Anti-roll bar clamp

Abstract

The invention relates to an anti-roll bar clamp (20) for securing an anti-roll bar (40) to a vehicle. The anti-roll bar clamp (20) has a receptacle (22) for the anti-roll bar (40), wherein the receptacle (22) is formed as an intermediate space between two limbs (24, 24a, 24b) for securing the anti-roll bar clamp (20) to the vehicle and a bow (26) which connects the two limbs (24, 24a, 24b). The anti-roll bar clamp (20) consists predominantly of plastic or predominantly of fibre-reinforced plastic. The bow (26) has a flexural rigidity with respect to a curvature about the axial axis of at least 35,000,000 Nmm² in an axially arranged sectional plane relative to the centre of gravity of the sectional plane, wherein the sectional plane extends through a circle centre (28) of the bow or a fictitious radial centre of an anti-roll bar, for the diameter of which the anti-roll bar clamp (20) is designed.

Description

[0001] Stabilizer clamp

[0002] Description

[0003] The invention relates to a stabilizer clamp made predominantly of plastic or predominantly of fiber-reinforced plastic, e.g., glass-fiber-reinforced (GFRP) or carbon-fiber-reinforced (CFRP) plastic, with measures to reduce the loss of stiffness of the rubber mount. Carbon fiber is synonymous with.

[0004] (Vehicle) stabilizers for (motor) vehicles are known in a variety of designs and are also referred to, for example, as anti-roll bars, stabilizing torsion bars, or torsion spring bars. These stabilizing torsion bars serve to stabilize the body against inclination and twisting, particularly when cornering, and to adjust the handling of a (motor) vehicle. Such stabilizers are usually located in the area of ​​the front and / or rear axle and usually extend almost across the entire width of the vehicle. The attachment of such stabilizers to the chassis on the one hand and the frame on the other hand entails the problem that the vibrations, oscillations, and noise arriving at, generated by, and / or absorbed by the chassis, such as wheel and road vibrations, are transmitted via the attachment to the frame and thus also into the passenger compartment.

[0005] To dampen, and in particular to reduce, this transmission, the stabilizers are usually attached in a damping manner via stabilizer bearings. These stabilizer bearings can also be referred to as sleeve bearings. The stabilizer bearing typically comprises a rigid outer sleeve, also referred to as a stabilizer clamp, and an elastic insert element arranged coaxially in the interior of this stabilizer clamp. Also known is the arrangement of an elastic insert element around a stabilizer bar, wherein the stabilizer bar is arranged for attachment to the vehicle via the elastic insert element arranged on the stabilizer bar. The stabilizer bar can be attached to a vehicle chassis by means of the stabilizer clamp.

[0006] Current requirements from vehicle manufacturers mean that weight should be saved in all areas. Accordingly, one approach is to produce stabilizer clamps from fiber-reinforced plastic. Plastic clamps are not only lightweight, but also cheap to manufacture. However, it has been found that plastic clamps have significant disadvantages when compared to steel clamps, for example, in terms of durability. The continuous static load on the stabilizer clamp, caused in particular by the preload of the rubber mount, leads to the plastic material relaxing. The high preload is necessary to achieve the desired properties, in particular the specified radial and torsional stiffnesses and their relationship to one another, as well as a specified service life. This means that the pressure orThe force exerted by the stabilizer clamp on the mount decreases over time. As the material relaxes, the (rubber) mount gains more clearance, resulting in a loss of radial stiffness. This can be in the range of 20%. This impairs handling characteristics and, for example, increases driving noise. In particular, this can result in changes to the dynamic handling, changes to the vehicle's setup, a reduction in service life, an increase or emergence of relative movement between the rubber mount and the stabilizer clamp, and, as a result, possible noise development.

[0007] The object of the present invention is therefore to create an improved concept for stabilizer clamps.

[0008] This problem is solved by the subject matter of the independent patent claims. Further advantageous embodiments are the subject matter of the dependent patent claims.

[0009] Two similar concepts for reducing the relaxation of the plastic clamp are now presented. The first of the two concepts discloses a stabilizer clamp for attaching a stabilizer rod to a vehicle. The stabilizer clamp has a receptacle for the stabilizer rod. This means that the stabilizer rod can be inserted into the receptacle of the stabilizer clamp. Typically, a bearing, in particular a rubber bearing, is arranged between the stabilizer clamp and the stabilizer rod. The receptacle is formed as an intermediate space between two legs for attaching the stabilizer clamp to the vehicle and an arch that connects the two legs. A stabilizer rod can be, in particular, a solid rod or a tube.

[0010] Furthermore, the stabilizer clamp is predominantly made of plastic or predominantly of fiber-reinforced plastic. "Predominantly" means that the stabilizer clamp is made of more than 50% plastic or fiber-reinforced plastic. However, the stabilizer clamp is preferably made of a larger proportion, for example at least 70%, or at least 90%, or 100% plastic or fiber-reinforced plastic. For example, inserts made of other materials, for example comprising a metal or an organic sheet, can result in the stabilizer clamp not being made of 100% fiber-reinforced plastic. A PA6 or PA66 polyamide, for example, can be used as the plastic. Advantageously, a (glass or carbon) fiber content of between 25% and 70%, preferably between 35% and 65%, more preferably between 45% and 60% can be used. For example, the (glass / carbon) fiber content is 50% ± 4%.

[0011] The arch has, in an axially arranged section plane relative to the center of gravity of the section plane, a bending stiffness with respect to a curvature around the axial (rotation or curvature) axis of at least 35,000,000 Nmm 2 (= 35 • 10 6 • N • mm 2 ). The axial axis is also referred to as the y-axis in Fig. 5. The axial (and subsequently also the radial) axis preferably refers to the mount for the stabilizer bar (or the fictitious inserted stabilizer bar). Fatigue load tests have shown that a plastic clamp with a bending stiffness with respect to a curvature around the y-axis of at least 35,000,000 Nmm 2 exhibits only low relaxation and thus a sufficient service life. Higher bending stiffnesses of, for example, at least 50,000,000 Nmm 2 , at least 125,000,000 Nmm 2 , at least 250,000,000 Nmm 2 , at least 375,000,000 Nmm2 or at least 500,000,000 Nmm 2 They therefore each exhibit improved stiffness and thus lower relaxation. The section plane runs through a circle center of the bend or a fictitious radial center of a stabilizer rod, for whose diameter the stabilizer clamp is designed. The inner radius of the bend can be used, for example, to determine the circle center of the bend. Increasing the flexural stiffness also means that the material input required to achieve the optimum strength of the stabilizer clamp for permissible requirements may sometimes be significantly exceeded.

[0012] The arc can, for example, span at least an angle between 70° and 110°, measured from the circle center of the arc or the notional radial center (i.e., the center of a cross section) of the stabilizer bar, for whose diameter the stabilizer clamp is designed. In other words, the cutting plane can be arranged at an angle between 70° and 110°, measured from a contact surface of the stabilizer clamp on the body. Preferably, at least 80%, more preferably 90%, most preferably 95%, or ideally 100% of the arc has the aforementioned flexural rigidity. In other words, the stabilizer clamp has at least 80%, more preferably 90%, most preferably 95% or ideally 100% of the aforementioned flexural rigidity in an angular range between 80° and 100°, preferably between 75° and 105°, more preferably between 65° and 115° or even more preferably between 60° and 120°.In the case of 100%, this means that there is no cutting plane in the arch, especially within the specified angle ranges, whose bending stiffness is below the specified value.

[0013] Optionally, the cutting plane that intersects the bend at an angle of 90° is a cutting plane that divides a mirror-symmetrical mount for the stabilizer bar into its mirror-symmetrical parts. In an analysis that also applies to non-mirror-symmetrical stabilizer clamps, the cutting plane that intersects the bend at an angle of 90° runs perpendicularly through the fictitious radial center of the stabilizer bar, for whose diameter the stabilizer clamp is designed. The vertical course of the cutting plane refers, for example, to the orientation of the stabilizer clamp when the stabilizer clamp rests with its legs on a flat surface. This cutting plane preferably has the aforementioned high flexural rigidity. The angle (range) can be determined based on a screw-on surface.The statements in this paragraph regarding the axial axis also apply optionally to the following description regarding the flexural rigidity with respect to a curvature around the radial axis. The radial axis is arranged perpendicular to the axial axis. An example radial axis is designated as the z-axis in Fig. 5.

[0014] A corresponding bending stiffness with respect to a curvature around the radial axis preferably has a value of at least 650,000,000 Nmm 2 , preferably at least 750,000,000 Nmm 2 more preferably at least 1,000,000,000 Nmm 2 on.

[0015] The bending stiffness characterizes the resistance of the stabilizer clamp under bending stress in a flat cross-section against curvature around the bending axis. In the case of a stabilizer clamp with a homogeneous, i.e. constant, modulus of elasticity, the bending stiffness S Bfrom the product of the (tensile) elastic modulus E and the axial area moment of inertia I Y relative to the bending axis Y (S B = E • / r However, for plastics and fiber-reinforced plastics, the modulus of elasticity varies with moisture content. The value given is in the conditioned state according to ISO 1110, i.e., at 70°C and a relative humidity of 62%.

[0016] In the case of a plastic clamp with an insert, for example a metal or an organic sheet, a discrete distribution of the modulus of elasticity across different layers i results. This means that the above formula for the homogeneous modulus of elasticity must be modified to sum over the number n of individual layers. Et ■ I Y i ).

[0017] The idea behind the first concept is to reduce clamp relaxation by using a stabilizer clamp made of plastic or fiber-reinforced plastic with a correspondingly high flexural rigidity, thus maintaining consistent driving characteristics throughout the entire service life of the stabilizer clamp. Therefore, it is obviously not possible to produce increasingly lighter clamps, as a certain minimum amount of material is required to maintain the described flexural rigidity. However, the advantage of the clamp's greater stability outweighs the disadvantage of the material used.

[0018] A second of the two concepts also discloses a stabilizer clamp for attaching a stabilizer bar to a vehicle. The stabilizer clamp also has a receptacle for the stabilizer bar, with the receptacle being formed as an intermediate space between two legs for attaching the stabilizer clamp to the vehicle and the arch connecting the two legs. Furthermore, this stabilizer clamp is also predominantly made of plastic or fiber-reinforced plastic. In this respect, the stabilizer clamps of both concepts are constructed identically.

[0019] However, instead of the high bending stiffness, the stabilizer clamp of the second concept has an alternative shape to reduce relaxation. Here, the two legs each have a first bearing surface for arrangement on the vehicle and a second bearing surface opposite the first bearing surface for a head of a fastening means. The two legs furthermore each have a bore between the respective first and second bearing surface for the passage of the fastening means. This means that one side of the legs faces the underbody of the vehicle and preferably also rests there. After the stabilizer clamp has been mounted on the vehicle, the head of the fastening means, e.g. a screw head of a screw, with which the stabilizer clamp is fastened, in particular screwed, to the vehicle, rests on the second side of the legs. The second bearing surface, this meansthe support for the head of the fastening means, at least one of the two legs is arranged above a circle center of the arc or a fictitious radial center of a stabilizer rod for whose diameter the stabilizer clamp is designed.

[0020] The idea behind the second concept is to move the support surfaces for the fasteners to a higher point, making it possible to drill the holes for the fasteners closer to the holder for the stabilizer bar. For the standard deep support surfaces, a minimum distance is specified by the (radial) thickness of the bend, i.e. the outer radius of the bend, and the size of the head of the fastener. If the support surface is above the center of the circle of the bend or the fictitious radial center of the stabilizer bar, for whose diameter the stabilizer clamp is designed, the head of the fastener no longer collides with the bend due to the curvature of the bend, so that the hole for the fastener can be drilled directly next to the bend, i.e. in particular next to the base of the bend.In addition to reducing relaxation, such a clamp also requires less installation space.

[0021] Both concepts can now be combined to further improve the relaxation of the stabilizer clamp. This means that the stabilizer clamp with high flexural rigidity can also have a support surface for the fastener that is located above the circular center of the bend or the notional radial center of the stabilizer rod, for whose diameter the stabilizer clamp is designed.

[0022] The following examples can be used for both concepts.

[0023] In exemplary embodiments, the stabilizer clamp has a rubber bearing in the receptacle. In the mounted state in the vehicle, the rubber bearing is pressed between the stabilizer bar and the stabilizer clamp in such a way that the rubber bearing has a reduction in its radial cross-sectional area compared to its unloaded cross-sectional area by at least 10% (i.e. a calibration factor of at least 10%), in particular at least 14%, preferably at least 16% or particularly preferably at least 20%. The stabilizer mounted in the vehicle is referred to as the mounted state. A bearing that is pressed against the stabilizer with such great pressure is also referred to as a highly preloaded bearing. The rubber bearing exhibits an elastic deformation as a result of a compressive load. The change in cross-section is also referred to as the calibration factor.Here, a 10% reduction in height and the resulting material displacement are defined as a cross-sectional change / calibration factor of 10%. In particular, the cross-sectional change can be in a range between 10% and 35%, preferably between 14% and 30%, and more preferably between 16% and 27%. Due to their design, the risk of relaxation is greatest in highly preloaded, incompressible bearings, so there is a greatest need to reduce relaxation here.

[0024] In exemplary embodiments, the stabilizer clamp has a cutting plane height of at least 11 mm. The height (radial extent) of the cross-sectional plane is decisive for determining the axial area moment of inertia and thus the flexural rigidity. Here, the height is used to determine the more relevant axial area moment of inertia with a higher power than the width (axial extent). However, the axial area moment of inertia about the axial axis of rotation is typically smaller than the axial area moment of inertia about the radial axis of rotation and thus contributes more significantly to relaxation than the area moment of inertia about the radial axis of rotation. In this respect, the weight of the stabilizer clamp can be reduced by maintaining this minimum height compared to a clamp with a lower height. A height-to-width ratio can, for example, be greater than 1:5, preferably greater than 1:4, more preferably greater than 1:3.The ratio then becomes larger as the second number becomes smaller, i.e. the resulting quotient is considered.

[0025] It has been found that when using plastic clamps, especially fiber-reinforced plastic clamps for the production of the stabilizer clamp, an axial area moment of inertia around the axial axis of rotation of at least 2,600 mm 4 When considering the area moment of inertia instead of the bending stiffness, complex simulations of the component can be omitted, since the area moment of inertia is a purely geometric quantity. The evaluation of mounted, otherwise unloaded, stabilizer clamps has shown that a plastic clamp with an area moment of inertia of at least 2,600 mm 4only slight relaxation, thus ensuring a sufficient service life for the (rubber) bearing. Without relaxation of the plastic clamp, the rubber bearing remains permanently designed for compression. With greater relaxation, a tensile load can also occur, which would cause the rubber bearing to fail very quickly. Larger axial area moments of inertia around the axial rotational axis, for example, at least 3,000 mm 4 , preferably at least 4,000mm 4 , again preferably at least 10,000mm 4 , more preferably at least 20,000mm 4 or most preferably at least 40,000mm 4 therefore each exhibit improved radial stiffness and thus reduced relaxation.

[0026] The axial moment of inertia around the radial axis of rotation can, for example, be more than 52,000 mm 4 , preferably at least 60,000 mm 4 , more preferably at least 80,000mm 4 be.

[0027] Further embodiments disclose a one-piece or multi-piece stabilizer clamp. The multi-piece stabilizer clamp thus consists of at least two parts, wherein the at least two parts, when assembled, form the two legs and the arch and close the receptacle on the underside. Multi-piece stabilizer clamps that close the receptacle on the underside allow the bearing to be preloaded before installation on the chassis, thereby reducing or counteracting the bending of the stabilizer clamp. Bending refers to the increase in the bore spacing of the clamp. The multi-piece stabilizer clamp thus reduces the assembly effort during vehicle assembly at the customer's site.

[0028] In the multi-part stabilizer clamp, in exemplary embodiments the at least two parts are connected to one another by means of a materially bonded connection, in particular by means of an adhesive or a thermal joining operation. Cyanoacrylate, for example, is a suitable adhesive. In further exemplary embodiments the two parts are connected to one another by means of a positive connection. Both of these enable the realization of a stable stabilizer clamp, even from several parts, which can withstand the large preload forces, in particular in the case of highly preloaded bearings. Additionally or alternatively, the at least two parts can be connected to one another by means of a positive connection. The positive connection can be implemented, for example, as a clip closure, i.e. by means of a locking lug.Other positive-locking connections, such as a screw or rivet connection or a positive-locking connection using other fastening means, are also possible. In exemplary embodiments, a metallic threaded insert, e.g., a screw nut, is integrated into at least one of the two legs, in particular into both legs. The metallic threaded insert can be cast into the fiber-reinforced plastic of the stabilizer clamp. Thus, only screws are required for mounting the stabilizer during vehicle assembly. A separate supply of nuts during the assembly process can be eliminated. The assembly process is thus simplified. This enables a cost-effective assembly concept.

[0029] Alternatively, a sleeve for receiving a fastening screw can be integrated into at least one of the two legs, in particular into both legs. The sleeve preferably has the absence of any metal. A carbon fiber reinforced plastic (CFRP), for example, can be used for the sleeve. The carbon fibers are in particular unidirectionally aligned. However, it is also possible to design the carbon fibers as a non-crimp fabric, so that the fibers are aligned, for example, at 0°, ± 45° or 90'° to one another. In the absence of metal sleeves or metallic threaded inserts, it is possible to adhere the rubber mount to the stabilizer bar by means of inductive adhesion, regardless of any metal components in the stabilizer clamp. This allows greater flexibility in the design of the inductors and the process flow.

[0030] Preferred embodiments of the present invention are explained below with reference to the accompanying drawings. They show:

[0031] Fig. 1: a schematic perspective view of a stabilizer clamp, wherein the support for a head of the fastening means is located below the stabilizer center point in Fig. 1a and above the stabilizer center point in Fig. 1b; Fig. 2: a schematic perspective view of a stabilizer rod with two stabilizer clamps arranged thereon (see Fig. 1a);

[0032] Fig. 3: a schematic perspective view of a two-part stabilizer clamp, wherein in Fig. 3a the second part only closes the receptacle for the stabilizer bar, while in Fig. 3b an embodiment is disclosed in which the legs of the stabilizer clamp are assembled from the first and second parts; Fig. 4: a schematic perspective view of the stabilizer clamp from Fig. 1b, wherein Fig. 4a discloses an embodiment with a metallic threaded insert integrated into one leg, and Fig. 4b discloses an embodiment with a sleeve integrated into one leg; and

[0033] Fig. 5: a schematic plan view of a cutting plane for determining the area moment of inertia as a basis for determining the bending stiffness.

[0034] Before exemplary embodiments of the present invention are explained in more detail below with reference to the drawings, it is pointed out that identical, functionally equivalent or equivalent elements, objects and / or structures in the different figures are provided with the same reference numerals, so that the description of these elements shown in different exemplary embodiments is interchangeable or can be applied to one another.

[0035] Fig. 1 shows, in Fig. 1a and Fig. 1b, a schematic perspective view of a stabilizer clamp 20. The stabilizer clamp 20 has a receptacle 22 for a stabilizer rod (not shown here). The receptacle 22 is formed as an intermediate space between two legs 24a, 24b and an arc 26 connecting the two legs. The legs 24a, 24b serve to fasten the stabilizer clamp 20 to the vehicle. Furthermore, the arc 26 has a circle center 28. In both illustrations, this is identical to a fictitious radial center of a stabilizer rod, for whose diameter the stabilizer clamp is designed. In the case of non-symmetrical, i.e. asymmetrical, stabilizer clamps, the fictitious radial center of the stabilizer rod and the circle center of the arc can also differ. The arc is referred to in particular as the inner shape (or inner contour) of the stabilizer clamp.The asymmetry can be caused by an external shape of the stabilizer clamp that differs from the internal shape.

[0036] The legs 24a, 24b optionally each have a (first) support surface 30a, 30b for arranging the stabilizer clamp 20 on a vehicle, in particular a chassis. Opposite, a (second) support surface 32a, 32b is provided for a fastening means for attaching the stabilizer clamp to the vehicle. Furthermore, the two legs each have a bore 34a, 34b for passing the fastening means between the first and second support surfaces.

[0037] The second support surface 32a, 32b for the fastening means is arranged below the circle center 28 in Fig. 1a. In Fig. 1b, the second support surface 32a, 32b is arranged above the circle center 28.

[0038] Fig. 2 shows a schematic perspective view of two stabilizer clamps 20, as shown in Fig. 1a, on a stabilizer rod 40. A (rubber) bearing 38 is arranged between each stabilizer rod 40 and stabilizer clamp 20.

[0039] Fig. 3a shows a schematic perspective view of a two-part stabilizer clamp 20, wherein the exemplary embodiment from Fig. 1b is used as the first part, and a closure plate 36 for closing the receptacle 22 is arranged between the legs 24a, 24b as the second part. The closure plate 36 can also be arranged below the legs 24a, 24b. For example, the first part and the second part of the stabilizer clamp can be connected to one another by means of a material-to-material connection.

[0040] Fig. 3b shows a schematic perspective view of an alternative embodiment of a two-part stabilizer clamp 20. The first part of the stabilizer clamp is formed here from the arch 26 and a portion of the legs 24a, 24b. The second part forms another portion of the legs 24a', 24b' and also fits into the receptacle 26. When the first and second parts of the stabilizer clamp are joined together, a hollow space remains, which exerts a force on a (rubber) bearing 38 and thus fixes the stabilizer rod 40.

[0041] For example, the first and second parts are connected to one another in a form-fitting manner, for example with rivets 42. Instead of rivets, locking hooks (also referred to as locking lugs or clips), screws, or similar fastening elements can be used. Here, too, a material-to-material connection can be used as a supplement or alternative to the form-fitting connection. Furthermore, Fig. 3b shows an induction coil 44 for heating the bearing 38 in the assembled and preloaded stabilizer clamp and adhering it to the stabilizer bar. Thus, the vulcanization process can take place within the plastic clamp. A separate bonding tool is not required.

[0042] Fig. 4a shows, based on the embodiment of Fig. 1b, a schematic perspective view of the stabilizer clamp with a metallic threaded insert 46 integrated into one leg. The metallic threaded insert can be cast into the stabilizer clamp 20 during an injection molding process for manufacturing the same.

[0043] Fig. 4b shows, based on the exemplary embodiment from Fig. 1b, a schematic perspective view of the stabilizer clamp with a sleeve 48 integrated into one leg. The sleeve 48 can be made of carbon fiber reinforced plastic (CFRP) or another material, for example. In particular, however, the sleeve is devoid of any metal.

[0044] Fig. 5 shows a schematic perspective sectional view of the stabilizer clamp from Fig. 1a. The section plane intersects the arch at an angle of 90°. Since the stabilizer clamp from Fig. 1a is mirror-symmetrical, the section plane lies in the mirror plane. This means that Fig. 5 shows a mirror-symmetrical half. The axial area moments of inertia are calculated around the center of gravity of the section plane as follows:

[0045] Axial area moment of inertia about the radial axis:

[0046] Axial area moment of inertia about the axial axis:

[0047] Although some aspects have been described in connection with a device, it is understood that these aspects also represent a description of the corresponding method, so that a block or component of a device can also be understood as a corresponding method step or as a feature of a method step. Similarly, aspects described in connection with or as a method step also represent a description of a corresponding block, detail, or feature of a corresponding device.

[0048] The above-described embodiments are merely illustrative of the principles of the present invention. It is understood that modifications and variations of the arrangements and details described herein will be apparent to others skilled in the art. Therefore, it is intended that the invention be limited only by the scope of the following claims and not by the specific details presented in the description and explanation of the embodiments herein.

[0049] List of reference symbols:

[0050] 20 stabilizer clamp

[0051] 22 Mounting for a stabilizer bar 24 Leg

[0052] 26 sheets

[0053] 28 Circle center

[0054] 30 first support surface

[0055] 32 second support surface 34 bore

[0056] 36 locking plate

[0057] 38 warehouses

[0058] 40 Stabilizer bar

[0059] 42 Rivet 44 Induction coil

[0060] 46 metallic thread insert

[0061] 48 sleeve

[0062] 50 cutting plane

Claims

Patent claims 1 . Stabilizer clamp (20) for attaching a stabilizer bar (40) to a vehicle, the stabilizer clamp (20) having the following features: - a receptacle (22) for the stabilizer rod (40), the receptacle (22) being formed as an intermediate space between two legs (24, 24a, 24b) for fastening the stabilizer clamp (20) to the vehicle and an arc (26) connecting the two legs (24, 24a, 24b); - wherein the stabilizer clamp (20) consists predominantly of plastic or predominantly of fiber-reinforced plastic; - wherein the arch (26) has, in an axially arranged section plane relative to the center of gravity of the section plane, a flexural rigidity with respect to a curvature about the axial axis of at least 35,000,000 Nmm 2wherein the cutting plane runs through a circle center (28) of the arc or a fictitious radial center of a stabilizer rod for whose diameter the stabilizer clamp (20) is designed.

2. Stabilizer clamp (20) according to claim 1, wherein the two legs (24, 24a, 24b) each have a first support surface (30, 30a, 30b) for arrangement on the vehicle and a second support surface (32, 32a, 32b) opposite the first support surface (30) for a head of a fastening means, - wherein the two legs (24, 24a, 24b) each have a bore (34) between the respective first and second support surface (30, 32) for the passage of the fastening means; - wherein the second support surface (32) of at least one of the two legs (24, 24a, 24b) is arranged above a circle center (28) of the arc or a fictitious radial center of a stabilizer rod, for whose diameter the stabilizer clamp (20) is designed.

3. Stabilizer clamp (20) for attaching a stabilizer bar (40) to a vehicle, the stabilizer clamp (20) having the following features: - a receptacle (22) for the stabilizer rod (40), the receptacle (22) being designed as an intermediate space between two legs (24, 24a, 24b) for fastening the stabilizer clamp (20) is formed on the vehicle and an arch (26) connecting the two legs (24, 24a, 24b); - wherein the stabilizer clamp (20) consists predominantly of plastic or fiber-reinforced plastic, - wherein the two legs (24, 24a, 24b) each have a first support surface (30, 30a, 30b) for arrangement on the vehicle and a second support surface (30, 32) opposite the first support surface (30, 32) for a head of a fastening means, - wherein the two legs (24, 24a, 24b) each have a bore (34) between the respective first and second support surface (30, 32) for the passage of the fastening means; - wherein the second support surface (32) of at least one of the two legs (24, 24a, 24b) is arranged above a circle center (28) of the arc or a fictitious radial center of a stabilizer rod, for whose diameter the stabilizer clamp (20) is designed.

4. Stabilizer clamp (20) according to claim 3, wherein the arc (26) in an axially arranged sectional plane relative to the center of gravity of the sectional plane, around the axial axis, has a flexural rigidity of at least 35,000,000 Nmm2 wherein the cutting plane runs through a circle center (28) of the arc or a fictitious radial center of a stabilizer rod for whose diameter the stabilizer clamp (20) is designed.

5. Stabilizer clamp (20) according to one of claims 1, 2 or 4, wherein a height of the cutting plane is at least 11 mm.

6. Stabilizer clamp (20) according to one of the preceding claims, wherein a rubber bearing is arranged in the receptacle (22) of the stabilizer clamp (20).

7. Stabilizer clamp (20) according to claim 6, wherein the rubber bearing in the mounted state in the vehicle is pressed between the stabilizer rod and the stabilizer clamp in such a way that the rubber bearing has a reduction in its radial cross-sectional area compared to its unloaded cross-sectional area by at least 10%, in particular at least 14% or at least 16%.

8. Stabilizer clamp (20) according to one of the preceding claims, wherein the stabilizer clamp (20) consists of at least two parts, wherein the at least two parts, when assembled, form the two legs (24, 24a, 24b) and the arch (26) and close the receptacle (22) on the underside.

9. Stabilizer clamp (20) according to claim 8, wherein the at least two parts are connected to one another by means of a material connection, in particular by means of an adhesive or a thermal joining operation.

10. Stabilizer clamp (20) according to claim 8 or claim 9, wherein the at least two parts are connected to one another by means of a positive connection, in particular by means of a locking lug.

11. Stabilizer clamp (20) according to one of the preceding claims, wherein a metallic threaded insert (46) is integrated into at least one of the two legs (24, 24a, 24b), in particular into both legs (24, 24a, 24b).

12. Stabilizer clamp (20) according to one of claims 1 to 10, wherein in at least one of the two legs (24, 24a, 24b), in particular in both legs (24, 24a, 24b), a sleeve (48) for receiving (22) a fastening screw is integrated, wherein the sleeve has the absence of a metal.

13. Stabilizer clamp (20) according to claim 12, wherein the sleeve consists predominantly of carbon fiber reinforced plastic (CFRP).

14. Stabilizer clamp (20) according to one of claims 1, 2 or 4 to 13, wherein the arch (26) in the axially arranged section plane relative to the center of gravity of the section plane has a flexural rigidity with respect to a curvature around the radial axis of at least 650,000,000 Nmm 2 wherein the cutting plane passes through a circle center (28) of the arc or a fictitious radial center point of a stabilizer rod, for whose diameter the stabilizer clamp (20) is designed.

Images