DE102018104888A1 - Roll stabilizer for a motor vehicle - Google Patents

Abstract

The invention relates to a roll stabilizer (1) for a motor vehicle, comprising a first stabilizer half (2a) and a second stabilizer half (2b), wherein the two stabilizer halves (2a, 2b) can be connected to one another by means of an actuator (3) in order to provide a torsional moment wherein the actuator (3) comprises a motor unit (4) and a gear unit (5), wherein the first stabilizer half (2a) with a first at least partially toothed end portion (6a) in a first at least partially toothed recess (7a) of a motor flange (8) of the motor unit (4) is axially joined, wherein the second stabilizer half (2b) with a second at least partially toothed end portion (6b) in a second at least partially toothed recess (7b) of a planetary carrier (11) of the transmission unit (5) axially is added in order to produce a splines for rotationally fixed connection of the respective stabilizer half (2a, 2b) on the actuator (3).

Description

The invention relates to a roll stabilizer for a motor vehicle, comprising a first stabilizer half and a second stabilizer half, wherein the two stabilizer halves are connected to each other by means of an actuator to transmit a torsional moment, wherein the actuator comprises a motor unit and a gear unit.

Usually, each wheel axle of a motor vehicle on a roll stabilizer, which operates on the torsion bar principle. The roll stabilizer is arranged substantially parallel to the respective vehicle axle and connected at both ends via a respective coupling rod with the wheel suspension. Furthermore, the roll stabilizer is provided to stabilize the body structure against unwanted rolling movements about the longitudinal axis of the motor vehicle. Such rolling movements occur, for example, when cornering or off-road driving of the motor vehicle. The rolling motion of the motor vehicle is influenced by the roll stabilizer by the compression movement of the left and right wheel suspension of an axle is coupled together using the roll stabilizer. Thus, there is a copying effect between the compression movements of the two wheels on the axle.

From the DE 10 2011 053 277 A1 a stabilizer with an integrated actuator is known which has an electromechanical drive which is arranged in a housing and is equipped with a measuring arrangement. The drive torque of the actuator is transferable to two output shafts, which are each connected to an associated stabilizer part of a stabilizer.

The object of the present invention is to simplify a connection of the stabilizer halves of a roll stabilizer on an actuator and in particular to form releasably. The object is solved by the subject matter of claim 1. Preferred embodiments are given in the dependent claims, the description and the figures.

An inventive roll stabilizer for a motor vehicle comprises a first stabilizer half and a second stabilizer half, wherein the two stabilizer halves are connected to each other by means of an actuator to transmit a torsional moment, wherein the actuator comprises a motor unit and a gear unit, wherein the first stabilizer half with a first at least partially toothed end portion is axially joined in a first at least partially toothed recess of a motor flange of the motor unit, the second stabilizer half is axially joined with a second at least partially toothed end portion in a second at least partially toothed recess of a planetary carrier of the gear unit to a splined engagement for rotationally fixed connection to produce the respective stabilizer half on the actuator.

In other words, the roll stabilizer is an active, electro-mechanical roll stabilizer. The two end portions of the respective stabilizer half are inserted by means of a Axialfügevorganges in the respective recess. This is to be understood that by the axial joining or plugging of the respective end portion into the associated recess, the interference toothing between the motor-side first stabilizer half and the motor flange or between the transmission side second stabilizer half and the planet carrier is generated. Due to the required accuracy of fit, the joining partners passing into the splines are heat-treated prior to the axial joining process and designed so precisely that a slight, preferably no backlash in the respective splines is ensured. Thus, the actuator is on the motor side with the first stabilizer half and the transmission side detachably connected to the second stabilizer half. Thus, the end portions of the two stabilizer halves can be produced with identical manufacturing processes, whereby the detachable formation of the connection of the stabilizer halves to the actuator and in particular the assembly and the transport of the roll stabilizer are simplified.

The torque or Torsionsmomentübertragung is realized by the meshing splines of the respective at least partially toothed end portion and the associated at least partially toothed recess of the planet carrier or the motor flange to couple a compression movement of the left and right suspension of an axle through the roll stabilizer and thus to allow a copying effect between the compression movements of the two wheels on the axle. Slippage of the components joined together is thus prevented by the splines. On the motor side, the torsional moment is conducted via the motor flange into an actuator housing, wherein the motor flange is preferably firmly welded to the actuator housing. On the transmission side, the torsion moment is passed from the second stabilizer half over the planet carrier in the gear unit, wherein by means of the gear unit in particular the stiffness of the roll stabilizer is adjustable. Thus, the first stabilizer half rotatably connected to the motor flange and the second stabilizer half rotatably connected to the planet carrier.

The term "at least partially toothed" is to be understood that a toothing on the respective end portion or on the respective recess is formed partially encircling. The respective toothing can also be formed fully rotating. Furthermore, it is conceivable to form the toothing over the entire axial length of the respective end section or over the entire axial length of the respective recess. However, the toothing can also be formed only over part of the axial length of the respective end section or the respective recess. The respective joining teeth forming the splines are preferably formed complementary to each other, so that an optimal torque or Torsionsmomentübertragung is realized.

According to a preferred embodiment, the two end portions are each externally toothed and the two recesses each formed internally toothed. The two end portions are further formed in each case in the solid cross-section, wherein alternatively a tubular design is conceivable.

Preferably, a union nut for axially securing the first stabilizer half is provided, wherein the union nut has a collar which comes to rest on a shoulder of the first stabilizer half, wherein the union nut further comprises an internal thread, which is screwed onto an external thread formed on the motor flange to the axially preloading the first stabilizer half and creating a detachable connection between the union nut and the motor flange. In other words, the axial forces occurring due to bending moments are absorbed by the union nut and transmitted to the motor flange and then passed through the weld between the motor flange and the actuator housing in the actuator housing. As a result, the union nut prevents the migration of the first stabilizer half from the first recess of the motor flange. The term "emigration" is to be understood that the respective stabilizer half due to axial forces, which arise in particular by bending moments occurring during operation, can slide axially out of the splines. The union nut also has additional geometries, such as holes, grooves, and / or flat surfaces, these geometries are preferably arranged on the outer surface of the union nut and in particular serve a tool engagement, so that a simple screwing the union nut is realized on the motor flange.

Further preferably, an axial ring is provided to secure the second stabilizer half axially on the planet carrier. The axial ring has an external thread and can be screwed at least partially into an internal thread of the actuator housing. The task of the axial ring is to secure both the planet carrier and the second stabilizer half axially and in particular to initiate axial forces in the actuator housing. In other words, the axial forces occurring due to bending moments in the second stabilizer half are transmitted through the axial ring on the actuator housing. Furthermore, the axial ring limits or prevents the axial migration of the second stabilizer half out of the second recess.

Preferably, a radial bearing element is arranged radially between the axial ring and the second stabilizer half, which is intended to rotatably support the second stabilizer half, as well as to support bending moments via the axial ring in an actuator housing. The radial bearing element is preferably already mounted on the second stabilizer half in the second recess before the Axialfügevorgang the second stabilizer half. In this case, the radial bearing element comes to a shoulder of the second end portion of the second stabilizer half to the plant, so that the radial bearing element is axially biased during assembly of the axial ring.

The invention includes the technical teaching that the axial ring has a ring element for indirect axial prestressing of the planet carrier and a cover element for axially biasing the radial bearing element. Thus, the axial ring is formed at least in two parts, wherein the ring element at least partially receives the cover element and thus is firmly connected. When connecting the second stabilizer half to the actuator, first the ring element is screwed into the actuator housing. In this case, the ring element comes with an actuator facing end face on the planet carrier to the plant, wherein the planet carrier is rotatably supported by means of a separate roller bearing relative to the actuator housing. The rolling bearing of the planet carrier may for example be designed as a double-row angular contact ball bearings and is supported against the actuator housing. By screwing the Axialrings in the actuator housing thus the planet carrier is axially biased and secured. Subsequently, the second stabilizer half is inserted into the planet carrier of the gear unit in order to realize the meshing teeth. The cover element is arranged coaxially with the ring element and is at least partially received by the ring element. Furthermore, the ring element has threaded bores and the cover element has through holes, wherein screw elements can be screwed through the through bores of the cover element into the threaded bores in the ring element.

The radial bearing element between the second stabilizer half and the ring element ensures a further axial securing of the second stabilizer half within the planet carrier. In addition, the axial ring may further comprise a sealing element, which is arranged radially between the second stabilizer half and the cover element. The sealing element may be formed, for example, as a cartridge seal to seal an interior of the actuator against external influences, such as dirt and / or moisture.

According to a further preferred embodiment, a first circumferential groove for partially receiving a first snap ring is formed in the first recess of the motor flange, wherein the first snap ring at least partially protrudes into a second circumferential groove on the first end portion of the first stabilizer half to the first stabilizer half on the motor flange secure axially. The first snap ring thus protrudes into both the first and in the second groove and thus secures the first stabilizer half axially.

Preferably, in the second recess of the planet carrier, a third circumferential groove for partially receiving a second snap ring is formed, wherein the second snap ring projects at least partially into a fourth circumferential groove on the second end portion of the second stabilizer half to axially secure the second stabilizer half on the planet carrier. The second snap ring thus protrudes into both the third and in the fourth groove and thus secures the second stabilizer half axially. Since the two snap rings take part of the axial forces or the total axial forces due to the positive connection with the respective grooves, the union nut and / or the axial ring can be made slimmer or it can be completely dispensed with the union nut and / or the axial ring.

The invention includes you technical teaching that the first circumferential groove and the third circumferential groove have a larger outer diameter than the respective snap ring. During a Axialfügevorgangs in which the first and second end portion are pushed through the associated snap ring into the respective recess, the respective snap ring is initially at least partially received in the first and third groove of the respective recess. The larger outer diameter of the first and third groove allows the associated snap ring to be widened during the Axialfügevorgangs and snaps into the second and fourth groove of the respective end portion after reaching the corresponding axial position of the respective end portion. The term "widening" is to be understood as meaning an elastic deformation of the respective snap ring with an associated enlargement of the diameter. The snap ring is preferably formed interrupted, whereby a simple radial elastic expansion of the respective snap ring during the Axialfügevorganges is made possible.

• 1 eine vereinfachte schematische Ansicht eines erfindungsgemäßen Wankstabilisators,
• 2 eine vereinfachte schematische Längsschnittdarstellung einer ersten Stabilisatorhälfte und eines Aktuators des erfindungsgemäßen Wankstabilisators gemäß einer ersten Ausführungsform vor einem Axialfügevorgang,
• 3 eine vereinfachte schematische Längsschnittdarstellung zur Veranschaulichung der motorseitigen Anbindung der ersten Stabilisatorhälfte an den Aktuator nach dem Axialfügevorgang,
• 4 eine vereinfachte schematische Längsschnittdarstellung einer zweiten Stabilisatorhälfte und des Aktuators vor einem Axialfügevorgang,
• 5 eine vereinfachte schematische Längsschnittdarstellung zur Veranschaulichung der getriebeseitigen Anbindung der zweiten Stabilisatorhälfte an den Aktuator nach dem Axialfügevorgang,
• 6 eine vereinfachte schematische Längsschnittdarstellung zur Veranschaulichung der motorseitigen Anbindung der ersten Stabilisatorhälfte an den Aktuator nach dem Axialfügevorgang gemäß einer zweiten Ausführungsform,
• 7 eine vereinfachte schematische Längsschnittdarstellung zur Veranschaulichung der zweiten Stabilisatorhälfte und des Aktuators vor dem Axialfügevorgang, und
• 8 eine vereinfachte schematische Längsschnittdarstellung zur Veranschaulichung der getriebeseitigen Anbindung der zweiten Stabilisatorhälfte an den Aktuator nach dem Axialfügevorgang.

Further measures improving the invention will be described in more detail below together with the description of two preferred embodiments of the invention with reference to FIGS. It shows

• 1 a simplified schematic view of a roll stabilizer according to the invention,
• 2 2 shows a simplified schematic longitudinal sectional illustration of a first stabilizer half and of an actuator of the roll stabilizer according to the invention according to a first embodiment before an axial joining process,
• 3 a simplified schematic longitudinal sectional view for illustrating the motor-side connection of the first stabilizer half to the actuator after the Axialfügevorgang,
• 4 a simplified schematic longitudinal sectional view of a second stabilizer half and the actuator before a Axialfügevorgang,
• 5 a simplified schematic longitudinal sectional view for illustrating the transmission-side connection of the second stabilizer half to the actuator after the Axialfügevorgang,
• 6 2 is a simplified schematic longitudinal sectional illustration for illustrating the motor-side connection of the first stabilizer half to the actuator after the axial joining process according to a second embodiment,
• 7 a simplified schematic longitudinal sectional view illustrating the second stabilizer half and the actuator before Axialfügevorgang, and
• 8th a simplified schematic longitudinal sectional view illustrating the transmission-side connection of the second stabilizer half to the actuator after the Axialfügevorgang.

According to 1 includes a roll stabilizer 1 for a - not shown here - motor vehicle a first stabilizer half 2a and a second stabilizer half 2 B that have an actuator 3 are connectable to each other, to a torsional moment between the two stabilizer halves 2a . 2 B transferred to. The switchable roll stabilizer 1 is across to Vehicle longitudinal axis arranged and connected at its free ends to - not shown here - wheels or wheel carrier. The actuator 3 has a motor unit 4 and a transmission unit 5 on, with the first stabilizer half 2a motor side and the second stabilizer half 2 B Gearbox side on the actuator 3 are connected.

In the present show the 2 to 5 a first embodiment for connecting the respective stabilizer half 2a . 2 B to the actuator 3 ,

After the 2 and 3 has the first stabilizer half 2a a fully externally toothed first end portion 6a on. The engine unit 4 has a motor flange 8th on, the first stabilizer half 2a is facing. The motor flange 8th has a first recess 7a on, which is complementary to the first end portion 6a is fully internally toothed. The motor flange 8th is in the present case firmly with an actuator housing eighteen of the actuator 3 welded.

According to 2 lies the first stabilizer half 2a before an axial joining operation. At the first stabilizer half 2a is a union nut 10 arranged loosely, after the Axialfügevorgang for axially securing the first stabilizer half 2a is provided.

In 3 is the connection of the first stabilizer half 2a to the actuator 3 shown after the Axialfügevorgang. During the axial joining operation, the first end portion becomes 6a the first stabilizer half 2a in the first recess 7a inserted axially, thereby a spline between the first stabilizer half 2a and the engine flange 8th be generated. This can be a on the roll stabilizer 1 occurring torsional moment on the connection between the first stabilizer half 2a and the actuator 3 be transmitted. The external toothing of the first end section 6a and the internal teeth of the first recess 7a In the present case, they are designed in such a way that a backlash is prevented.

The union nut 10 in this case has an internal thread 14 and the motor flange 8th an external thread 15 on, with the union nut 10 for axial securing of the first stabilizer half 2a in a subsequent step on the motor flange 8th is screwed. The union nut 10 also has a radial collar 12 on, on a first shoulder 13a the first stabilizer half 2a comes to the plant, around the first stabilizer half 2a axially bias. Thus, there is a releasable connection between the first stabilizer half 2a and the actuator 3 in front. Disassembly of the first stabilizer half 2a First, by unscrewing the nut 10 from the motor flange 8th and then by axially pulling out the first end portion 6a from the first recess 7a of the motor flange 8th ,

After the 4 and 5 has the second stabilizer half 2 B a fully externally toothed second end portion 6b on. The gear unit 5 has a planet carrier 11 on, further comprising a second recess 7b which is complementary to the second end portion 6b is fully internally toothed. The planet carrier 11 is present through the motor unit 4 drivable and rotatable, the planet carrier 11 by a rolling bearing element 22 in the actuator housing eighteen is rotatably mounted. On the second stabilizer half 2 B is also a radial bearing element 17 arranged, which in the present case is designed as a deep groove ball bearing and on a second shoulder 13b of the second end portion 6b comes to the plant. The radial bearing element 17 relies on a multi-part formed axial ring 16 and is intended to provide bending moments over the axial ring 16 in the actuator housing eighteen to lead. Bending moments in the respective stabilizer half 2a . 2 B lead to an axial emigration of the respective end sections 6a . 6b from the corresponding recesses 7a . 7b , In other words, an additional support of these bending moments in turn leads to a reduction of the axial forces occurring.

According to 4 is the second stabilizer half 2 B before the axial joining process. First, a ring element 19 in the actuator housing eighteen screwed in, with the ring element 19 Part of the axial ring 16 is and an external thread 15 and wherein the actuator housing eighteen a corresponding internal thread 14 having. The ring element 19 comes on the rolling bearing element 22 axially to the plant and biases it axially.

Out 5 goes the connection of the second stabilizer half 2 B after the Axialfügevorgang and assembly out. During the Axialfügevorgangs the second end portion 6b the second stabilizer half 2 B in the second recess 7b joined, with a spline between the second stabilizer half 2 B and the planet carrier 11 be formed. This can be done on the roll stabilizer 1 occurring torsional moment via the connection between the second stabilizer half 2 B and the actuator 3 be transmitted. The external toothing of the second end portion 6b and the internal teeth of the second recess 7b In the present case, they are designed in such a way that a backlash is prevented.

After the Axialfügevorgang becomes a cover element 20 , which is also part of the axial ring 16 is, on the ring element 19 screwed. As a result, on the one hand, the radial bearing element 17 axial preloaded and centered. On the other hand, an additional support of the splines between the second stabilizer half 2 B and the planet carrier 11 generated. The axial ring 16 is therefore intended to the second stabilizer half 2 B axially on the planet carrier 11 secure as well as support radially. By screwing the axial ring 16 on the actuator housing eighteen Consequently, there is a releasable connection between the second stabilizer half 2 B and the actuator 3 in front. Disassembly of the second stabilizer half 2 B from the actuator 3 done by dismantling the axial ring 16 and by an axial withdrawal of the second end portion 6b the second stabilizer half 2 B from the second recess 7b of the planet carrier 11 , For sealing the actuator 3 against external influences, such as dirt and moisture, has the axial ring 16 beyond a sealing element 23 on, which is designed as a cassette seal and radially between the cover element 20 and the second stabilizer half 2 B is arranged.

The Axialfügevorgänge the two stabilizer halves 2a . 2 B are designed identically in this case, whereby the use of tools and the production times of the roll stabilizer 1 be reduced. Furthermore, by the detachable connection of the two stabilizer halves 2a . 2 B on the actuator a space-saving transport of the roll stabilizer 1 possible. Equally advantageous is the associated maintenance and repair.

According to the 6 to 8th is a second embodiment of the roll stabilizer 1 shown. The actuator 3 is formed analogously to the first embodiment, wherein the axial securing of the two stabilizer halves 2a . 2 B instead of with a union nut and a separate cover element, with a respective snap ring 21a . 21b he follows.

To 6 is the connection of the first stabilizer half 2a to the actuator 3 shown after the axial joining process, wherein the splines between the first end portion 6a and the engine flange 8th is present. The first recess 7a of the motor flange 8th has a first circumferential groove 9a for partially receiving the first snap ring 21a on. During the Axialfügevorganges is the first snap ring 21a first in the first groove 9a arranged, wherein the first groove 9a has a larger outer diameter than the relaxed and unloaded first snap ring 21a , Furthermore, the first snap ring points 21a in the unloaded state, a smaller inner diameter than the outer diameter of the first end portion 6a , Becomes the first end section 6a in the first recess 7a at the first snap ring 21a passed, this extends elastically until the desired axial position of the first stabilizer half 2a is reached, at the second circumferential groove 9b at the first end portion 6a is arranged so that the first snap ring 21a in the second groove 9b snaps. Thus, the first snap ring 21a then partly from the first groove 9a and partially from the second groove 9b absorbed and thus transmits the axial forces of the first stabilizer half 2a in the engine flange 8th or the other way around. In other words, the first end portion 6a with an axial joining force in the first recess 7a joined, wherein the axial joining force is designed so large that the radial expansion of the first snap ring 21a is possible. By means of the snapped-in first snap ring 21a So it will be the first stabilizer half 2a secured axially, wherein the transmittable axial force of the compound is designed to be greater than the actual axial force occurring within the roll stabilizer 1 or the first stabilizer half 2a ,

In the 7 and 8th Below is the connection of the second stabilizer half 2 B to the actuator 3 described in more detail. Analogous to the connection of the first stabilizer half 2a in 6 points the planet carrier 11 a third circumferential groove 9c and the second end portion 6b the second stabilizer half 2 B a fourth circumferential groove 9d for at least partially receiving the second snap ring 21b on.

7 shows the second stabilizer half 2 B before the axial joining process. In contrast to the first embodiment, the axial ring 16 only from the ring element 19 and the sealing element 23 , wherein the ring element 19 also takes over the task of a cover element. Before the Axialfügevorgang the axial ring 16 in the actuator housing eighteen screwed, wherein the radial bearing element 17 previously already in the axial ring 16 was arranged. Thus, all parts required for the connection are present at the axial position before the axial joining operation, so that the second stabilizer half 2 B in the planet carrier 11 can be joined.

To 8th is the connection of the second stabilizer half 2 B to the actuator 3 shown after the axial joining process, wherein the splines between the second end portion 6b and the planet carrier 11 is present. During the Axialfügevorganges is the second snap ring 21b first in the third groove 9c of the planet carrier 11 arranged, wherein the third groove 9c has a larger outer diameter than the relaxed and unloaded second snap ring 21b , Furthermore, the second snap ring 21b in the unloaded state, a smaller inner diameter than the outer diameter of the second end portion 6b , Will the second end section 6b in the second recess 7b at the second snap ring 21b passed, this extends elastically until the desired axial position of the second stabilizer half 2 B is reached. At this axial position, the second snap ring snaps 21b in the fourth groove 9d on. Thus, the second snap ring 21b then partly from the third groove 9c and partly from the fourth groove 9d absorbed and thus transmits the axial forces of the second stabilizer half 2 B in the planet carrier 11 or the other way around. In other words, the second end portion becomes 6b with an axial joining force in the second recess 7b joined, wherein the axial joining force is designed so large that the radial expansion of the second snap ring 21b is possible. By means of the snapped-second snap ring 21b so the second stabilizer half 2 B secured axially, wherein the transmittable axial force of the compound is designed to be greater than the actual axial force occurring within the roll stabilizer 1 or the second stabilizer half 2 B ,

The transmittable axial force of the connection between the respective end section 6a . 6b and the corresponding recess 7a . 7b is on the one hand dependent on the groove geometry of the respective grooves 9a . 9b . 9c . 9d , On the other hand, the transmittable axial force depends on the snap ring geometry of the respective snap ring 21a . 21b , For example, on the grooves 9a . 9b . 9c . 9d , at the respective end sections 6a . 6b and / or on the motor flange 8th or at the planet carrier 11 Chamfers be designed to assemble or disassemble the respective stabilizer half 2a . 2 B to simplify. The transmissible axial force is the axial load caused by the positive connection between the respective snap ring 21a . 21b and the corresponding groove 9a . 9b . 9c . 9d can be recorded without the respective snap ring 21a . 21b unintentionally radially expands or even fails. The required pull-off force for disassembly of the respective stabilizer halves 2a . 2 B on the other hand, it is greater than the frictional force of the splines and larger than the transmittable axial force.

LIST OF REFERENCE NUMBERS

1

roll stabilizer

2a, 2b

stabilizer half

3

actuator

4

motor unit

5

gear unit

6a, 6b

end

7a, 7b

recess

8th

motor flange

9a, 9b, 9c, 9d

groove

10

Nut

11

planet carrier

12

Federation

13a, 13b

shoulder

14

inner thread

15

external thread

16

axial ring

17

Radial bearing element

18

actuator housing

19

ring element

20

cover element

21a, 21b

snap ring

22

Rolling element

23

sealing element

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102011053277 A1 [0003]

Claims (9)

A roll stabilizer (1) for a motor vehicle, comprising a first stabilizer half (2a) and a second stabilizer half (2b), wherein the two stabilizer halves (2a, 2b) are connectable to one another by means of an actuator (3) in order to transmit a torsional moment, wherein the Actuator (3) has a motor unit (4) and a gear unit (5), characterized in that the first stabilizer half (2a) with a first at least partially toothed end portion (6a) in a first at least partially toothed recess (7a) of a motor flange ( 8) of the motor unit (4) is axially joined, wherein the second stabilizer half (2b) with a second at least partially toothed end portion (6b) axially into a second at least partially toothed recess (7b) of a planet carrier (11) of the transmission unit (5) is to produce a splines for rotationally fixed connection of the respective stabilizer half (2a, 2b) on the actuator (3). Roll stabilizer (1) after Claim 1 , characterized in that the two end portions (6a, 6b) each externally toothed and the two recesses (7a, 7b) are each formed internally toothed. Roll stabilizer (1) according to any one of the preceding claims, characterized in that a union nut (10) for axially securing the first stabilizer half (2a) is provided, wherein the union nut (10) has a collar (12) which on a shoulder (13 ) of the first stabilizer half (2a) comes into abutment, wherein the union nut (10) further comprises an internal thread (14) which on a motor flange (8) formed external thread (15) can be screwed to bias the first stabilizer half (2a) axially and to create a releasable connection between the union nut (10) and the motor flange (8). Roll stabilizer (1) according to one of the preceding claims, characterized in that an axial ring (16) is provided to axially secure the second stabilizer half (2b) on the planet carrier (11). Roll stabilizer (1) after Claim 4 , characterized in that radially between the axial ring (16) and the second stabilizer half (2b) a radial bearing element (17) is arranged, which is intended to rotatably support the second stabilizer half (2b), and bending moments on the axial ring (16) in an actuator housing (18) support. Roll stabilizer (1) after Claim 5 , characterized in that the axial ring (16) has a ring element (19) for the indirect axial prestressing of the planetary carrier (11) and a cover element (20) for the axial prestressing of the radial bearing element (17). Roll stabilizer (1) according to one of the preceding claims, characterized in that in the first recess (7a) of the motor flange (8) a first circumferential groove (9a) for partially receiving a first snap ring (21a) is formed, wherein the first snap ring ( 21a) projects at least partially into a second circumferential groove (9b) at the first end portion (6a) of the first stabilizer half (2a) to axially secure the first stabilizer half (2a) to the motor flange (8). Roll stabilizer (1) according to one of the preceding claims, characterized in that in the second recess (7b) of the planet carrier (11) has a third circumferential groove (9c) for partially receiving a second snap ring (21b) is formed, wherein the second snap ring ( 21b) protrudes at least partially into a fourth circumferential groove (9d) on the second end portion (6b) of the second stabilizer half (2b) to axially secure the second stabilizer half (2b) to the planetary carrier (11). Roll stabilizer (1) according to one of Claims 7 or 8th , characterized in that the first and the third circumferential groove (9a, 9c) and a larger outer diameter than the respective snap ring (21a, 21b).

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