Device for positioning fastenings Device for positioning fastenings

Abstract

A device for positionally securing a rotation angle sensor relative to a sensor carrier about an axis of rotation, the rotation angle sensor determining a rotation angle between a rotor and a stator, the device comprising: a base body; a torsionally rigid support bearing, seen in a circumferential direction about the axis of rotation, for receiving a torsional force from the rotation angle sensor, and a spring held on the support bearing, configured to exert a restoring force on the sensor carrier, the spring having at least one spring leg and a spring arm extending at least partially axially relative to the axis of rotation, the spring arm comprising, seen in the circumferential direction about the axis of rotation, a forwardly directed spring arm flank and a rearwardly directed spring arm flank opposite the forwardly directed spring arm flank. At least one of the spring leg and the spring arm flanks is arranged within the base body.

Description

Technical Field

[0001] This invention relates to a device for positioning and fastening. Background Technology

[0002] Such a device is known in DE102022103722A1.

[0003] The object of the present invention is to improve upon the known device. Summary of the Invention

[0004] An apparatus for positioning and securing a rotation angle sensor relative to a sensor holder about a rotation axis, the rotation angle sensor determining the rotation angle between a rotor and a stator, the apparatus comprising: a base; a torsional rigid support bearing, viewed circumferentially about the rotation axis, the support bearing for receiving torsional forces from the rotation angle sensor; and a spring configured to apply a restoring force to the sensor holder, the spring having at least one spring foot and a spring arm extending at least partially axially relative to the rotation axis, the spring arm including a forward-oriented spring arm side and a rearward-oriented spring arm side opposite the forward-oriented spring arm side. According to the invention, the spring foot and at least one of the spring arm sides are arranged within the base.

[0005] The device described above utilizes a spring arm, with its spring feet entirely located outside the supporting housing or structural body, in the aforementioned positioning and fastening mechanism. In this document, the spring arm is designed with two opposing sides, one facing the base and the other facing away from it, such that the entire spring arm, including its attachment point, is externally attached to the supporting structure circumferentially. This arrangement results in unfavorable stress distribution in the area of ​​the spring feet, as the spring feet are oriented forward or backward circumferentially about the axis of rotation, and force transmission therefore acts circumferentially, causing material stress due to torsion of the spring feet to concentrate on the inner V-shaped notch between the spring arm and the base. Prolonged, repeated torsional loading leads to material fatigue or crack formation.

[0006] The design starting point of the device described in this application is to redefine the direction of force introduction and structurally integrate spring feet, so that the material stress in the spring foot region can be better distributed circumferentially with respect to torsional motion. According to the invention, this objective is achieved by arranging the spring feet and at least one side of the spring arm inside the base, so that the spring arm is no longer connected to the outside of the base circumferentially, but is instead axially housed within the support structure. By orienting the spring feet along the axis of rotation, the mechanical stress distribution in the transition region between the spring arm and the base at the spring feet is improved; in this region, torsional loads are no longer transmitted into the structure through tangential contact, but through an axially oriented clamping region. The axial orientation design enables more regionalized force transmission, transmitting force to deeper material regions of the base, thereby significantly reducing local stress peaks in the spring foot region. Simultaneously, by integrating it into the base to form a geometrically guiding structure, the movement of the spring arm can be restricted, and overload due to excessive deflection can be prevented. In principle, additional limiting walls are no longer needed. The clamping structure formed inside the matrix creates a more stable and oriented load path, thereby enabling an anti-rotation fixing design that is compatible with the load, which is something that the tangential connection method in the known device mentioned at the beginning cannot achieve.

[0007] By reducing stress peaks, material fatigue, and uncontrolled spring travel overrun in the spring foot region, a significantly reduced failure rate in operation can be achieved using the device according to the invention. The altered force transmission achieved via the axially oriented spring feet embedded in the matrix results in a more uniform stress distribution and, in particular, reduces locally concentrated load peaks that have been identified as causes of crack initiation or fracture in known constructions. This has a positive impact on the fatigue strength of the entire component and extends service life even under cyclic or thermal loads. The geometric guidance of the spring arm within the matrix further ensures that the path of movement of the spring arm remains controlled and avoids mechanical overload due to excessive deflection. Overall, the result is a robust, series-stable solution with higher fail-safety, lower maintenance requirements, and improved manufacturing tolerances, as functionally critical load points are geometrically defined and guided in a structurally protected manner.

[0008] In a further improvement, the base includes a circumferential base wall in the axial direction relative to the axis of rotation, within which the spring arm is arranged. In this way, the spring arm can be completely enclosed by the supporting hollow structure, achieving not only safe and defined axial clamping but also geometric guidance and mechanical restraint of the spring arm. The circumferential wall specifically defines the movement space of the spring arm and mechanically prevents overload due to excessive deflection. Furthermore, the enclosed base wall reliably protects the spring arm from external influences such as dust, mechanical contact, or thermal spikes. The hollow structure also allows for optimized integration into existing housing shapes and provides construction freedom for the arrangement of multiple spring arms or sensor components. Manufacturing advantages are also generated because the wall structure can be produced particularly efficiently as rotationally symmetric or segmented injection-molded parts in a closed mold.

[0009] In another improved embodiment, the base wall includes a groove viewed axially from the axis of rotation, in which the spring arm is arranged. In this way, the spring arm is not only spatially guided within the base but also received by a laterally and / or axially restrained structure, which enables precise and directional guidance of the spring arm. The arrangement in the groove improves the structural integration of the spring arm because stress from the spring arm can be introduced into the surrounding wall structure in a controlled manner and is not concentrated at the point of connection located externally. Furthermore, the geometry of the groove allows for defined movement restriction of the spring arm, preventing undesirable over-deflection and thus increasing component lifespan. The arrangement recessed into the wall structure also provides increased protection for the spring arm against mechanical damage or environmental impacts and creates construction freedom for further integration possibilities, such as receiving additional guiding or damping elements.

[0010] In another advantageous embodiment, viewed axially from the axis of rotation, the spring foot is positioned at the bottom of the groove. In this way, the spring arm is axially introduced into the substrate structure from its foot region and anchored there. Thus, force introduction occurs along the axis of rotation into the depth of the groove wall, thereby achieving a particularly stable clamping with a uniform stress distribution. The embedded bottom achieves low-loss return of bending and torsional forces to the surrounding material structure and minimizes critical stress peaks, such as those occurring in tangential or lateral attachment clamping devices. Furthermore, this results in a clear structural separation between the active spring region of the substrate and the passive force-absorbing section, which is advantageous for both spatial organization and reproducibility during manufacturing.

[0011] Furthermore, the spring arm in its relaxed state is oriented parallel to the base wall. This creates an optimized resting position for the spring arm, which is guided regionally along the wall structure without preloading or deflection. The parallel orientation not only improves the guidance of the spring arm within the recess but also contributes to particularly compact space designs, as the unloaded spring arm does not occupy additional volume outside the wall profile. Additionally, this geometry simplifies manufacturing, as the spring arm geometry can be more easily integrated into rotationally symmetric or linearly guided tool forms. When force is applied, the parallel orientation additionally supports the defined and repeatable deflection characteristics, as the deflection direction appears exactly orthogonal to the initial mounting position.

[0012] In a further advantageous embodiment, reinforcing ribs are preferably arranged radially relative to the axis of rotation within the base wall. In this way, the mechanical stiffness of the wall structure can be increased in a targeted manner, particularly radially, where bending and shear forces may arise due to the action of the spring arm during deflection. The reinforcing ribs act as structural mating supports that help receive and dissipate these forces while preventing deformation or undesirable compliance of the wall structure. Thus, the position of the spring arm within the groove is stabilized, and the spring's restoring characteristics remain constant even under prolonged loads or temperature fluctuations. The reinforcing ribs can additionally serve as guiding elements for the spring arm or as contact surfaces for movement restriction, thereby expanding the functional range of the component in terms of construction.

[0013] In another advantageous embodiment, viewed from the axis of rotation, the base wall is formed concave in the region supporting the bearing. This results in the support bearing shape being fitted into a correspondingly shaped receiving structure, whereby the component can self-center during assembly and can be securely positioned to prevent relative rotation. The concave shape supports a uniform distribution of circumferential forces because it promotes large-area contact and reduces localized load concentration. Particularly when receiving circumferential torsional moments, the concave geometry results in improved force flow into adjacent wall regions, which increases the torsional stiffness of the overall structure. Furthermore, the concave forming element can be used as a defined contact surface for attaching fastening elements (e.g., locking lugs or assembly structures).

[0014] In another embodiment, as viewed from the axis of rotation, the base wall has a protrusion opposite the support bearing, facing the internal space enclosed by the base wall. In this way, a locally protruding structure is formed within the internal space, which serves for targeted reinforcement, functional expansion, or geometric adaptation. The protrusion can thus be used as a contact or limiting surface for the spring arm, such as for defined movement restriction or for positioning in an unloaded state. Simultaneously, the protrusion structurally acts as an additional reinforcement to the wall structure by increasing axial bending stiffness and supporting the dimensional stability of the internal space. The protrusion can also be used to receive additional functional elements, such as damping bands, guide protrusions, or integrated locking lugs. The targeted arrangement on the side opposite the support bearing further achieves a more uniform material distribution within the base wall, which reduces stress differences under torsional loads.

[0015] In another embodiment, viewed circumferentially about the axis of rotation, the substrate has stop walls oriented rearward and / or frontward in the circumferential direction. In this way, a defined mechanical constraint is created, restricting the movement of the spring arm or the entire housing or substrate relative to the sensor support. The stop walls act as form-fitting retaining elements during circumferential deflection and prevent the spring from being stressed beyond its intended operating range. This contributes to component lifespan and reduces the risk of material fatigue due to excessive deformation. Depending on the front-side and / or rear-side arrangement, the stop walls can function as single-sided or double-sided end stops and can optionally be used to adjust or lock the component in the installed state. Furthermore, the stop walls support spatially defined integration into the surrounding housing or load-bearing structure.

[0016] According to another aspect of the invention, a rotational angle sensor for detecting the rotational angle between a rotor and a stator includes: a rotor; a stator having a housing and a circuit board for evaluating an encoder field affected by the rotor; and one of the means for fixing the rotational position of the housing relative to a sensor support about a rotational axis. Integrating one of the means for positioning and securing the housing into the rotational angle sensor provides several advantages for the sensor function itself. In particular, the orientation-defined, structurally stable connection of the housing enables reproducible fixation of the stator position relative to the rotor, thereby improving the sensor's measurement accuracy, repeatability, and thermal stability. Furthermore, it increases the long-term stability of calibration and simplifies the assembly process, which has a positive impact on the overall reliability of the sensor system. Attached Figure Description

[0017] The properties, features, advantages, and implementations of the invention described above will become clearer from the following description of embodiments explained in more detail with reference to the accompanying drawings. In the drawings: Figure 1This is a structural diagram of a vehicle equipped with sensors for detecting rotational angle and torque; Figure 2 It comes from Figure 1 A structural diagram of a sensor used to detect rotation angle and torque; Figure 3a It is a traditional method used to... Figure 1 A structural diagram of a sensor positioning and fastening device in a vehicle; Figure 3b It is according to the invention for using Figure 1 A structural diagram of a sensor positioning and fastening device in a vehicle; Figure 4 This is a perspective view of the device according to the first embodiment of the present invention; and Figure 5 This is a perspective view of the device according to a second embodiment of the present invention.

[0018] In the accompanying drawings, the same technical elements are referred to by the same reference numerals and are described only once. The drawings are schematic only and do not specifically indicate actual geometric relationships. Detailed Implementation

[0019] refer to Figure 1 The figure schematically shows a perspective view of a vehicle 1 with a steering system 2.

[0020] In this embodiment, vehicle 1 includes a chassis 5 supported on two front wheels 3 and two rear wheels 4. The front wheels 3 can be steered via a steering system 2, enabling vehicle 1 to turn.

[0021] The steering system 2 includes a steering wheel 6 mounted on a first steering shaft 7. The steering wheel 6 is further arranged to rotate about a rotation axis 8. The first steering shaft 7 is connected to a sensor 9 for detecting position (here, angular position) and is connected here to a torsion element 10 in a manner not further specified. The torsion element has a freely selectable spring stiffness (preferably constant and linear), thus enabling the application of torque to be converted into a measurable and detectable torque angle. A second steering shaft 11 is connected to the torsion element 10 on the side of the rotation axis 8 opposite to the first steering shaft 7, and the second steering shaft further terminates at a steering gear 12. When the steering wheel 6 is rotated with applied torque in the form of a steering torque 13, the steering torque 13 is correspondingly transmitted to the steering gear 12 via the steering shafts 7 and 11, in response to which the steering gear causes the front wheels 3 to turn by a wheel steering angle 14 to achieve cornering.

[0022] Steering is assisted by an auxiliary motor 15, which causes the second steering shaft 11 to rotate together. For this purpose, a steering torque 13 is derived based on the rotation angle difference 16 between the first steering shaft 7 and the second steering shaft 11, which is detected by a sensing sensor 9. The auxiliary motor 15 then drives the second steering shaft 11 to rotate according to the detected steering torque 13.

[0023] To detect the aforementioned rotation angle difference 16 and thus the steering torque 13, sensor 9 includes a thin rail 17 connected to the first steering shaft 7 and a thick rail 18 connected to the second steering shaft 11, which will be discussed in more detail later. Sensor 9 also includes a measuring circuit 19 fixed in place relative to vehicle 1. The measuring circuit 19 is used to detect the angular position of the thin rail 17 and the angular position of the thick rail 18, and thereby determine the rotation angle difference 16. This will also be discussed in more detail below. Based on the rotation angle difference 16, control unit 20 can now control auxiliary motor 15 using appropriate control signal 21.

[0024] In addition to the rotation angle difference 16, the measurement circuit 19 of sensor 9 also determines the rotation angle 22 of the entire steering shafts 7, 11 so as to use the rotation angle, for example, in a vehicle dynamics system.

[0025] The following will refer to Figure 2 The structure of sensor 9 will be described in more detail, which forms the basis for explaining this embodiment.

[0026] Although the coarse rail 18 is directly fastened to the second steering shaft 11 in an anti-rotation manner, the fine rail 17 is held on the first steering shaft 7 via the support sleeve 23. In addition, the drive wheel 24 is held on the support sleeve 23 in an anti-rotation manner, which drives the driven wheel 25 for the multi-angle detection device 26 in a manner described below.

[0027] In this embodiment, the guide rail 17 is designed as an impeller with multiple guide rail blades 27 made of metal. Each guide rail blade 27 is equidistantly distributed circumferentially around the first steering shaft 7 and held on the guide rail support 28. For further explanation, it will be assumed that there are twelve guide rail blades 27, although... Figure 2 More fine rail blades 27 are shown in the image.

[0028] Similarly, the coarse rail 18 in this embodiment is also designed as an impeller with multiple coarse rail blades 29 made of metal. Each coarse rail blade 29 is similarly equidistantly distributed circumferentially around the first steering axis 7 and held on the coarse rail support 30 in a manner similar to that of the fine rail 17. For further explanation, it will be assumed that there are eight coarse rail blades 29. From Figure 2 From this angle, some of the rough rail blades are not visible.

[0029] Using the coarse rail blade 29 and the fine rail blade 27, the measuring circuit 19 can determine the rotation angle 22. For this purpose, the measuring circuit 19 can, in principle, be configured as described in EP3865824A1.

[0030] The measuring circuit 19 has a thin rail side 31 facing the thin rail blade 27 and a coarse rail side 32 facing the coarse rail blade 29. A transmitting coil (not shown in detail) and at least one receiving coil (also not shown in detail) are arranged on each side of the measuring circuit 19. The transmitting coil preferably excites a high-frequency magnetic field, which induces a voltage in the receiving coil. Therefore, on the thin rail side 31, a thin rail signal is generated in the corresponding receiving coil, while on the coarse rail side 32, a coarse rail signal is generated in the corresponding receiving coil.

[0031] In this configuration of the measurement circuit 19, the blades 27 and 29 interfere with the magnetic fields generated by the corresponding transmitting coils, thereby altering the fine rail signal and the coarse rail signal according to the rotation angles of the corresponding rails 17 and 18. This basic configuration can be extended, for example, to enhance the measurement system's resistance to measurement errors. Such extensions are discussed in the previously cited EP3865824A1. However, these extensions are irrelevant to understanding this embodiment.

[0032] All that is relevant to understanding this embodiment is that the blades 27 and 29 of tracks 17 and 18 generate track signals that change periodically with the angular position of the corresponding tracks 17 and 18.

[0033] In addition to these track signals, the multi-angle detection device 26 also outputs a magnetic angle signal. This magnetic angle signal is generated based on a radially magnetized magnet 36 in the magnetic sensor element 37. The radially magnetized magnet is arranged on the side of the driven wheel 25 facing the circuit board 19 and rotates above the magnetic sensor element 37 via the driven wheel 25.

[0034] Then, based on the track signal and magnetic angle signal, the rotation angle 22 of the entire steering shaft 7, 11 is calculated on the circuit board 19 and the rotation angle is output through the output interface 38.

[0035] In the sensor 9 described above, the measuring circuit 19 is fixed in place relative to the vehicle 1, and therefore fixed relative to the rotation axis 8. In order to accurately detect the angular position of the thin rail 17 and the thick rail 18, it is necessary to precisely fix the measuring circuit 19 and the housing supporting it in their rotational position to prevent them from rotating relative to the rotation axis 8.

[0036] While this requires circumferential (i.e., about the axis of rotation 8) fastening via suitable anti-rotation fasteners, it also presents the challenge of radially positioning and securing the housing relative to the axis of rotation 8. This is because manufacturing tolerances, thermal expansion, or mounting forces can cause radial displacement or tilting of the housing, which in turn leads to displacement of the transmitting and receiving coils of the measuring circuit 19 relative to the blades 27, 29 or relative to the magnet 36.

[0037] Especially when using high-frequency magnetic fields, this radial positional deviation alters the coupling characteristics between the coil and the track blades, potentially affecting the amplitude and phase of the received track signal. Similarly, this also applies to the magnetic angle signal of the magnetic sensor element 37. Even small positional deviations in the sub-millimeter range can lead to increased system measurement errors or temperature sensitivity of the angle signal.

[0038] In this context, precise and permanently stable radial positioning of the measurement circuit 19 relative to the sensor bracket fixed to the chassis 5 of the vehicle 1 is particularly important. Radial positional deviations of the measurement circuit 19 (e.g., due to manufacturing tolerances, temperature effects, or mechanical loads under installation conditions) can cause displacement of the transmitting and receiving coils of the measurement circuit 19 relative to the fine rail blade 27, the coarse rail blade 29, or the magnet 36. This displacement affects the coupling between the coil and blade structure or the magnetic field, which can alter the amplitude, phase, or linearity of the detected track and magnetic angle signals. To avoid this, the measurement circuit 19 must be held in a precisely positioned and form-locked manner relative to the sensor bracket and therefore relative to the chassis 5.

[0039] For this purpose, device 40 is used to position and secure sensor 9 in vehicle 1 relative to sensor bracket and thus relative to chassis 5. First, refer to... Figure 3a and Figure 3b The principle of device 40 will be explained. Figure 3a The principle of the conventional device 39 known in DE102022103722A1 is shown. Figure 3b A device 40 according to the invention is shown. For simplicity, the devices 39 and 40 will be described below in a cylindrical coordinate system comprising: an axial direction 42 extending parallel to the axis of rotation 8, a circumferential direction 44 extending circumferentially about the axis of rotation 8, and a radial direction 46 extending perpendicular to both the axial direction 42 and the circumferential direction 44. To understand this function, it is important in this context that the sensor 9 does not necessarily have to be located behind the devices 39 and 40 in the circumferential direction 44. During operation, viewed from the radial direction 46, the sensor 9 is typically located behind the devices 39 and 40, which is... Figure 4 and Figure 5 This is shown in detail in the text.

[0040] Both the conventional device 39 and the device 40 according to the invention include a base 48 and a spring 50 held on the base 48 via a support bearing 52. The spring 50 is used to apply a restoring force opposite to the circumferential direction 44 to the sensor holder, and further to the chassis 5, thereby securing the sensor 9 in the circumferential direction 44 in the manner described above.

[0041] As described in DE102022103722A1, applying restoring force via a spring independent of the base 48 is costly, complex to manufacture, and requires extensive maintenance. Therefore, it is proposed to integrally manufacture the spring 50 with the base 48. The spring 50 of the known device 39 has a spring arm 54, which is connected to the support bearing 52 and then to the base 48 via a spring foot 56.

[0042] Viewed circumferentially 44, the conventional device 39 has a first spring arm side 58 facing the sensor bracket and further towards the chassis 5, and a second spring arm side 60 facing the base 48. DE102022103722A1 teaches that the second spring arm side must be positioned facing the base 48, which means that, viewed circumferentially 44, the entire spring foot 56 and the support bearing 52 are located in front of the base 48, and the spring arm 54 must extend at an acute angle relative to the base 48, otherwise restoring force cannot be generated.

[0043] However, this acute-angle arrangement of the spring arm 5 relative to the base 48 and the axis 42 (and consequently relative to the rotation axis 8) has several disadvantages. First, the acute angle formed between the extension of the spring arm 54 and the axis 42 generates an unfavorable force flow in the spring foot 56 region. The restoring force required by the spring 50 needs to act substantially in the opposite direction of the circumferential direction 44, while the spring arm 54 is connected to the base 48 at a large angle. As a result, torsional and bending loads are generated, especially at the acute angle in the spring foot 56 region, which are significantly greater than the mechanical load on the conventional device 39 relative to the lower side when viewed along the axis 42. This leads to unfavorable force redirection, resulting in localized stress increases in the material at the acute angle location, and significantly increasing the risk of material fatigue or cracking in the transition area between the spring foot 56 and the support bearing 52.

[0044] Furthermore, due to the acute-angle arrangement, a long, angled spring arm 54 is required to apply the desired restoring force completely opposite to that in the circumferential direction 44. This adversely affects the absolutely necessary mounting space, as the spring 50 must extend significantly away from the base 48 in both the circumferential direction 44 and the axial direction 42 in order to position the spring head opposite the spring foot 56 sufficiently away from the base 48. The smaller the available mounting space, the more difficult it is to integrate the sensor 9 into a corresponding compact module or housing structure.

[0045] Finally, this acute-angled geometry restricts the movement path of the spring arm along its primary deflection direction. During deflection in the direction of the sensor support, the bending load may increase rapidly, which limits the effective spring action and increases the risk of overload under impact or sustained loads.

[0046] To address this problem, the device 40 of the present invention solves the aforementioned issues by arranging the spring foot 56 and at least the side surface 60 of the second spring arm within the base 48. This arrangement allows the path of the spring arm 54 to be substantially perpendicular to the circumferential direction 44, thereby enabling the spring arm to move along a straight line orthogonal to the direction of the applied restoring force when the sensor support rotates. This offers several technical advantages: First, this allows for material loads adapted to the force flow, as the restoring force of spring 50 is now transmitted transversely to the main extension direction of spring arm 54. Bending loads are distributed more evenly across support bearing 52, thereby reducing peak stress in the material.

[0047] Secondly, the right-angle geometry allows for a shorter and more compact spring structure, where force is transmitted in a more linear and defined manner. Since there is no inclined bending path that would affect the restoring force in a non-linear way, the spring characteristics are easier to dimensionally determine. This improves the reproducibility of spring behavior, especially under varying temperatures or continuous dynamic loads during drive operation. Furthermore, from a manufacturing perspective, the right-angle mounting position in the base 48 can be implemented more easily and robustly because this shape provides well-defined wall relationships, upon which the spring can be guided and supported.

[0048] Now refer to Figure 4 Specific embodiments of the device 40 according to the present invention are described.

[0049] Appendix Figure 4 The base of the device 40 is essentially a hollow cylindrical structure with a base wall 62 extending circumferentially around an axis 42, which separates the internal space 64 from the external space 66. As previously described, when viewed circumferentially 44, the spring 50 is located at the front of the device 40, while when viewed radially 46, the device 40 is connected to the sensor 9 attached thereto at its rear. This attachment can be achieved by fasteners or by integrally molding with a portion of the sensor 9's structure (e.g., the housing surrounding the components).

[0050] The term "one-piece molding" should be understood as follows: the substrate 48 (optionally together with the sensor component) is made of a continuous material body through a one-time molding process, especially injection molding, eliminating the need for subsequent adhesive bonding, threaded connections, or snap-fit ​​connections. This one-piece molding structure ensures a force-locked, tolerance-free connection between the device 40 and the sensor 9, thereby achieving precise and durable stable positioning. It also reduces assembly costs, which is particularly advantageous in automated production line scenarios.

[0051] Another advantage of the one-piece structure is that the force flow from spring 50 can be directly introduced into the surrounding sensor structure without creating material or geometric transitions that could be potential weak points. This improves the mechanical robustness of the entire sensor assembly and extends its lifespan under cyclic loading. Furthermore, the one-piece integrated structure provides design freedom to incorporate additional functional structures such as sealing lips, locking lugs, or mating profiles.

[0052] On the front side viewed radially 46, a concave protrusion 68 is formed in the region of the connection point with the sensor 9 on the substrate wall 62. This concave protrusion extends radially 46 towards the front into the internal space. Similarly, another protrusion 70 is formed on the outer side wall viewed radially 46, extending into the internal space 64, such that the two protrusions 68 and 70 face each other, and their respective vertices (not separately labeled) are opposite each other. At these vertices, the internal space 64 of the substrate 48 is reinforced by a support wall 72.

[0053] The concave protrusions 68 and 70 and their connection through the support wall 72 serve as local reinforcement units, which can specifically stabilize the base wall in the connection point area. This shape forms a double-shell structure with a pillar-like connection, which acts as a local stiffener or sandwich structure. Especially when the base is subjected to torsional or bending loads, the support wall can divert the forces appearing in the area to the surrounding wall structure, thereby avoiding stress concentration and reducing material fatigue.

[0054] Since the connection point with sensor 9 is arranged radially 46 on the rear side of device 40, this connection point serves as the central force transmission point between sensor 9 and device 40. The reinforcement structure at the apex of the protrusion supports this mechanical connection and ensures that the force introduced at this point (especially the force from spring arm 54) is oriented back. In this scenario, the protrusion functions as a force flow guiding volume, similar to a form-fitting body or a shaped load path guide.

[0055] The concave shape on both sides of the base wall 62 allows the material to be arranged in a manner suitable for loads without the need for a large wall thickness. This saves weight and material costs while maintaining high rigidity. The symmetrical shape also facilitates uniform cooling of the part during injection molding and reduces the risk of dents or warping.

[0056] The concave protrusions also serve as assembly or guiding features, such as for axial positioning within a sensor holder, or as contact surfaces for seals, locking lugs, or guide sleeves. A defined contact surface is created through the central support wall, which can also be used for additional functional elements such as clamps, centering pins, etc.

[0057] The base wall 62 has an axial groove 74 on its front side in the circumferential direction 44. This groove extends upward from the lower side of the axial direction 42, and the bottom 76 of the groove is located at the upper end of the axial direction 42, connecting radially 46 to the remaining base wall 62. The spring 50 is positioned (more precisely, suspended) on the bottom 76 of the groove in the opposite direction of the axial direction 42, thus the bottom 76 of the groove acts as a support bearing here. In the relaxed state, the spring 50 and its spring arm 54 are at the same height as the base wall 62 in the circumferential direction 44 and are pivotable to both sides of the inner space 64 and the outer space 66.

[0058] If it is necessary to protect the spring 50 from excessive stretching, the movement of the spring 50 in the opposite direction of the circumferential direction 44 can be limited by the appropriate arrangement of the support wall 72 or by adding a stop structure.

[0059] To achieve fixation along the axial direction 42, a hook portion 78 can be formed at the end of the spring 50 opposite to the spring foot 56. This hook portion forms an inverted buckle structure in the opposite direction of the axial direction 42, which can be locked and engaged with the corresponding mating component on the sensor bracket fixed relative to the chassis. To achieve coarse positioning of the device 40, a stop wall 80 extending in the circumferential direction 44 and the opposite direction of the circumferential direction 44 can be formed on the base 48.

[0060] Now for reference Figure 5 Further improvements to the device 40 are described. In this improvement, the spring arm 54 of the spring 50 has spring feet 56 at both ends of the axial direction 42, so that the spring 50 is fixed to the base 48 at both ends. The elasticity is achieved by splitting the groove bottom 76 explained above, so that two grooves 74 are formed, which extend in opposite directions in the axial direction 42 into the base wall 62, and ultimately form two groove bottoms 76.

[0061] In this way, the spring arm 54 is no longer constructed as a freely extending cantilever, but rather as a curved beam structure clamped at both ends. This results in a more symmetrical stress distribution within the material, leading to higher fatigue strength. The spring foot 56 enters the transition area in the bottom of the groove 76 geometrically through... Figure 5 The matrix wall 62 is protected by a route and embedded in a force flow optimized manner, which further reduces the risk of local stress peaks and fatigue fracture.

[0062] Furthermore, the dual mounting allows the spring arm 54 to achieve more defined kinematic characteristics because it is symmetrically loaded and unloaded during deflection in the circumferential direction 44. This improves recovery behavior and increases the reproducibility of spring characteristics even under thermal or dynamic loads. Additionally, integrating the two mounting points into the wall structure of the base 48 achieves a very compact construction, as the spring arm 54 is guided entirely within the wall thickness of the base wall 62.

[0063] Furthermore, the dual-sided anchoring creates the possibility of integrating additional functional elements (such as damping elements, stops, or positioning aids) between the two mounting points. Therefore, the spring 50 becomes a structural component that not only transmits restoring force to the sensor support but also actively improves the mechanical stability of the device 40. List of reference numerals 1 vehicle 2. Steering System 3. Front wheels 4 Rear wheels 5. Chassis 6. Steering wheel 7 First Steering Axle 8 Rotation axis 9 sensors 10 Torsion element 11 Second Steering Axle 12 Steering Gears 13 Steering torque 14 Wheel steering angle 15 Auxiliary Motors 16. Rotation angle difference 17 Fine Rails 18 rough rails 19 Measurement Circuit 20 Control Units 21 Control Signals 22. Rotation angle (entire steering shaft) 23 Load-bearing sleeve 24 drive wheels 25 Driven wheel 26 Multi-angle detection device 27 Fine rail blades 28 Fine Rail Bracket 29. Coarse rail blades 30 Rough Rail Support 31 Fine rail side 32. Rough rail side 33 Fine Rail Signal 34. Coarse rail signal 36 magnets 37 Magnetic sensor element 38 Output Interfaces 39 Traditional devices 40. Device according to the invention 42 Axial 44 Zhou Xiang 46 Radial 48 matrix 50 springs 52 Support bearing 54 Spring Arm 56 Spring Feet 58 First spring arm side view 60 Second spring arm side 62 base wall 64 Interior Space 66 External Space 68 Internal protrusion 70 External protrusion 72 Supporting wall 74 Axial Grooves 76. Bottom of the groove 78 Hook 80 stop wall

Claims

1. A device (40) for positioning and securing a rotation angle sensor (9) relative to a sensor bracket about a rotation axis (8), the rotation angle sensor (9) determining the rotation angle between a rotor and a stator, the device (40) comprising: -Matrix (48); -Anti-torsional rigid support bearing (52), viewed along the circumferential direction (44) about the rotation axis (8), is used to receive torsional force from the rotation angle sensor (9); as well as A spring (50) held on the support bearing (52) is configured to apply a restoring force to the sensor bracket. The spring has at least one spring foot (56) and a spring arm (54) extending at least partially axially (42) relative to the axis of rotation (8). Viewed from the circumferential direction (44) about the axis of rotation (8), the spring arm includes a forward-oriented spring arm side (58) and a rearward-oriented spring arm side (60) opposite to the forward-oriented spring arm side. in, - At least one of the spring foot (56) and the spring arm side (58, 60) is disposed within the base (48).

2. The apparatus (40) according to claim 1, wherein, Relative to the axis of rotation (8), the base (48) includes a circumferential base wall (62) in the axial direction (42), and the spring arm (54) is disposed within the circumferential base wall.

3. The apparatus (40) according to claim 2, wherein, The base wall (62) has a groove (74) viewed from the axial (42) direction of the rotation axis (8), and the spring arm (54) is disposed in the groove.

4. The apparatus (40) according to claim 3, wherein, Viewed from the axial direction (42) of the rotation axis (8), the spring foot (56) is located at the bottom (76) of the groove (74).

5. The apparatus (40) according to any one of claims 2 to 4, wherein, The spring arm (54) is oriented parallel to the base wall (62) in the relaxed state.

6. The apparatus (40) according to any one of claims 2 to 5, wherein, A reinforcing rib is provided in the base wall (62), and the reinforcing rib is radially oriented (46) relative to the rotation axis (8).

7. The apparatus (40) according to any one of claims 2 to 6, wherein, Viewed from the axis of rotation (8), the base wall (62) is concave in the region of the support bearing (52).

8. The apparatus (40) according to any one of claims 2 to 7, wherein, Viewed from the side of the rotation axis (8) opposite to the support bearing (52), the base wall (62) has a protrusion (70) protruding toward the internal space (64) enclosed by the base wall (62).

9. The apparatus (40) according to any one of the preceding claims, wherein, Viewed from the circumferential direction (44) about the axis of rotation (8), the base (48) has a stop wall (80) on the rear side and / or front side in the circumferential direction (44).

10. A rotation angle sensor (9) for detecting the rotation angle between a rotor and a stator, the rotation angle sensor comprising: The rotor; the stator having a housing and a circuit board (19) for evaluating the encoder field affected by the rotor; and a device (40) according to any one of the preceding claims for fixing the rotational position of the housing relative to the sensor support about the rotational axis (8).

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