FASTENING ELEMENT AND ADJUSTMENT SYSTEM WITH A FASTENING ELEMENT

Abstract

The invention relates to a fastening element, in particular an eccentric screw, and to an adjustment system comprising a fastening element. Fastening elements are already known from the prior art. These are often used in an adjustment system, for example, to adjust parts of a vehicle chassis. For this purpose, eccentric elements are often mounted or formed on or within the fastening element to achieve adjustability. To ensure secure positioning of the eccentric element within the fastening element, it is often guided in a rotation-resistant manner within the fastening element via a groove.The problem in this regard, however, is that the groove results in particularly expensive manufacturing of the fastener, especially due to the thread forming process. The thread forming tool is often damaged by the groove, particularly at its exit end, or wears down significantly, resulting in a short service life. Therefore, the objective of the present invention is to achieve cost-effective manufacturing of a fastener, particularly for an adjustment system, while simultaneously ensuring a high mechanical load capacity.

Description

FASTENING ELEMENT AND ADJUSTMENT SYSTEM WITH A FASTENING ELEMENT The invention relates to a fastening element, in particular an eccentric screw, and to an adjustment system comprising a fastening element. Fasteners are already known from the prior art. These are often used in an adjustment system, for example, to adjust parts of a vehicle chassis. For this purpose, eccentric elements are often mounted or formed on or within the fastener to achieve adjustability. To ensure secure positioning of the eccentric element within the fastener, it is often guided in a rotation-resistant manner through a groove. The problem with this, however, is that the groove results in particularly expensive manufacturing of the fastener, especially due to the thread forming process. The thread forming tool is often damaged by the groove, particularly at its exit end, or wears down significantly, resulting in a short service life for these tools. Therefore, the objective of the present invention is to achieve a cost-effective manufacture of a fastening element, in particular for an adjustment system, the fastening element having at the same time a high mechanical load capacity. This objective is achieved with a fastening element according to claim 1, with an adjustment system according to claim 14, and with a manufacturing process for a fastening element according to claim 15. Improvements, features, and advantageous embodiments follow from the dependent claims, the description, and the figures. According to one aspect of the invention, a fastening element, in particular an eccentric fastening element and / or an eccentric screw, is provided, comprising a threaded element, the threaded element extending along a longitudinal direction, the threaded element having a thread section, a head, and a groove, the groove in particular extending along the longitudinal direction, the groove having an end section near the head and a distal end section, the end section near the head being arranged in the longitudinal direction closer to the head than the thread section, extending The fastener according to the invention is designed to be used in an adjustment system, advantageously for a vehicle or vehicle chassis. The fastener comprises at least one threaded element extending longitudinally. The longitudinal direction is, in this respect, the direction in which the length of the threaded element is determined. Advantageously, the threaded element is configured to be essentially rotationally symmetric about this longitudinal direction.By essentially rotationally symmetric, it is understood in particular that over approximately 70% or more of the length, preferably at least 80% of the threaded element, the outer contour of the threaded element is rotationally symmetric about the longitudinal direction, with no particular threads or knurling breaking rotational symmetry. The threaded element according to the invention comprises at least a thread section, a head, and a groove. The head of the threaded element advantageously forms a distal end section in the longitudinal direction of the threaded element. The head of the threaded element serves, in this respect, to transmit a torque about the longitudinal direction, particularly by form drive, to the threaded element.For this purpose, the head has tooling surfaces to facilitate mounting the threaded element and / or general rotation, for example, to adjust a chassis. Therefore, the head of the threaded element may have tooling surfaces in the form of an external hexagon, an internal hexagon, a Torx drive, and / or a cross-slot. The threaded section of the threaded element, on the other hand, advantageously also forms a distal end section in the longitudinal direction, this end section preferably being the distal end section opposite the head in the longitudinal direction. The threaded section has a thread, particularly around its outer perimeter. This thread can be configured as a metric thread, for example. The threaded element can be easily joined to other elements by applying force through the threaded section.In addition to a threaded section and a head, the threaded element also has at least one groove. The groove of the threaded element serves, in particular, to interact with another element, specifically an eccentric element, in such a way as to prevent, by form drag, the rotation, particularly around the longitudinal direction, of the other element, particularly the eccentric element, relative to the threaded element. ML / a / ZUZ or / UUl DUO For example, this can be achieved because an anti-torsion structure of the eccentric element fits into the groove of the threaded element in such a way that the rotation of the eccentric element relative to the threaded element in the longitudinal direction is prevented by form drag. In this way, adjustment of the other element, for example, the eccentric element, can be achieved particularly easily by rotating the fastening element. The groove of the threaded element extends in a straight line and / or along the longitudinal direction parallel to it. This allows for particularly simple manufacturing of the groove. The groove of the threaded element has an end section near the head and a distal end section. The respective end section is the section where the groove has a free end and / or a closed end.A closed end, in this respect, is the area of ​​the groove where the lateral boundary contours of the groove meet or merge, and the groove's course along its length thus ends at this junction. A free-terminating end, on the other hand, is an end where the lateral boundary contours do not meet, but rather, for example, a ridge or a step terminates the useful course. Alternatively or additionally, the respective end section may already be present, preferably, in areas where the groove, in particular the base section of the groove, has an increasing distance from the longitudinal direction or longitudinal axis. In other words, this can mean that the end section of a groove can also be formed by the area where the groove exhibits a decrease in groove depth along its course.The groove of the threaded element according to the invention is configured in this respect such that it extends at least partially through the thread section. In other words, this may mean that at least a portion of the groove runs within the thread section, such that the groove is also cut in a plane through the thread section, with a normal parallel to the longitudinal direction. The end section near the head of the groove of the threaded element is arranged in this respect such that, viewed in the longitudinal direction, it is at least partially closer to the head than the thread section. In other words, this may mean that the end section near the head is closer to the head in the longitudinal direction than the thread section.The thread section of the threaded element that is decisive in this respect is the thread section through which at least one groove of the element extends. ML / a / ZUZ or / UUl DUO threaded. Advantageously, the threaded element according to the invention not only has one such groove, but several such grooves can also be arranged, each exhibiting some or all of the characteristics of the described groove. Advantageously, the grooves are distributed or arranged equidistantly around the perimeter of the threaded element. By configuring the end section near the head in a zone that is closer to the head than the thread section, the end section of the groove near the head can be at least partially, and preferably completely, free of threads. This results in a considerably longer tool life, particularly when rolling the thread, leading to cost-effective manufacturing of the fastener.Furthermore, this way the influences of the notch effect of the end section near the head can be reduced, so that at the same time a high mechanical load capacity of the screw is achieved. Advantageously, the groove extends completely through the threaded section. "Complete extension through the threaded section" means that there is no sectional plane through the threaded section that presents a normal parallel to the longitudinal direction that does not also intersect the groove. Furthermore, the groove can also extend over other areas of the threaded element, such that it can extend beyond the threaded section. This type of groove configuration allows for particularly easy mounting of an eccentric element within the groove. The groove preferably has a rounded base and / or rounded side sections in a section plane whose normal is parallel to the longitudinal direction, with the base and / or side sections in particular having an advantageously constant radius of rounding. The base section of the groove is, in this respect, the section of the groove that is oriented along the longitudinal direction. In other words, the base section delimits the groove along the longitudinal direction. The side sections of the groove are the parts of the groove that form a lateral contour on the surface or surfaces in which the groove is cut. Therefore, the side sections delimit the groove laterally with respect to the groove's path.Advantageously, the ratio of the rounding radius of the base and / or side section of the groove to the diameter of the thread section is in a range of 0.1 to 0.5, preferably in a range of 0.2 to 0.5. ML / a ZUZJ / UU I DUO 0.3. With a ratio in the range of 0.1 to 0.5, a threaded element with a particular mechanical load capacity can be achieved. With a ratio in the range of 0.2 to 0.3, the applicant has surprisingly demonstrated that a particularly long tool life can be achieved, especially for the forming tool used to create the groove and / or thread section. For cost-effective manufacturing, it is particularly advantageous for the rounding radius of the base and side sections to be the same. Conveniently, the threaded element is manufactured by a forming process, and / or the groove is manufactured by a forming process, particularly stamping and / or rolling, and / or by a machining process involving chip removal. By manufacturing the threaded element by a forming process, a structure with a particular mechanical load-bearing capacity can be achieved within the threaded element, thus providing it with a high degree of mechanical load-bearing capacity. When the groove is manufactured by stamping, rolling, or another forming process, an advantageous grain direction can also be achieved in the threaded element, thereby increasing and / or at least positively influencing its strength.If the groove is manufactured using a machining process, a particularly high level of precision in the geometry can be achieved, allowing for the use of an eccentric element to provide a secure, form-weighted, anti-torsion mechanism with a high mechanical load capacity. A machining process could be, for example, grinding, milling, punching, or planing. The threaded element conveniently has a drive zone, which is located closer to the head, particularly in the longitudinal direction, than the end section of the groove near the head and / or the thread section. This drive zone serves to rotate the threaded element during manufacturing, particularly when the thread is rolled, using rolling dies. In other words, the drive zone ensures sufficient rotation of the raw or finished threaded element during the thread manufacturing process. The drive zone is specifically arranged such that, viewed longitudinally, it is closer to the head than the end section of the groove near the head. ML / a / ZUZ or / UUl DUO end section of the groove near the head and / or the thread section. In this way, the drive zone can be configured without grooves. By a configuration without grooves, it should be understood that the groove does not extend into the drive zone. By configuring the drive zone without grooves, particularly simple manufacturing of the drive zone and / or a particularly mechanically robust drive zone can be achieved. By positioning the draw zone closer to the head in the longitudinal direction than the end section of the groove near the head and / or the thread section, it is also possible to ensure that there is always sufficient contact area for the rolling dies in the draw zone when rolling the thread. Therefore, a high and / or reliable torque transmission between the rolling dies and the draw zone can be achieved particularly effectively. Advantageously, the draw zone is bounded longitudinally, either positively or negatively, by steps and / or annular grooves. In other words, the distal ends of the draw zone, viewed longitudinally, can be positioned as close as possible to the steps or annular grooves.In this way, a clear delimitation can be achieved with respect to other areas of the threaded element, so that it can be ensured that these areas are used in any case only slightly for the transmission of torque during the manufacture of the threaded element and / or the fastening element. Advantageously, the drag zone is configured in a rotationally symmetrical manner around the longitudinal direction, specifically cylindrically. As a result, a particularly simple and economical design of the drag zone can be achieved. Advantageously, the end section of the groove near the head lies at least partially, preferably entirely, in the longitudinal direction between the thread section and the head and / or is separated by at least a minimum distance from the head and / or the thread section in the longitudinal direction. This minimum distance is preferably 0.5 mm, 1 mm, or 1.5 mm. Alternatively, or additionally, the minimum distance may also preferably be 0.1 times the outside diameter of the thread section. Because the groove runs at a certain distance from the thread section and the head in the longitudinal direction, a particularly good distribution of the notch effect can be achieved in the longitudinal direction. ML / a / ZUZ or / UUl DUO In an advantageous refinement, the end section of the groove near the head lies at least partially, and preferably entirely, in the longitudinal direction between the thread section and the drive zone. The decisive factor for this is, in particular, the section of the end section near the head where the groove forms its final distal end, viewed longitudinally. Alternatively, or preferably, the decisive factor may also be the portion of the end section of the groove near the head where the groove, viewed along its longitudinal course, begins to exhibit an increasing distance from the longitudinal direction. In other words, the decisive factor may also be, as an alternative, the end section of the groove where it begins to lose its original and / or minimum distance from the longitudinal direction.By configuring the end section longitudinally between the thread section and the drive zone, a groove termination with a particularly low notch effect can be easily achieved. Furthermore, this method also helps prevent or reduce weakening of the drive zone. The drive zone advantageously has the same internal and / or external diameter as the thread section. In other words, the internal and / or external diameter of the thread section can correspond to the respective internal and / or external diameter of the drive zone. In this respect, the internal diameter is specifically twice the smallest possible distance of the relevant outer perimeter zone from the longitudinal direction. Conversely, the external diameter of the drive zone or the thread section is specifically twice the distance of the outermost zone of the drive zone and / or the thread section from the longitudinal direction. The internal and / or external diameters are referred to in this context as the core and external diameters, particularly in the case of a thread.Alternatively or additionally, the flank diameter of the drive zone can also preferably be the same as the flank diameter of the thread section. In a preferred embodiment, the drive zone has drive structures around its outer perimeter, enabling torque transmission by form drive around the longitudinal direction. These drive structures may be structures formed in the drive zone during and / or before the thread rolling process. Therefore, these drive structures serve to transmit torque. ML / a / ZUZ or UUl DUO by dragging the rolling dies around the longitudinal direction of the fastener and / or the threaded element. In this way, a reliable torque transmission can be achieved, so that, through a forming process, in particular a rolling process, a particularly reliable and economical thread manufacturing process is made possible. This makes it possible, for example, to achieve a screw strength class of > 10.9 for the threaded element, in particular at least 12.9. Conveniently, the drive structure is a spline and / or a thread. Alternatively or additionally, and preferably, the drive structure can also be a knurled structure and / or a multi-toothed pattern. This drive structure(s) allows for particularly reliable and simple torque transmission during the thread forming process. Advantageously, the drive structure, when configured as a thread, is arranged and / or configured such that the threads in the drive structure are a direct extension of the thread or thread profile of the threaded element. In other words, the thread or threads of the drive structure can be arranged so that, viewed in the direction of rotation about the longitudinal axis, they have no rotational displacement with respect to the imaginary continuation of the thread or threads of the threaded element. Thus, the drive area can also be used for fastening, providing another fastening option for the threaded element in a simple and economical manner. The threaded element conveniently has a strength class >= 10.9. By configuring the threaded element to have a strength class greater than 10.9, it can be used in high-strength threaded connections. Therefore, the threaded element material advantageously exhibits a tensile strength (Rmen N / m²) of more than 1,000 and / or an elongation at break (A) of 9%. In particular, the tensile strength of the material used for the threaded element is crucial for achieving a higher strength class. The material used in the thread section, head, and / or groove area is especially important in assessing tensile strength. Advantageously, the final section of the slot near the head, seen in The ML / a / ZUZ or UUl DUO, in particular, in the longitudinal direction, is arranged in an annular groove running around the longitudinal direction. This allows for a particularly reduced notch effect at the end section, so that the screw's bending strength is only slightly negatively affected by the notch effect of the groove's end section. Furthermore, this method also allows for a high degree of elasticity, so that the threaded element or fastener exhibits a high degree of fatigue resistance. Conveniently, the fastener features an eccentric structure, which is resistant to rotation about the longitudinal direction relative to the threaded element. Specifically, the eccentric structure has an outer perimeter and / or contour that is eccentric and / or cam-shaped with respect to the longitudinal direction. In an assembled or fixed state, the eccentric structure is arranged so that it cannot rotate about the longitudinal direction relative to the threaded element. In other words, a torque can be transmitted about the longitudinal direction between the eccentric structure and the threaded element, particularly through form drag. In this way, the fastener can be used by the eccentric structure, or a cam-like feature of the eccentric structure, to adjust, for example, a vehicle chassis component. Advantageously, the eccentric structure is formed as a single piece with the threaded element, or alternatively, the eccentric structure can preferably be a separate component from the threaded element. If the eccentric structure is formed as a single piece with the threaded element, a mechanically load-bearing connection between the eccentric structure and the fastener or threaded element can be achieved particularly easily. The eccentric structure and the threaded element are preferably manufactured from the same or a single blank by a primary forming and / or forming process. Therefore, the eccentric element is preferably not bonded to the threaded element. In other words, therefore, it may be preferable for the fastening element to be designed as a single piece to allow for a particularly high mechanical load capacity. However, to save on manufacturing costs, it may be advantageous for the eccentric structure to be configured as a component. ML / a / ZUZ or / UUl DUO independent. In this respect, it is preferable that torque transmission by form drag occurs around the longitudinal direction between the eccentric structure and the threaded element in an assembled state. Alternatively or additionally, advantageously the eccentric structure can also be shrunk, pressed, and / or caulked in a zone of the threaded element to ensure that the eccentric structure cannot slip in the longitudinal direction of the threaded element. In a preferred embodiment, the eccentric structure is positioned closer to the head in the longitudinal direction than the end section of the groove near the head and / or the drive zone and / or the thread section, with the eccentric structure advantageously arranged directly adjacent to the head in the longitudinal direction. By positioning the eccentric structure longitudinally in close proximity to the head, only a small relative rotation between the head and the eccentric element about the longitudinal direction occurs during operation, thus achieving a particularly high degree of adjustment accuracy.Furthermore, or alternatively, by positioning the eccentric structure in the longitudinal direction closer to the head than the end section of the groove near the head, and / or than the drive zone, and / or than the thread section, it is preferable that these areas are not subjected to a tightening or driving torque applied to the screw head. Therefore, by means of the above-described arrangement of the eccentric structure in the longitudinal direction, a threaded element with a particularly high mechanical load-bearing capacity can be achieved. Another aspect of the invention relates to an adjustment system comprising a fastening element as described above and below, and an eccentric element. The eccentric element has an anti-torsion structure, fitting into the groove in such a way as to prevent rotation of the eccentric element in the longitudinal direction relative to the threaded element by means of a drag mechanism. The eccentric element has an eccentric and / or cam-shaped structure, particularly on its outer perimeter and, advantageously, on its inner perimeter, an anti-torsion structure that fits into the groove in the assembled state, thus preventing rotation of the eccentric element relative to the threaded element of the fastening element by means of a drag mechanism. The outer eccentric structure of the eccentric element is configured in particular eccentrically relative to the longitudinal direction. By means of the With the provision of an eccentric element, an adjustment option can be created, for example, for a part of a vehicle's chassis, using the adjustment system in a simple way, either in addition to or as an alternative to the eccentric structure. Therefore, the adjustment system is particularly suitable for use in a vehicle. For example, a tension rod on a chassis and / or a wheel suspension of a vehicle can be adjusted using such an adjustment system. Advantageously, the eccentric element and the eccentric structure are uniformly eccentric; in particular, the projection of the outer contour of the eccentric element and the outer contour of the eccentric structure cover the same space in the longitudinal direction. The assembled state of the eccentric structure and the eccentric element with respect to the threaded element is particularly crucial for evaluating spatial alignment and uniformity. The assembled state is generally, in particular, the state in which all elements of the fastening element and / or the adjustment system have assumed their final relative positions, especially in the longitudinal direction. Therefore, in particular, the anti-torsion structure of the eccentric element fits into at least one groove of the threaded element in the assembled state.In this context, "uniformly eccentric" means that the eccentricity of both the eccentric element and the eccentric structure is configured to be uniform and directed in the same direction with respect to the longitudinal axis. This uniformity allows for a uniform and simultaneous adjustment across the eccentric element and the eccentric structure when the threaded element or fastener is rotated. Another aspect of the invention may relate to a method for manufacturing a fastener, in particular a fastener as described above and below. This manufacturing method may comprise the following steps: • making available a raw piece, • forming a thread section by shaping, in particular by rolling; • in particular, shaping the raw piece so as to form a head; • shaping and / or machining of the raw piece using a chip-removal machining process, in particular milling, to form a groove, the groove having a final cross-section ML / a / ZUZ or / UUl DUO near the head and a distal end section, the end section near the head being arranged closer to the head in the longitudinal direction than the thread section, the groove extending at least partially through the thread section. The advantages already explained with respect to the fastening element can be easily achieved by this manufacturing process. In particular, during the rolling of the thread section, a three-piece rolling tool can be used, with the thread section being formed by one part of this tool, an annular groove advantageously being made in the threaded element by another part of the rolling tool, and / or no forming being carried out on the threaded element, and the drive zone of the threaded element being machined by forming in a third part, and / or a torque being transmitted, in particular by form drive, and / or alternatively preferably by friction, between the rolling tool and the drive zone.Therefore, another aspect of the invention may also relate to a rolling tool, in particular a rolling die, or a group of rolling tools. In another preferred embodiment, the manufacturing process comprises the following additional steps: Forming and / or shaping a drive zone with at least one drive structure, the drive structure(s) being formed in the same process step, particularly by rolling, and the thread section also being formed by rolling. This allows for the production of a particularly economical fastener with a high mechanical load capacity. Additional advantages and features of the present invention are apparent from the following description with respect to the figures. In this regard, the individual features of the depicted embodiment may also be used in other embodiments, unless expressly excluded. They show: Figure 1 shows a view with a break in an adjustment system; Figure 2 shows a partial view of the end section near the head of the groove of the threaded element; and Figure 3 shows a view of a threaded element in the longitudinal direction. Figure 1 shows an adjustment system 50 comprising an element ML / a / ZUZ or / UUl DUO of fastening 1 and an eccentric element 20. The fastening element 1 comprises a threaded element 2 that is configured as a single piece with an eccentric structure 16. Therefore, in Figure 1, the fastening element 1 is configured as a single piece. In the longitudinal direction L, the head 6 forms a distal end zone of the threaded element 2. The head 6 is configured in this respect as an external hexagon. The eccentric structure 16 of the fastening element 1 is arranged directly downstream of the head in the longitudinal direction L. The drive zone 10 is arranged as close as possible to the eccentric structure 16 in the longitudinal direction L. There is a wide annular groove 14 between the drive zone 10 and the thread section 4 of the threaded element 2.The eccentric element 20 is arranged partially around the threaded section 4 of the threaded element 2. The eccentric element 20 has an anti-torsion structure 22 that fits into the groove 8 of the threaded element 2. Groove 8 has a distal end section E2 in the longitudinal direction L and a near-head end section E1 in the longitudinal direction. The near-head end section E1 is located in the annular groove 14. The distal end section E2 of groove 8, on the other hand, extends below the mounted nut and is therefore not visible in Figure 1. In Figure 1, a fragment view, shown in more detail in Figure 2, is indicated by Z. In Figure 2, the fragment view marked with Z in Figure 1 is shown in more detail. Therefore, in Figure 2 you can see the final section E1 of the slot 8 near the head, which in particular, as shown in Figure 2, is arranged largely and / or completely within the annular slot 14. Figure 3 shows a view of a threaded element 2 of a fastening element 1 in the longitudinal direction L. In Figure 3, the eccentric structure 16 of the fastening element 1 can be seen. Due to the fact that the outer contour of an eccentric element 20 can be congruent with the eccentric structure 16 in the longitudinal direction L, the outer contour of the eccentric structure 16 could also correspond to the outer contour of an eccentric element 20, which is not otherwise visible in Figure 3. List of references: - Fastening element - Threaded element ML / a / ZUZ Ó / UU1 DUO - Thread section - Head - Slot - Drag zone - Annular groove - Eccentric structure - Eccentric element - Anti-torsion structure - Adjustment system - Final section near the head of the slot (8) - Distal end section of the groove (8) - Longitudinal direction or longitudinal axis

Claims

1. Fastening element (1) comprising a threaded element (2), the threaded element (2) extending along a longitudinal direction (L), the threaded element (2) having a thread section (4), a head (6) and a groove (8), the groove (8) extending in particular along the longitudinal direction (L), the groove (8) having an end section (E1) close to the head and a distal end section (E2), the end section (E1) close to the head being arranged closer to the head (6) in the longitudinal direction (L) than the thread section (4), the groove (8) extending at least partially through the thread section (4), the threaded element (2) having a strength class greater than or equal to 10.9, the groove (8) having a rounded base and / or rounded side sections in a section plane whose normal is parallel to the longitudinal direction (L),the ratio of the radius of rounding of the base and / or side section of the groove (8) to the diameter of the thread section (4) being in the range of 0.1 to 0.5, preferably in the range of 0.2 to 0.3, the groove (8) being stamped and / or rolled or the threaded element (2) being manufactured by a forming process.

2. Fastening element (1) according to claim 1, the groove (8) extending completely through the thread section (4).

3. Fastening element (1) according to one of the preceding claims, the threaded element (2) having a drive zone (10), the drive zone (10) being arranged closer to the head (6), in particular in the longitudinal direction (L), than the end section (E1) of the groove (8) near the head and / or than the thread section (4).

4. Fastening element (1) according to any of the preceding claims, the end section near the head (E1) of the groove (8) being located in the longitudinal direction (L) between the threaded section (4) and the drive zone (10). ML / a / ZUZ or / UUl DUO 5. Fastening element (1) according to one of the preceding claims, the drive zone (10) having the same inner and / or outer diameter as the thread section (4).

6. Fixing element (1) according to one of the preceding claims, the drag zone (10) having drag structures on its outer perimeter, the drag structures enabling a transmission of torque by dragging in the longitudinal direction (L).

7. Fastening element (1) according to one of the preceding claims, the drive structure being a groove and / or a thread.

8. Fixing element (1) according to one of the preceding claims, the end section near the head (E1) of the groove (8), in particular viewed in the longitudinal direction (L), being arranged in an annular groove (14) running in the longitudinal direction (L).

9. Fastening element (1) according to one of the preceding claims, the fastening element (1) having an eccentric structure (16), the eccentric structure (16) being resistant to rotation in the longitudinal direction (L) with respect to the threaded element (2).

10. Fixing element (1) according to one of the preceding claims, the eccentric structure (16) being configured as a single piece with the threaded element (2), or the eccentric structure (16) being an independent component.

11. Fastening element (1) according to any of the preceding claims, wherein the eccentric structure (16) is arranged closer to the head (6) in the longitudinal direction (L) than the end section near the head (E1) of the groove (8) and / or than the drive zone (10) and / or than the threaded section (4), the eccentric structure (16) being advantageously arranged directly next to the head (6) in the longitudinal direction (L). ML / a ZUZO / UU I DUO 12. Adjustment system (50) comprising a fixing element (1) according to any one of claims 1 to 11 and an eccentric element (20), the eccentric element (20) having an anti-torsion structure (22), the anti-torsion structure (22) fitting into the groove (8) in such a way as to prevent by dragging the rotation of the eccentric element (20) in the longitudinal direction (L) with respect to the threaded element (2).

13. A method for manufacturing a fastening element (1) according to any one of claims 1 to 11, comprising the steps of: - providing a blank, - rolling a thread section (4); - in particular, shaping the blank to form a head (6); - shaping and / or machining the blank by a chip-removal machining process, in particular milling, to form a groove (8), the groove (8) having an end section (E1) close to the head and a distal end section (E2), the end section (E1) close to the head being arranged closer to the head (6) in the longitudinal direction (L) than the thread section (4), the groove (8) extending at least partially through the thread section (4).

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