore, a cutting force Fs can act on the shredding tool 90 by engaging with the material being processed. Both forces combine to form a resultant force that acts predominantly radially outwards on the shredding tool 90 with respect to the axis of rotation of the rotor. The direction of the resultant force can correspond to a main load direction 124.

[0109] This resulting force can be at least partially transferred from the shredding tool 90 to the profile section 20 of the fastening element 10, as schematically indicated by the force Fi in Figure 13. The force F1 is then supported at the tool holder 70 by the contact of the profile section 20 with the profile area 73, as symbolically represented by the force F2. By arranging the profile section 20 such that it has an increased area moment of inertia in the direction of the main load direction 124, greater resistance to bending loads is achieved. Furthermore, the larger cross-sectional area of ​​the profile section 20 compared to the shaft section 32 leads to higher shear strength.

[0110] This results in increased operational load-bearing capacity for the tool system 120, in particular increased reliability of the attachment of the shredding tool 90 to the tool holder 70. Furthermore, the rotationally fixed design of the fastening element 10 simplifies assembly. Additional elements, such as projections and corresponding receptacles on the shredding tool 90 and / or tool holder 70, which can involve increased manufacturing effort, are also unnecessary, since shear, bending, and torsional loads can be reliably transmitted by the fastening element 10 between the shredding tool 90 and the tool holder 70, especially via the profile section 20.

[0111] As can be seen particularly in Figure 15, the design of the fastening element 10, the shredding tool 90, and the tool holder 70 according to the invention also allows tool systems 120 with comparatively narrow tool holders 70 to benefit from the described advantages. As shown here, for example, a tool holder 70 can be used which is not, or only insignificantly, wider (particularly in one 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 than the head diameter 17 by a factor of, for example, 1.5 or 2.

[0112] To mount the shredding tool 90 to the tool holder 70, the shredding tool 90 can be brought with its receiving side 95 into the area of ​​the receiving side 71 of the tool holder 70, in particular the tool contact surface 96 being 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 each other, in particular along a common straight line. Now the fastening element 10, preferably with its end region 40 facing away from the head section 16 leading, can be inserted 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 into contact with the opposing 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 along a common straight line.

[0113] In particular, if the threaded section 41 has an external thread 42, the dimensions of the tool system 120 are preferably designed such that, in the area of ​​the side 76 of the tool holder 70 facing away from the receiving side 71, the end region 40 of the fastening element 10 protrudes, in particular at least partially the threaded section 41. The counter-fastening element 60, in particular a nut, can then be screwed onto the threaded section 41 and initially brought into contact with the side 76 of the tool holder 70 facing away from the receiving side 71, and then, for example, tightened further using a torque wrench to clamp the tool system 120 by means of the fastening element 10.

[0114] If the threaded section 41 has an internal thread 45, the dimensions of the tool system 120 can be designed so that the fastening element 10, with its end region 40 facing away from the receiving side (71), does not protrude beyond the side 76 facing away from the receiving side (71), but remains recessed relative to it. The counter-fastening element 60, for example in the form of a screw, can then be inserted from this side into the tool holder passage 78 and ultimately screwed into the internal thread 45. The screw head of the counter-fastening element 60 can thus first be brought into contact with the side 76 of the tool holder 70 facing away from the receiving side 71 and then, for example, tightened further using a torque wrench to clamp the tool system 120 by means of the fastening element 10.

Claims

Claims 1. Fastening element (10) for fastening a crushing tool (90) to a tool holder (70), wherein the fastening element (10) has a head section (16) and a shaft section (32), wherein the shaft section (32) has at least in an end region (40) facing away from the head section (16) along a central longitudinal axis (11) of the fastening element (10) a threaded section (41) for connection with a fastening counter element (60), wherein the cross-section (16.1 ) of the head section (16) overhangs the cross-section (35) of the shaft section (32) at least in some areas, characterized in that the fastening element (10) further comprises a profile section (20) which is arranged along the central longitudinal axis (11 ) between the head section (16) and the shaft section (32), that the cross-section (27) of the profile section (20) overhangs the cross-section (35) of the shaft section (32) at least in some areas, and that the cross-section (27) of the profile section (20) has a shape which deviates from the circular shape.

2. Fastening element (10) according to claim 1, characterized in that the cross-section (27) of the profile section (20) is axially symmetric with respect to a first radial direction (13.1) oriented perpendicular to the central longitudinal axis (11), preferably that the cross-section (27) of the profile section (20) is axially symmetric with respect to a second radial direction (13.2) oriented perpendicular to the central longitudinal axis (11), wherein the second radial direction (13.2) is oriented transversely, in particular perpendicularly to the first radial direction (13.1).

3. Fastening element (10) according to claim 1 or 2, characterized in that, that the cross-section (27) of the profile section (20) is constant along the central longitudinal axis (11), or 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 towards the head section (16).

4. 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), 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 that the profile width (22) is less than the profile height (21).

5. 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), that the maximum profile height (21) is greater than a maximum transverse extent of the shaft section (32) in the radial direction (13), preferably by a factor of at least 1.6 and / or at most 2, and / or that the maximum profile height (21) corresponds to a maximum transverse extent of the head section (16) in the radial direction (13).

6. 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 a second radial direction (13.2) corresponds to a profile width (22), and that the maximum profile width (22) corresponds to the maximum extent of the shaft section (32) in the radial direction (13), or that the maximum profile width (22) is greater than the / a maximum extension of the shaft section (32) in the radial direction (13).

7. Fastening element (10) according to one of claims 1 to 6, characterized in that the cross-section (27) of the profile section (20) has essentially the shape of a polygon, preferably the shape of a quadrilateral, in particular the shape of a rectangle or a rhombus, wherein preferably at least one corner of the polygon has a chamfer or rounding.

8. 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 shaft section (32) and the profile section (20), wherein the transition section (30) has a variable cross-section along the central longitudinal axis (11) which transitions along the central longitudinal axis (11) from the cross-section (27) of the profile section (20) to the cross-section (35) of the shaft section (32), preferably continuously.

9. Fastening element (10) according to one of claims 1 to 8, characterized in that the shaft section (32) has a threadless section (36) facing the profile section (20).

10. Fastening element (10) according to one of claims 1 to 9, characterized in that the threaded section (41 ) has an external thread (42), or that the threaded section (41 ) has a bore (43) with an internal thread (45), wherein the bore (43) is preferably aligned along the central longitudinal axis (11 ).

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 area of ​​the head section (16).

12. Fastening element (10) according to one of claims 1 to 11, characterized in that the head section (16), the profile section (20), the shaft section (32), the threaded section (41) and preferably the transition section (30) form a one-piece component, in particular the fastening element (10) is formed in one piece, or that at least one of the sections (16, 20, 32, 41, 30), preferably the profile section (20), is provided on at least one separate component, in particular a sleeve.

13. A shredding tool (90) for attachment to a tool holder (70) by means of a fastening element (10), wherein the shredding tool (90) has a receiving side (95) for receiving on the tool holder (70) and a side (91) facing away from the receiving side (95), in particular a working side, wherein a tool passage (98) for guiding 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 section (16) of the fastening element (10) and / or for at least partially receiving a fastening counter-element (60), that the tool passage (98) further has a profile receptacle (92) for at least partially receiving a profile section (20) of the fastening element (10), that the cross-section (93.2) the mounting receptacle (93) overhangs the cross-section (92.2) of the profile receptacle (92) at least in some areas. and that the cross-section (92.2) of the profile recording (92) has a shape that deviates from the circular shape.

14. Crushing tool (90) according to claim 13, characterized in that the mounting receptacle (93) extends from the receiving side (95) along the central longitudinal axis (98.1 ) of the tool passage (98) in the direction of the side (91 ) facing away from the receiving side (95) and follows the profile receptacle (92) directly or indirectly.

15. Crushing tool (90) according to claim 13 or 14, characterized in that the mounting receptacle (93) has a counter-contact surface (94) at its end facing the profile receptacle (92), which is designed to engage a contact surface (19) of the fastening element (10) and / or to engage a fastening counter-element (60), wherein the counter-contact surface (94) is designed at least partially transverse, in particular perpendicular to the central longitudinal axis (98.1 ) of the tool passage (98).

16. 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 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 area (73) for at least partially receiving a profile section (20) of the fastening element (10), and that the cross-section of the profile area (73) has a shape that deviates from the circular shape.

7. Tool system (120) comprising a comminution tool (90) according to any one of claims 12 to 14, a tool holder (70) according to claim 15, a fastening element (10) according to any one of claims 1 to 11 and a fastening counter element (60), wherein the comminution tool (90) and the tool holder (70) are clamped against each other by means of the fastening element (10) and a fastening counter element (60), wherein the profile area (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 partially in both the profile receptacle (92) and the profile area (73).

Images