Swing arm damper with axis of rotation

Abstract

The present invention relates to a pendulum rocker arm damper (1) having a rotation axis (2), the pendulum rocker arm damper having at least the following components: - an input side (3); - an output side (4); - an energy storage source (5) for transmitting torque between the input side (3) and the output side (4); - a plurality of rocker arm elements (6), the rocker arm elements having an input side roller track (7) and an output side roller track (8); and - a corresponding number of rolling elements (9, 10), wherein the input side (3) Each input-side roller track (7) has a mating track (11), and each input-side rolling element (9) is rollably held between the input-side roller track and the input-side mating track by means of a stored energy source (5). The output side (4) has a mating track (12) for each output-side roller track (8), and each output-side rolling element (10) is rollably held between the output-side roller track and the output-side mating track by means of a stored energy source (5). The pendulum rocker arm damper (1) is characterized firstly by the rocker arm element (6) comprising three separate partial tracks (13, 14, 15) arranged axially offset from each other, and the roller tracks (7, 8) are formed by said three separate partial tracks. The invention also relates to a roll stabilizer (32) having a pendulum rocker arm damper (1). The pendulum rocker arm damper proposed herein is compact and can produce high torsional stiffness. The roll stabilizer can operate with reduced noise.

Description

Technical Field

[0001] This invention relates to a pendulum rocker arm damper having a rotation axis, the pendulum rocker arm damper having at least the following components:

[0002] - Input side;

[0003] -Output side;

[0004] - A storage energy source used to transmit torque between the input and output sides;

[0005] - Multiple rocker arm elements, each rocker arm element having an input-side roller track and an output-side roller track; and

[0006] - Corresponding number of rolling elements,

[0007] The input side has mating tracks, each for a corresponding input side roller track. Each input side rolling element is held between the mating track and the input side roller track in a rollable manner by means of a stored energy source.

[0008] The output side has mating tracks, each for a corresponding output-side roller track in the output-side roller track. Each output-side rolling element is held in a rolling manner between the mating track and the output-side roller track by means of a stored energy source. The pendulum rocker arm damper is characterized primarily by each rocker arm element comprising three separate partial tracks arranged axially offset relative to each other, and the roller track being formed by these three separate partial tracks. Furthermore, the present invention relates to a roll stabilizer having such a pendulum rocker arm damper. The invention also relates to a roll stabilizer for a wheel axle of a motor vehicle and a motor vehicle. Background Technology

[0009] So-called pendulum rocker arm dampers are known from the prior art. For example, concepts for adjusting the stiffness of a rotating shaft or rotating shaft system in a transmission system are known from DE 10 2019121 204A1 and DE 10 2019 121 205 A1. These pendulum rocker arm dampers include an input side and an output side connected to each other in a torque-transmitting manner (in two directions). Multiple rocker arm elements (also called rockers) and multiple spring elements are provided. The rocker arm elements are supported on the input side and / or the output side in a relatively displaceable manner by means of at least one rolling element. The rolling element is clamped by means of the spring element so that the rolling element can roll between a corresponding transmission track and a complementary mating track. The relative torsional angle between the input side and the output side is converted into spring deflection of the spring element by means of this pendulum rocker arm damper. By means of the transmission track forming a helical gear and the complementary mating track, the transmission ratio can be adjusted and therefore the stiffness of the pendulum rocker arm damper can be adjusted. Another advantage here is that the gear ratio does not need to be constant; rather, the slope of the helical gear can be variably adjusted by the torsional angles on the input and output sides. Another advantage of this pendulum rocker arm damper compared to other implementations is that it exhibits (virtually) no hysteresis, especially at zero crossover. Known pendulum rocker arm dampers require significant installation space and are designed to reduce the stiffness of the rotating shaft.

[0010] Furthermore, so-called roll stabilizers are known from the prior art, by means of which the spring behavior of one wheel on a two-wheeled vehicle axle is replicated to the corresponding other wheel. For example, when cornering, the body roll rate decreases towards the outside of the curve. Active roll stabilizers are increasingly used, for example, to prevent mimicking the other wheel when driving over potholes. These active roll stabilizers include actuators and damping devices. The damping devices are configured to separate and / or delay the transmission of short-term (vertical) wheel deflection (e.g., short-term (vertical) wheel deflection in the case of potholes) to protect components. Currently, damping devices with elastomers are used as damping bodies. These damping devices withstand very high loads, such as 1.5 kNm [1.5 kNm]. Furthermore, it is difficult to reliably adjust the transmission characteristics of such damping devices, and signs of aging appear in the elastomer during the service life of such damping devices. These damping devices, which use an elastomer as the damping element, have a significant advantage: they are very compact. Summary of the Invention

[0011] Therefore, the object of the present invention is to at least partially overcome the disadvantages known in the prior art. Features of the invention are derived from the independent claims, and advantageous embodiments for the independent claims are shown in the dependent claims. The features of the claims can be combined in any technically reasonable manner, wherein descriptions in the following description including additional embodiments of the invention and features derived from the drawings may also be used for this purpose.

[0012] This invention relates to a pendulum rocker arm damper having a rotation axis, the pendulum rocker arm damper having at least the following components:

[0013] - Input side;

[0014] -Output side;

[0015] - A storage energy source used to transmit torque between the input and output sides;

[0016] - Multiple rocker arm elements, each rocker arm element having an input-side roller track and an output-side roller track;

[0017] - Multiple rolling elements, the number of which corresponds to the number of roller tracks of the rocker arm element.

[0018] The input side has input side mating tracks, each corresponding to a corresponding input side roller track in the input side roller track. Each rolling element on each input side is held in a rotatable manner between the input side mating track and the input side roller track by means of a stored energy source. The output side has output side mating tracks, each corresponding to a corresponding output side roller track in the output side roller track. Each rolling element on the output side is held in a rotatable manner between the output side mating track and the output side roller track by means of a stored energy source.

[0019] The main feature of a pendulum rocker damper is that each rocker element comprises three separate partial tracks, which are arranged to be axially offset relative to each other, and the roller track is formed by these three separate partial tracks.

[0020] Unless otherwise expressly stated, when the terms “center,” “axial direction,” “radial direction,” or “circumferential direction,” and their corresponding terms, are used below, reference shall be made to the stated axis of rotation. Unless otherwise expressly stated, the ordinal numbers used in the preceding and following descriptions are for the purpose of clear distinction only and do not indicate the order or rank of specified components. An ordinal number greater than one does not necessarily imply the presence of another such component.

[0021] The pendulum rocker arm damper proposed here is very compact because the arrangement of the roller tracks, namely the input-side roller tracks and the output-side roller tracks, allows for a very compact design on the respective rocker arm elements. The rolling elements can be arranged so that they are close together in the direction of travel (corresponding to the rocking motion of the relevant rocker arm element) due to their axial proximity. The direction of travel is the movement of the rolling axis of the rolling element during the rocking motion of the relevant rocker arm element. In one embodiment, when the rocker arm element is in a stationary position, the rolling axes of the rolling elements of the rocker arm element are arranged at the same height relative to the energy storage source, preferably such that this alone creates a force balance on the sides of the rolling elements, the rocker arm element, and the roller tracks having the same geometry. In an advantageous embodiment, both the input and output sides are arranged radially outward. Therefore, the central mounting space is occupied only by the rocker arm element and the energy storage source. It should be noted that the energy storage source comprises one or more elements that are (at least in combination) designed to absorb and output forces with (almost) no loss. Such components are, for example, helical springs, solid springs, pneumatic accumulators, or blocks of material exhibiting rubber-like elastic behavior. The force maintained by the stored energy source is preferably provided as compressive force.

[0022] The mating tracks on the input side and the mating tracks on the output side are respectively radially inward, such that rolling elements are arranged between the tracks, each track forming a pair of tracks consisting of a roller track and a corresponding (and complementary) mating track. The force introduction point or surface of the energy storage source is further arranged radially inward of the respective rocker arm element. Therefore, a radially outward preload is applied to the rolling element via the track. Thus, the rolling element (when actuated according to the design) can only move relative to the track in a rolling manner (around the respective rolling axis of the rolling element). This creates a helical gear. In a preferred embodiment, no further measures are provided to fasten and / or support the components of the rocker arm damper mentioned herein. In an advantageous embodiment, the respective rolling element and at least one of the respective two tracks form a mechanical stop for axially fastening the components to each other. For example, at least one of the rolling elements has a shoulder that points radially outward relative to its rolling axis.

[0023] The input and output sides are defined here for better distinction. However, this does not define the direction of the torque curve. Specifically, the torque, preferably without difference in maximum torque, maximum torsional angle, and / or transmittance of the gear ratio, can be transmitted functionally in both directions between the two sides by means of a rocker arm element and a stored energy source. The input and / or output sides are, for example, formed as a ring shape around a central (common) axis of rotation. On the radially inner side (relative to the axis of rotation), mating tracks and possible protrusions and / or at least one stop are provided for the relative mobility of other components, for example to prevent excessive relative torsional angles under overload conditions.

[0024] This rocker arm element includes at least one roller track for receiving a rolling element near the input side and at least one other roller track for receiving a rolling element near the output side. Furthermore, the rocker arm element includes a receiving surface for storing an energy source element, which introduces a preload force and a force that is converted by means of the tracks and rolling elements into a torque opposite to the relative rotation from the input side to the output side. The preload force and the force for the desired (maximum) transmittable torque are configured to act at least partially, preferably entirely, in the same direction. The tracks are arranged such that when the input and output sides rotate relative to each other, the rocker arm elements experience only a slight relative tilt, preferably no relative tilt or negligible relative tilt. In one embodiment (preferably only as a whole), the two rocker arm elements are arranged opposite each other, and when the two sides rotate relative to each other and do not tilt or tilt negligibly relative to each other, the stored energy source is only compressed between the two rocker arm elements. Disregarding the previously explained implementation, in the preferred embodiment, the force formed on the rolling element of the pendulum damper is always aligned perpendicular to the tangent (aligned along the direction of the track) of the contact line immediately adjacent to the corresponding track.

[0025] The proposed rocker arm element comprises three separate partial tracks arranged axially offset relative to each other. For example, a (single) roller track (e.g., an output-side roller track) is formed by two of the partial tracks. A (single) second roller track (e.g., an input-side roller track) is formed by a third partial track. Particularly preferably, the first and second partial tracks are arranged axially on the outer sides and the third partial track is arranged axially between the other two partial tracks. In a particularly preferred embodiment, partial mating tracks corresponding to the partial tracks are formed on both sides; specifically, two partial mating tracks are provided when there is one (single) partial track, and one (single) partial mating track is provided when there are two partial tracks. For example, the input side includes an input-side mating track formed by a (single) partial mating track and in rolling contact with the input-side second running surface of the input-side rolling element. There, the rocker arm element includes an input-side roller track formed by two partial tracks and in rolling contact with the corresponding input-side first running surface of the input-side rolling element. For the output side, the opposite is preferably true, i.e., the output side rolling element is axially centered on the output side roller track of the rocker arm element in a rolling manner, and is axially supported on the output side mating track of the output side by two partially mating tracks on the outside.

[0026] With this pendulum rocker arm damper, energy is converted into individually adjustable transmission characteristics (torque and relative torsional angle) via rolling elements. Because of the pure rolling motion and therefore the absence of friction in the rolling contact of the rolling elements, there is virtually no hysteresis. The roller tracks and complementary mating tracks allow for modular implementation of any transmission characteristic without changing the stored energy source.

[0027] In an advantageous embodiment, each rolling element is supported on an equal-surface running surface on its outer side along the rolling axis to resist tilting moments transverse to the rolling axis. The equal-surface running surface is formed on the output side, input side, or corresponding rocker arm element. Other running surfaces (preferably integral) are arranged between the two externally supported running surfaces and are thus supported on opposing components, i.e., respectively (in the corresponding order as described above) on the corresponding rocker arm element, output side, or input side. On the rocker arm element side, this tilting moment is preferably supported in the opposite direction by a stored energy source, particularly preferably by the same element that generates or contributes to the preload force.

[0028] In a preferred embodiment, the swing arm damper presented herein is not used on the axis of rotation, but is statically torsional about one or both sides of the axis of rotation of the swing arm damper for use, for example, in vehicle suspension, such as roll stabilizers, as a damper device for, for example, a trunk lid or hood, a flap damper, or to provide a latching function for a vehicle door.

[0029] In an advantageous embodiment of the pendulum rocker arm damper, it is further proposed that the input-side roller track and the output-side roller track are each arranged on the radially outer side of the rocker arm element.

[0030] For particularly compact designs, the rocker arm element is designed to open radially outward (i.e., toward the corresponding side and / or away from the energy storage source). The rolling element can be placed radially on the associated roller track from the outside, i.e., relative to the corresponding rolling axis of the rolling element. However, in one embodiment, the rolling element is axially pushed along the rolling axis of the rolling element during assembly. It should be noted that in this embodiment, all existing roller tracks are arranged radially outward (i.e., away from the center of the energy storage source and / or the axis of symmetry of the force balance and / or the pendulum rocker arm damper). No roller tracks are arranged inside the rocker arm element or arranged to point toward the energy storage source. Existing (complementary) mating tracks are therefore also all arranged radially inward, preferably on the radially inner side of the annular side. For particularly compact designs, these sides are also designed to open radially inward (i.e., toward the corresponding rocker arm element or toward the energy storage source). One side preferably has an axial extension that extends from one (maximum) end of the rolling element to the opposite (maximum) end of the rolling element, or is shorter or protrudes beyond the opposite (maximum) end. In one embodiment, at least one of the side portions is axially connected to or integrally formed with another element, and in addition to the axial overlap, (in the case of annular side portions in the radial direction) overlaps with the rocker arm element and / or energy storage source via a rolling element of one of the rolling elements toward the center of the pendulum rocker arm damper (energy storage source and / or force balance and / or axis of symmetry). In one embodiment, the axial overlap at the level of the rocker arm element and / or energy storage source is formed only in the outer region of the movable element (or the movement track of the movable element), for example, by a connecting bolt between two partial elements on one of the two side portions. In the case where the side portions are annular, the rocker arm element (e.g., a pair of rocker arm elements) forms two circular segments within the circle enclosed by these side portions. Within the enclosing circle minus the circular segments of the rocker arm element, there is a mounting space for the energy storage source. The energy storage source is preferably arranged such that the central mounting space is completely filled (in the case of a helical spring with a straight spring axis, through an envelope, for example, a cylindrical shape).

[0031] In an advantageous embodiment of the pendulum rocker damper, it is also proposed that the input side and the output side are arranged axially adjacent to each other, wherein the input side and / or the output side preferably comprises two separate partial elements.

[0032] This implementation allows for a particularly radially compact design. For example, the outer circumferences of the input and output sides are (approximately or completely) identical. In one implementation, the inner circumferences of the input and output sides, i.e., the extensions toward the rocker arm element, are (approximately or completely) identical, wherein the arrangement of the corresponding mating tracks is mirrored in a (preferably) symmetrical implementation due to opposite torsional angles. In one implementation, the input and output sides are structurally identical (possibly differing only in their axial mounting lengths). In one implementation, the input and output sides overlap axially, or vice versa, such that the overlapping input or output sides are supported relative to the axis of rotation and can be supported around an axial distance corresponding to (and possibly slightly less than) the mounting length of the rocker arm damper. This produces a high level of stiffness to resist tilting moments transverse to the axis of rotation. In one implementation, three or more separate roller tracks are arranged on the rocker arm element, and a corresponding number of separate mating tracks are arranged on the sides, and separate running surfaces are arranged on the rolling elements.

[0033] In an advantageous embodiment, one of the sides, such as the output side, is configured as a pair of separate partial elements, which are then arranged axially adjacent to the corresponding other side, such as the input side. In one embodiment, the two separate partial elements are not connected to each other, but only functionally together to form the corresponding side, which is distributed by a geared connection of a rolling element and a rocker arm element. Thus, the two partial elements always move synchronously with each other. As an alternative to the separate operating mode, a connector (e.g., by means of spacer bolts) is formed between the two partial elements of the relevant side, radially outside or within the core diameter of the pendulum damper (in which the rocker arm element is arranged) of the core diameter. The embodiment with a connector within the core diameter is advantageous for small relative torsional angles.

[0034] In an advantageous embodiment of the pendulum rocker arm damper, it is also proposed that the energy storage source comprises at least one helical compression spring having a straight spring axis, wherein the spring axis is preferably arranged to extend between the input-side rolling element and the output-side rolling element.

[0035] This particularly simple implementation allows for cost-effective design and separation of structural components for a few purposes. The helical compression spring, also configured as a rolling element by means of a rocker arm element, applies minimal preload to provide support against tilting moments laterally to the axis of rotation of the rocker arm damper, and (its primary function) to provide the necessary reaction force to resist relative rotation between the input and output sides. In a preferred embodiment, two rocker arm elements are arranged diametrically opposite each other, and one or more helical compression springs are aligned such that their (corresponding) spring axes are parallel to the shortest distance between the two rocker arm elements. The resulting helical gear results in increased compression of the helical compression spring as the torsional angle between the input and output sides increases, producing an increased reaction force (proportional to displacement). The helical compression spring exhibits low energy dissipation and can be designed in a simple manner to resist overload, for example, the helical compression spring is designed to safely prevent breakage under load on the block and / or the maximum spring deflection can be limited by means of a stop (e.g., a stop on the rocker arm element). Helical compression springs can also be manufactured at low cost with very precisely adjustable displacement-force characteristics (e.g., compared to blocks of rubber elastic material), or sold on the market as standard parts and unaffected by any signs of aging that must be considered over a sufficiently long service life. The ultimate load of the helical compression spring is also easily taken into account in the design, for example, by means of maximum spring deflection up to the load on the block.

[0036] In an advantageous embodiment, the spring axis of at least one helical compression spring is arranged between the rolling elements of the corresponding rocker arm element (e.g., two), preferably approximately (e.g., deviating by no more than 3 mm [three millimeters]) centered or exactly centered, particularly preferably intersecting the axis of rotation or having a small offset (e.g., a maximum of ±0.5 mm [plus / minus half a millimeter]). In one embodiment, two or more helical compression springs are arranged nested within each other, for example having the same spring axis, wherein one of the two helical compression springs preferably guides the other helical compression spring, and only one of the two helical compression springs is mounted transversely to the spring axis. In one embodiment, the helical compression spring at its relaxed length is shorter than the shortest distance (when the torsion angle is zero) between the rocker arm elements supported by each other by means of a stored energy source. The two rocker arm elements only make force-transmitting contact with the (short) helical compression spring when the two sides are at a predetermined torsion angle relative to each other. This also results in a (stepped) increase in stiffness in the transmission characteristics of the pendulum rocker damper and / or creates a protective mechanism to prevent load or overload on the block of another (long-term and permanent force-transmitting contact) helical compression spring. This short helical compression spring can also be combined with another implementation of an energy storage source element.

[0037] A pendulum rocker arm damper with at least one helical compression spring in the central position as an energy storage source allows for high wire thickness, which translates to very high energy. This energy is converted into individually adjustable transmission characteristics via rolling elements. Due to the presence of pure rolling and therefore no friction in the rolling contact, there is virtually no hysteresis. The stiffness variation of the helical compression spring is minimal. This ensures high-quality insulation throughout its service life. The roller tracks and complementary mating tracks allow for modular implementation of any characteristic without replacing the helical compression spring.

[0038] In an advantageous embodiment of the pendulum rocker arm damper, it is also proposed that the wire diameter of at least one of the helical compression springs deviates from the roller diameter of the rolling element at the running surface by less than 20%, preferably the wire diameter is more than 5% larger than the roller diameter, wherein the wire diameter is preferably greater than 5 mm, and the core diameter formed by the outer periphery of the rocker arm element is less than 80 mm, preferably less than 40 mm.

[0039] The pendulum rocker arm damper proposed herein features a helical compression spring with a high level of stiffness relative to its overall size or transmittable torque. In a preferred embodiment, the helical compression spring is the sole force-transmitting element at the maximum transmittable torque (by design), i.e., no parallel structures (e.g., stops and / or additional energy storage elements) are provided. For example, a maximum torque of 1.5 kNm [1.5 kNm] can be transmitted via the helical compression spring, wherein, for example, a maximum spring force of 5 kN [5 kN] to 30 kN is applied to the helical compression spring, and the helical compression spring still has free spring deflection capability and is therefore not loaded onto the block.

[0040] In an advantageous embodiment, the core diameter of the pendulum rocker damper is less than 80 mm, preferably less than 40 mm. The outer diameter of the pendulum rocker damper or the component described herein is preferably less than 100 mm, for example, about 60 mm. The core diameter is determined by the outer periphery of the rocker element in the installed case, wherein the core diameter corresponds to the diameter of a circle about the axis of rotation, which is arranged tangent to the (outward) maximum radial extension of the rocker element. Alternatively, the core diameter is the diameter of a circle passing through the rolling axis of the outermost (e.g., all) radially outermost rolling element in the installed case. The installed case is a state with no torsional angle between the input and output sides. Then, the wire diameter of at least one of the helical compression springs is preferably greater than 5 mm, and the wire diameter is particularly preferably about 10 mm. Then, the roller diameter of the rolling element is, for example, 9.5 mm, wherein the deviation from the wire diameter is –5% (minus five percent). In one embodiment, the axial installation length of the pendulum rocker arm damper is less than 100 mm, preferably about 50 mm. The rolling element is preferably exactly the same length as or slightly shorter than the axial installation length of the pendulum rocker arm damper.

[0041] In an advantageous embodiment of the pendulum rocker arm damper, it is also proposed that at least one rocker arm element has a recess in its receiving surface for receiving at least one helical compression spring in the helical compression spring, preferably receiving an internally located helical compression spring.

[0042] The recess provides a secure guide for the helical compression spring. Compared to the nose, the recess allows for the reception of a longer helical compression spring, and thus allows for greater spring deflection capacity and / or spring stiffness. The recess is also advantageous when the rocker arm element is manufactured by casting or sintering for reliable molding. In a preferred embodiment, only the innermost (or most innermost) helical compression spring is received by means of the recess. The other helical compression springs are preferably guided only by the helical compression springs guided by the recess. In one embodiment, the helical compression springs are designed such that they never contact each other when they are designed to function. Alternatively, the helical compression springs contact only when a limit load is reached, for example, when at least one of the helical compression springs is subjected to a block load. In one embodiment, friction between the helical compression springs is expected to arise from a predetermined load, resulting in energy dissipation. This energy dissipation preferably occurs only within the outer limits of the relative torsional angle, and not at the zero-crossing point. At the zero-crossing point, hysteresis is therefore (almost) zero. However, safety limitations and / or an increase in reaction force or counter-torque can occur at large torsional angles (compared to the maximum torsional angle according to the design).

[0043] In an advantageous embodiment of the pendulum rocker arm damper, it is further proposed that the maximum relative torsional angle between the input side and the output side is less than 10°, preferably less than 5°.

[0044] While previously known pendulum-type rocker arm dampers used in transmission systems of rotating shafts require a maximum torsional angle of ±20° [based on 360° plus / minus 20 degrees] to ±30° and low stiffness of 200 Nm [two hundred Newton-meters] to 300 Nm, this provides a very high stiffness of approximately 1.5 kNm (as described above) and a low torsional angle preferably less than ±10° [plus / minus 10 degrees] or even less than ±5°, for example, ±3° to ±4°. This pendulum-type rocker arm damper can, for example, be used as the sole damping device in the torque flow for a roll stabilizer without the need for other measures. Other values ​​can be achieved depending on the installation space and the mass or force on this roll stabilizer. Furthermore, a transmission curve with (virtually) no hysteresis can be achieved, thus exhibiting, for example, unique and, for instance, soft transmission characteristics for small torsional angles (e.g., in motor vehicles, when driving on uneven roads) and unique and, for instance, hard transmission characteristics for large torsional angles (e.g., when cornering with high lateral acceleration in motor vehicles). When driving over a pothole, low torque occurs in the roll stabilizer because only the weight of the wheel assembly is affected. With low stiffness (corresponding to low torque) transmission characteristics, these torques are not transmitted to the other wheel on the axle, or are transmitted under high damping conditions. During cornering, the entire vehicle mass accelerates (laterally) to the outside of the curve, resulting in significantly higher torque then occurring in the roll stabilizer. These torques are then transmitted to the other wheel, which has high stiffness transmission characteristics (corresponding to high torque).

[0045] In an advantageous embodiment of the pendulum rocker arm damper, it is also proposed that, by means of roller tracks and mating tracks, at the maximum relative torsional angle between the input and output sides according to the design, the maximum spring deflection of the stored energy source is approximately 1 mm to 10 mm, preferably up to a maximum of 6 mm.

[0046] The spring deflection of the energy storage source should be as small as possible to achieve a highly compact pendulum damper. For some applications, a pendulum damper with high (maximum) stiffness and a low maximum torsional angle is also required (e.g., as described above). This relationship can be achieved due to the track used for the rolling element, i.e., the helical gear, and can also be individually adapted to the required characteristic curves in each case. In advantageous embodiments, the energy storage source, which is always structurally identical or has only been slightly modified, can be used for different transmission characteristics. Only the geometry of the helical gear needs to be adjusted. Alternatively, only the energy storage source must be replaced to achieve the desired transmission characteristics with the same performance but different forces or torques. In the event of any necessary changes to the energy storage source and / or the helical gear, the required installation space is particularly preferably always the same. This means that the pendulum damper can be used in a large number of different vehicles with different masses and / or can still be adjusted effortlessly later during development, and can be used in many different applications.

[0047] According to another aspect, a roll stabilizer for axle of a motor vehicle is proposed, the roll stabilizer having at least the following components:

[0048] -At least one wheel spring connector;

[0049] - At least one pendulum rocker arm damper, preferably at least one pendulum rocker arm damper according to the embodiments described above.

[0050] The at least one wheel spring connector is connected to the pendulum rocker arm damper via torque transmission.

[0051] The pendulum rocker arm damper includes an input side, an output side, multiple rocker arm elements, a corresponding number of rolling elements, and a stored energy source. The rolling elements are held in a rolling manner between the roller tracks of the rocker arm elements and the paired tracks of the input or output side by means of the stored energy source. Preferably, an actuator is provided, and more preferably, a multi-stage planetary gear is provided in the torque flow between the actuator and the pendulum rocker arm damper. The at least one wheel spring connector is connected to the actuator by means of the pendulum rocker arm damper in a torque transmission manner.

[0052] In a classic implementation, a roll stabilizer is arranged between a first wheel spring connected, for example, via a first torsion bar, and a second wheel spring connected, for example, via a second torsion bar, and the roll stabilizer is configured to regulate the transmission of compressive or rebound forces between the two wheels of the (common) axle, for example, via a MacPherson strut on the (preferably steering) front axle. Each spring strut or torsion bar is connected in a force-transmitting manner to a wheel mount for one wheel of the common axle. In non-adjustable and passive implementations of the roll stabilizer, the two torsion bars are connected to each other or formed as a single element. In the roll stabilizer described herein, torque transmission is guided from one wheel spring to the other wheel spring via a pendulum damper by means of a corresponding wheel spring connector. The pendulum damper is inserted to dampen or suppress the up-and-down movement of one of the two wheels (e.g., due to uneven ground) transmitted to the other wheel of the common axle.

[0053] In the active implementation of the roll stabilizer, an actuator is also provided. The actuator is, for example, an electric motor. The actuator is preferably supplied with the required power voltage from outside the roll stabilizer, for example, by the vehicle's onboard power supply. In one implementation, a controller and / or a necessary sensor system for the actuator are integrated into the roll stabilizer. In one implementation, a separate roll stabilizer is provided for each wheel, such that only one wheel spring connector is provided in each case. This wheel spring connector is connected to the actuator by means of a swing arm damper. The sensor system records any compression or rebound of the wheel, which is torque-transmitted. The determined value is transmitted purely electronically to the actuator of the corresponding other roll stabilizer on the common axle, and there the actuator generates torque for transmission to the wheel spring connector there.

[0054] For good responsiveness and reduced noise in roll stabilizers, the use of a swing arm damper is particularly advantageous. The swing arm damper provides the required damping by means of its helical gears. Noise causes uncertainty for the vehicle driver, especially when encountering uneven surfaces that may trigger such noise. The swing arm damper is preferably the only damping device in the torque flow between two wheel spring connections or between the actuator and one or more wheel spring connections. The swing arm damper is formed without rubber-elastic damping elements. The swing arm damper includes multiple rocker arm elements, a corresponding number of rolling elements, and a stored energy source, wherein helical gears are formed by the rocker arm elements on the input and / or output sides. The torque directed to resist rotation of the input side relative to the output side is applied by the stored energy source, which preferably includes at least one helical compression spring, and particularly preferably only one helical compression spring. The rolling element is held in a rolling manner between the roller track of the rocker arm element and the mating track on the input or output side by means of a stored energy source. The pendulum rocker arm damper is designed, for example, as in the previously known implementation of the pendulum rocker arm damper mentioned earlier. The pendulum rocker arm damper can be designed such that the hysteresis performance is negligible. Therefore, the noise that occurs in the roll stabilizer can be effectively avoided or reduced to a sufficient degree. In a preferred embodiment, the pendulum rocker arm damper is designed according to the embodiments described above. The pendulum rocker arm damper offers the advantage of being particularly compact, thus preferably requiring less installation space compared to previously known rubber elastic damper devices used in conventional roll stabilizers. In addition, this pendulum rocker arm damper can be manufactured at low cost and can be flexibly adapted to a variety of different requirements without having to change the required installation space for this purpose.

[0055] In an advantageous embodiment, a multi-stage planetary gear is inserted into the torque flow between the actuator and the swing arm damper in the active roll stabilizer. This allows the use of inexpensive and very compact actuators with (too) low maximum torque for (undriven) use in the roll stabilizer. The multi-stage planetary gear enables a large gear ratio within minimal possible installation space. In one embodiment, a three-stage planetary gear is provided.

[0056] According to another aspect, a motor vehicle is proposed having a drive engine, at least one axle, and at least one roll stabilizer according to the above-described embodiment on at least one of the axles.

[0057] The quality of motor vehicles is becoming increasingly problematic, both in so-called sport utility vehicles (SUVs) and in electrified motor vehicles with large traction batteries. Additionally, there is a growing demand for high driving safety, including, for example, good roll stability on paved roads for precise cornering and a high level of ride comfort (and thus, increased sense of security). At the same time, due to the complexity of today's motor vehicles and a growing lack of understanding of what is happening inside them while driving, drivers are becoming more sensitive to the development of (unknown) noise.

[0058] In the motor vehicle presented herein, an active roll stabilizer is proposed, which features a compact swing arm damper and operates silently in all operating states. Compared to previously known roll stabilizers with rubber-elastic damper devices, this roll stabilizer can be designed to the same or smaller size, and therefore can be used as a replacement for previously known roll stabilizers in motor vehicles, for example, it can also be replaced during maintenance cycles when conventional roll stabilizers, for example, show signs of wear and tear.

[0059] Passenger vehicles are categorized based on factors such as size, price, weight, and performance, with the definition constantly evolving based on market demand. In the US market, according to the European classification, J-class (SUV) vehicles are designated as ranging from small SUVs to full-size SUVs, while in the UK market, J-class (SUV) vehicles correspond to either the 4x4 class or the Coupe SUV class. Examples of small SUVs include the Dacia Duster and Opel Mokka. Examples of large 4x4s include the Porsche Cayenne, Mercedes-Benz M-Class, and Ford Explorer. A well-known all-electric SUV is the Tesla Model X. Attached Figure Description

[0060] The invention described above will now be described in detail with reference to the accompanying drawings, which illustrate preferred embodiments, and in light of the relevant technical background. The invention is in no way limited to the drawings, which are merely illustrative; it should be noted that the drawings are not precise in size and are not intended to be to a limited scale. In the drawings:

[0061] Figure 1 A pendulum rocker arm damper is shown in a front view.

[0062] Figure 2 The cross-sectional view shows the results based on... Figure 1 Swing-type rocker arm damper;

[0063] Figure 3 : Shows according to Figure 1 and Figure 2Exploded view of a pendulum rocker arm damper;

[0064] Figure 4 This demonstrates the achievable transfer characteristics;

[0065] Figure 5 It shows that it has the following characteristics: Figures 1 to 3 Active roll stabilizer with pendulum rocker arm damper; and

[0066] Figure 6 The image shows a motor vehicle with two roll stabilizers. Detailed Implementation

[0067] Figure 1 A front view of a pendulum rocker arm damper 1 is shown, by means of which the input side 3 (here covered, see central rotation axis 2, which is annular) about the central rotation axis 2. Figure 2 and Figure 3 The torsional angle 30 between the input side 3 and the output side 4 (which is also annular) about the central rotation axis 2 is converted into a straight spring deflection 31 along the spring axis 20. This is achieved by means of a helical gear, which in this embodiment is formed by two rocker arm elements 6 with opposite diameters or by means of the roller tracks 7, 8 (on the input side 3 and the output side 4) of the rocker arm elements, paired tracks 11, 12, and rolling elements 9, 10 arranged between the roller tracks and the paired tracks (see See). Figure 3 The roller tracks 7 and 8 of the rocker arm element 6 point radially outward, and in this embodiment, the input side 3 and the output side 4 are arranged radially outward relative to the rocker arm element 6. It should be noted that due to the torsional angle 30 (not equal to zero) between the input side 3 and the output side 4, the rocker arm element 6 tilts relative to the sides 3 and 4 from the illustrated rest position. However, the rocker arm elements 6 remain aligned (at least nearly) with each other along the spring axis 20, that is, perpendicular to the spring axis, or, as described, with a slight lateral offset of the receiving surface 29 relative to each other. The rocker arm elements 6 move toward each other under the applied torsional angle 30 (not equal to zero), as indicated by the indicated spring deflection 31.

[0068] Rolling elements 9 and 10 are pressed against their respective roller tracks 7 and 8 and their respective mating tracks 11 and 12 by means of the energy storage source 5, making it possible for only rolling motion to occur as relative motion between the respective rolling elements 9 and 10 and the rocker arm element 6 and their respective sides 3 and 4. When the pendulum rocker arm damper 1 operates as designed, sliding motion of the respective rolling elements 9 and 10 that does not rotate about the rolling axis 41 is eliminated (here, for clarity, only the lower rolling elements 9 and 10 are specified according to the illustration). In this embodiment, the energy storage source 5 includes an outer helical compression spring 18 and an inner helical compression spring 19 having a common spring axis 20. The spring axis 20 is arranged perpendicular to the receiving surface 29 of the rocker arm element 6, and the preload force of the helical compression springs 18 and 19 is thus guided vertically into the rocker arm element 6. The spring axis 20 intersects the rotation axis 2 or is arranged slightly offset from the rotation axis 2. The preload force of the stored energy source 5 is then introduced into the associated rolling elements 9 and 10 via the corresponding roller tracks 7 and 8, and from there into the associated mating tracks 11 and 12 of the associated sides 3 and 4. In a preferred embodiment, this stable dynamic balance is achieved such that in each case the force on the rolling elements 9 and 10 is directed (at least approximately) perpendicular to the tangent (in the direction of the track) to the current contact line with the corresponding tracks 7, 8, 11, and 12. The force then passes through the rolling elements 9 and 10 in diametrical terms (i.e., intersecting the rolling axis 41).

[0069] exist Figure 2 In the middle, a cross-sectional view is shown according to Figure 1 The pendulum rocker arm damper 1, such as its in Figure 1 As shown in the diagram. At the top of the figure, the (output side) scroll element 10 is shown in a simplified form with dashed lines, while on the opposite side (below), the (input side) scroll element 9 is mostly covered and therefore not indicated here (see Figure 1). Figure 1It is readily apparent here how the two helical compression springs 18, 19, having a common spring axis 20, are arranged between the receiving surfaces 29 of the rocker arm element 6, one inside the other, and thus clamped to generate a preload force and a torque opposite to the relative rotation. The wire diameter 21 of the outer helical compression spring 18 is slightly larger than the (effective) roller diameter 22 of the rolling elements 9, 10. Sides 3, 4 are arranged radially outward, where the sides are formed in a ring-like manner as an (one-piece) input side 3 in the axial center and an output side 4 having a first part element 16 and a second part element 17, in each case the output side being axially adjacent to the input side 3. The torque applied via the input side 3 reaches the output side 4 via the input side rolling element 9, via the rocker arm element 6, and again via the output side rolling element 10. The (rocking) motion of the rocker arm element 6 generated in this way is opposite to the spring force of the energy storage source 5 (see...). Figure 1 (Spring deflection 31 in the middle). In order to guide or retain the helical compression springs 18, 19 against lateral forces, in this advantageous embodiment, recesses 28 are optionally provided in the receiving surface 29 of the rocker arm element 6. Each end of the inner helical compression spring 19 is received in these recesses 28. The inner helical compression spring 19 guides the outer helical compression spring 18 on its outer cylindrical periphery. A core diameter 27 is formed radially inside the annular sides 3, 4, which corresponds to the (maximum) outer periphery of the rocker arm element 6 in the illustrated mounting configuration. The core diameter 27 is very small (e.g., the core diameter is measured to be about 40 mm [forty millimeters]), but a maximum torque of 1.5 kNm [1.5 kilonewton-meters] or greater can be obtained in the case of relative torsion of the input side 3 and the output side 4 about the axis of rotation 2. Preferably, the maximum torsion angle 30 (by design) is less than ±6° [plus / minus six degrees].

[0070] Figure 3 It shows that according to Figure 1 and Figure 2 An exploded view of the pendulum rocker arm damper 1. Besides the already explained components of the pendulum rocker arm damper 1, the track is clearly visible here:

[0071] - On the upper rocker arm element 6 (as shown in the figure), a two-part output-side roller track 8 can be seen at the front, and an axially central input-side roller track 7 can be seen at the rear. The same applies to the lower rocker arm element 6, which rotates about the axis of rotation 2 and is preferably the same as the upper rocker arm element 6. Thus, in each case, the output-side roller track 8 is formed by a first part track 13 and a second part track 14, which are arranged axially outward. In each case, the input-side roller track 7 is formed by a third part track 15, which is arranged axially centrally between the other two first part tracks 13 and 14.

[0072] - On the input side 3 at the axial center, two (input side) paired tracks 11 can be seen facing each other. The input side paired tracks 11 are therefore formed by a third (axial center) paired track 44 in each case.

[0073] - On the two-part output side 4, in each case, two (output side) mating tracks 11, 12 opposite to each other can be seen on each part element 16, 17. In each case, the output side mating track 12 is thus formed by a first part mating track 42 (on the first part element 16 of the output side 4) and a second part mating track 43 (on the second part element 17 of the output side 4), that is, axially outward relative to the third part mating track 44.

[0074] Furthermore, the corresponding running surfaces can also be seen on the rolling elements 9 and 10:

[0075] - On the input-side rolling element 9 (as shown in the figure, the front input-side rolling element is at the top and the rear input-side rolling element is at the bottom), in each case, the input-side second running surface 25 for rolling on the input-side mating track 11 (third mating track 44) can be seen axially centered, and the input-side first running surface 23 for rolling on the input-side roller tracks 7 (first track 13 and second track 14) can be seen axially outward. Purely optional, the (input-side) running surfaces 23, 25 of the input-side rolling elements 9 are separated from each other here by means of shoulders, thus forming an axial support arrangement or protective portion.

[0076] - On the output-side rolling element 10 (as shown in the figure, the front output-side rolling element is at the bottom and the rear output-side rolling element body is at the top), in each case, the first output-side running surface 24 for rolling on the output-side roller track 8 (third part track 15) can be seen axially centered, and the second output-side running surface 26 for rolling on the output-side mating track 12 (first part mating track 42 and second part mating track 43) can be seen axially outward. Purely optional, the (output-side) running surfaces 24, 26 of the output-side rolling element 10 are also separated from each other here by means of shoulders, thus forming an axial support arrangement or protective portion.

[0077] Furthermore, here Figure 3 The recess 28 in the receiving surface 29 of the lower rocker arm element 6, as shown in the figure, can be clearly seen. (As already shown...) Figure 2As seen in this advantageous embodiment, the recess 28 is designed to receive only the inner helical compression spring 19 and the area of ​​the receiving surface 29 surrounding the recess 28 is designed to receive only the outer helical compression spring 18.

[0078] Figure 4 It is shown that a pendulum rocker arm damper 1 (e.g.) can be used Figures 1 to 3 The transfer characteristic 45 is implemented in (as shown in one of the figures). This transfer characteristic 45 is for the roll stabilizer 32 (e.g., as shown in the figure). Figure 5 The following (shown) is useful. The horizontal axis 46 is plotted in degrees, for example from –6° to +6°. The vertical axis 47 is plotted in kilonewton-meters, for example from –1.5 kNm to +1.5 kNm. The transfer characteristic 45 is flat and approximately straight around the zero cross 48 (i.e., with an approximately constant gradient). This achieves soft-response behavior with a small torsional angle 30. From a predetermined torsional angle 30, for example –4° or +4°, a sudden transition is formed, but a constant gradient is transferred to the steep portion and is also approximately straight (i.e., the stiffness increases rapidly). Within a small range of torsional angle 30 (e.g., from +4° to +6° or –4° to –6°), the torsional stiffness increases tenfold (or more) (e.g., from approximately 0.15 kNm to 1.5 kNm). It should be noted that the transfer characteristic 45 can be set as needed over a wide range. Additionally, with proper design, the hysteresis of the transfer characteristic 45 can be negligible, as shown. For example, the hysteresis at zero crossover 48 is less than 0.5 Nm [0.5 Nm].

[0079] Figure 5 It shows that it has the following characteristics: Figures 1 to 3 An example of the active roll stabilizer 32 of the pendulum rocker arm damper 1. The roll stabilizer 32 has, for example, a left wheel spring connector 36 for the left torsion bar 49 (partially shown) and a right wheel spring connector 37 for, for example, the right torsion bar 50 (partially shown). The naming of the sides is arbitrary and is chosen here without excluding the generality of representation. The left wheel spring connector 36 is connected to an actuator 38, which is designed as a motor, via its stator 52 in a torque-transmitting manner through the housing 51. The rotor 53 of the actuator 38 is connected to the output side 4 of the pendulum rocker arm damper 1 in a torque-transmitting manner via planetary gears 39, which include a first planetary gear 54, a second planetary gear 55, and a third planetary gear 56 connected in series. The input side 3 of the pendulum rocker arm damper 1 is in turn connected to the right wheel spring connector 37 in a torque-transmitting manner. Therefore, the torque transmission connection between the left wheel spring connector 36 and the right wheel spring connector 37 is formed only via the actuator 38, the planetary gear 39, and the pendulum rocker arm damper 1. In this way, on the one hand, torque transmission is achieved by means of the pendulum rocker arm damper 1, for example, according to... Figure 4The transmission characteristic 45 shown is damped and / or adjusted. On the other hand, the planetary gears 39 and actuator 38 prevent the small torque deflection and hysteresis performance resulting from conventional damping devices. Torque can also be generated by means of actuator 38, such that a torque greater (conversely) than that generated by actuating wheels 57, 58 (or torsion bars 49, 50) can be transmitted to the two wheel spring connections 36, 37. Actuator 38 is controlled here by means of an internal sensor system, which here is, for example, a magnetoelastic torque sensor 59 and a rotor position sensor 60.

[0080] exist Figure 6 The vehicle 35 is shown schematically in a top view, with a roll stabilizer 32 on each of the axles 33 and 34. In this vehicle 35, the rear axle 34 (along the vehicle's longitudinal axis 61) is driven by a (e.g., purely electric) drive engine 40. The front axle 33 is (for example only) a steering axle used to control the direction of travel of the vehicle 35 from the driver's cab 62 via a steering wheel 63. For example, if the left wheel 57 of axles 33 and 34 is compressed due to a turn (as shown here on the left), this relative upward movement of the left wheel 57 (i.e., on the outside of the curve) toward the body of the vehicle 35 is converted into torque in the left torsion bar 49 and transmitted to the roll stabilizer 32. There, the torque (optionally actively amplified) is transmitted to the right torsion bar 50 (on the inside of the curve). Therefore, the unloaded spring strut of the right wheel 58 is loaded and thus forms an abutment for the loaded left wheel 57. This reduces the tendency of vehicle 35 to roll. Vehicle 35 passes through the (left-hand) curve with a low roll rate. On the other hand, if only uneven ground causes wheels 57, 58 to move up and down, the resulting torque is absorbed by the rocker arm damper 1 or significantly reduced due to its smoothness. Vehicle 35 therefore does not sway.

[0081] The pendulum rocker arm damper proposed in this paper is compact and can produce high torsional stiffness. The roll stabilizer can operate with reduced noise.

[0082] List of reference numerals

[0083] 1. Swing arm damper 34. Rear wheel axle

[0084] 2 Rotation axis 35 Motor vehicles

[0085] 3 Input side 36 left wheel spring connector

[0086] 4 Output side 37 Right wheel spring connector

[0087] 5 energy storage sources and 38 actuators

[0088] 6 rocker arm components 39 planetary gears

[0089] 7 input side roller track 40 drive motor

[0090] 8 Output side roller track 41 Rolling axis

[0091] 9 Input side rolling element 42 First part mating track

[0092] 10 Output side rolling element 43 Second part mating track

[0093] 11 Input-side pairing track 44 Third part pairing track

[0094] 12 Output-side Paired Rails 45 Transmission Characteristics

[0095] 13 Part 1 Track 46 x-coordinate

[0096] 14 Part Two Track 47 Vertical Coordinate

[0097] 15 Part 3 Track 48 Zero Crossing

[0098] 16 First Part Components (Output Side) 49 Left Torsion Bar

[0099] 17 Part Two Components (Output Side) 50 Right Torsion Bar

[0100] 18 External helical compression springs 51 Housing

[0101] 19 Internal helical compression spring 52 stator

[0102] 20 spring shaft 53 rotor

[0103] 21 wire diameter 54 first row star

[0104] 22 rollers, 55mm diameter, second row of stars

[0105] 23 Input side first running surface 56 Third row star level

[0106] 24 Output side first running surface 57 Revolver

[0107] 25 Input side second running surface 58 Right wheel

[0108] 26 Output side second operating surface 59 Magnetoelastic torque sensor

[0109] 27-core, 60mm diameter rotor position sensor

[0110] 28. Recessed portion; 61. Vehicle longitudinal axis

[0111] 29 receiving surface 62 cab

[0112] 30-degree torsion angle, 63-degree steering wheel

[0113] 31 Spring Deflection

[0114] 32 Roll stabilizer

[0115] 33 front axle

Claims

1. A pendulum rocker arm damper (1) having a rotation axis (2), the pendulum rocker arm damper comprising at least the following components: - Input side (3); - Output side (4); - A storage energy source (5) for transmitting torque between the input side (3) and the output side (4); - Multiple rocker arm elements (6), each rocker arm element having an input-side roller track (7) and an output-side roller track (8); and - Multiple input-side rolling elements (9) and multiple output-side rolling elements (10), the number of the input-side rolling elements (9) corresponding to the number of the input-side roller tracks (7) of the rocker arm element (6), and the number of the output-side rolling elements (10) corresponding to the number of the output-side roller tracks (8) of the rocker arm element (6). in, The input side (3) has input side mating tracks (11), each of which corresponds to a corresponding input side roller track in the input side roller tracks (7). Each input side rolling element (9) is held in a rotatable manner between the input side mating track and the input side roller track by means of the stored energy source (5). The output side (4) has output side mating tracks (12), each of which corresponds to a corresponding output side roller track in the output side roller tracks (8). Each output side rolling element (10) is held in a rotatable manner between the output side mating track and the output side roller track by means of the stored energy source (5). Its features are, Each of the rocker arm elements (6) includes three separate partial tracks (13, 14, 15), which are arranged to be axially offset relative to each other, and the input side roller track (7) and the output side roller track (8) are formed by the three separate partial tracks respectively.

2. The pendulum rocker arm damper (1) according to claim 1, wherein, The input-side roller track (7) and the output-side roller track (8) are each arranged on the radial outer side of the rocker arm element (6).

3. The pendulum rocker arm damper (1) according to claim 1 or 2, wherein, The input side (3) and the output side (4) are arranged axially adjacent to each other. The input side (3) and / or the output side (4) include two separate partial elements (16, 17).

4. The pendulum rocker arm damper (1) according to claim 1, wherein, The energy storage source (5) includes at least one helical compression spring (18, 19) having a straight spring axis (20). The spring axis (20) is arranged to extend between the input-side rolling element (9) and the output-side rolling element (10).

5. The pendulum rocker arm damper (1) according to claim 4, wherein, The wire diameter (21) of at least one of the helical compression springs (18, 19) deviates by less than 20% from the roller diameter (22) of the input-side rolling element (9) or the output-side rolling element (10) at the running surfaces (23, 24, 25, 26). The diameter (21) of the wire is greater than 5 mm, and the diameter (27) of the core formed by the outer periphery of the rocker arm element (6) is less than 80 mm.

6. The pendulum rocker arm damper (1) according to claim 4, wherein, At least one of the rocker arm elements (6) has a recess (28) in its receiving surface (29) for receiving at least one of the helical compression springs (19).

7. The pendulum rocker arm damper (1) according to claim 1, wherein, The maximum relative torsional angle (30) between the input side (3) and the output side (4) is less than 10°.

8. The pendulum rocker arm damper (1) according to any one of the preceding claims, wherein, With the aid of the input-side roller track (7), the output-side roller track (8), the input-side matching track (11), and the output-side matching track (12), the maximum spring deflection (31) of the energy storage source (5) is about 1 mm to 10 mm at the maximum relative torsion angle (30) between the input side (3) and the output side (4) according to the design.

9. A roll stabilizer (32) for use on the axles (33, 34) of a motor vehicle (35), the roll stabilizer having at least the following components: - At least one wheel spring connector (36, 37); - At least one pendulum rocker arm damper (1) according to any one of the preceding claims. in, The at least one wheel spring connector (36, 37) is connected to the pendulum rocker arm damper (1) in a torque transmission manner. The device also provides an actuator (38) and a multi-stage planetary gear (39) in the torque flow between the actuator (38) and the pendulum damper (1), wherein at least one wheel spring connector (36, 37) is connected to the actuator (38) by means of the pendulum damper (1) in a torque-transmitting manner.

10. A motor vehicle (35), said motor vehicle having: The drive engine (40), at least one axle (33, 34), and at least one roll stabilizer (32) according to claim 9 located on at least one of the axles (33, 34).

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