Actuator assembly for friction disc clutch and differential assembly with same

Abstract

The invention relates to an actuator assembly comprising: a housing portion (3) having a sleeve-shaped portion (5) and a flange-shaped portion (6); a ball ramp mechanism (4) having a support ring (7) and a setting ring (8), wherein at least the support ring (7) is radially spaced from the outer face (36) of the sleeve-shaped portion (5); an actuating element (17) which is held coaxially with respect to the ball ramp mechanism (4) in an axially displaceable manner on the flange-shaped portion (6) of the housing part (3); an annular gap formed between the outer face (36) of the sleeve-shaped portion (5) and the actuating element (17); and a spring element (23), which is arranged radially outside of the actuating surface of the actuating element (17), axially between the housing part (3) and the actuating element (17), in order to exert a restoring force on the actuating element (17). The invention also relates to a differential assembly having such an actuator assembly.

Description

Technical Field

[0001] The present invention relates to an actuator assembly, in particular for actuating a controllable friction disc clutch for locking a differential transmission. The present invention also relates to a differential assembly having such an actuator assembly. Background Art

[0002] Friction disc clutches are used, for example, in lockable differential transmissions, in which, by operating the clutch, a locking torque is established between the differential case and one of the sideshaft gears and thus indirectly between the sideshafts. In this way, even if there is no reaction torque on one of the sideshaft gears, a torque introduced into the differential case can be effectively established on both sideshaft gears, respectively. A differential transmission of the type described can be used in a motor vehicle as an axle differential between the wheels of a driven axle or as a center differential between two driven axles. The applicant has also disclosed an electronically controlled torque manager. They are sold under the name of.

[0003] A differential transmission is known from WO 2005 / 064206 A1, in which a differential case has a cup-shaped case part in which the sideshaft gears and the differential gears are accommodated, and a cup-shaped cover attached to the case part in which the discs of the multi-disk clutch are accommodated. A ball ramp mechanism is provided for actuating the disc clutch, which is arranged outside the differential case on a sleeve part of the cover. The ball ramp mechanism converts a rotary motion into an axial motion, which is transmitted to a pressure plate of the disc clutch via several circumferentially distributed actuating elements, which extend axially through an opening in the cover.

[0004] A differential transmission with a controllable friction clutch is known from US 6537172 B1. The friction clutch is arranged axially adjacent to one of the output gears and can be operated between an engaged state, in which relative rotation between the output gear and the differential case is inhibited, and a disengaged state. The friction clutch can be controlled by an electromagnetically actuated ball ramp actuator, which is arranged adjacent to the opposite output gear. A plurality of elongated engagement portions distributed on the circumference are provided, which extend axially from the ball ramp actuator through the differential case to the friction clutch, so as to axially transmit the ramp effect of the ball ramp actuator to the friction clutch.

[0005] A differential arrangement with two friction clutches for variable torque distribution between two shafts in a drive train of a motor vehicle is known from WO 2007 / 071314 A1. Each of the two friction clutches can be controlled by a ball ramp arrangement which can be actuated by a common actuator.

[0006] From EP 3354920 A1 a transmission arrangement with a friction disk clutch is known which can be controlled by a ball ramp arrangement.

[0007] From DE 102014113937 B3 a transmission system with a pusher shaft is known which can be selectively connected or disconnected by means of a clutch. The upstream clutch comprises a friction plate pack and can be actuated by a ramp arrangement. Summary of the invention

[0008] The invention is based on the object of proposing an actuator assembly, in particular for operating a controllable friction disk clutch, which has a simple and compact design. The invention also relates to a differential assembly having such an actuator assembly.

[0009] An actuator assembly is proposed as a solution, comprising: a housing member having a sleeve portion and a flange-shaped portion; a ball ramp mechanism having an axially supported support ring and an axially movable setting ring, wherein at least one of the support ring and the setting ring can be rotatably driven by a drive source, and the resulting rotational movement is converted into an axial movement of the setting ring, and wherein at least the support ring is radially spaced apart from the outer side of the sleeve portion of the housing member; an actuating element, which is coaxially and axially movably held on the flange portion of the housing member with the ball ramp mechanism, wherein an annular gap is formed between the outer side of the sleeve portion and the annular actuating element, wherein the annular actuating element is at least indirectly axially supported against the setting ring on one side and has an actuating surface for acting on a friction disc clutch on the other side; and at least one spring element, which is arranged radially outside (respectively outside) the actuating surface of the actuating element and axially between the housing member and the actuating element so as to exert an elastic restoring force on the annular actuating element that is opposite to the actuating force of the ball ramp mechanism.

[0010] The actuator assembly is particularly suitable for controlling the transmittable torque of a friction disc clutch in a motor vehicle transmission system; it may also be referred to as an actuator arrangement or an axial setting device. The clutch may be arranged inside the housing and the actuator may be arranged outside the housing. In order to actuate / operate the clutch, a force transmission element, such as a bolt or a pin, may be provided in the housing, which extends through a through hole in the housing so as to transmit the actuating force from the actuator to the clutch. The through opening may extend through a flange-shaped portion forming a side wall of the housing. The actuator is reset (returned accordingly) via a spring element, wherein it is to be understood that one or more spring elements may be provided. The spring element is functionally arranged outside the force flow formed between the actuating element and the clutch, in particular the radially outer side / outside of the through opening and / or the force transmission element extending therethrough. This reduces the installation space between the housing and the actuating element by the space required for the spring.

[0011] The ball ramp assembly is rotatably driven by a drive source (e.g. a controllable electric motor) and is designed to convert the introduced rotational motion into axial motion. For this purpose, the setting ring and the support ring can each have a ball ramp, which has a reduced depth in the same circumferential direction when viewed from the end face. The balls are correspondingly accommodated in each pair of opposing ball grooves, and the setting ring and the support ring are axially supported against each other via the ball grooves. Therefore, the setting ring can be radially positioned relative to the support ring, preferably exclusively via the balls. The setting ring does not require an additional radial bearing, so that an annular gap can be formed between the outside of the sleeve part and the setting ring. This in turn has a positive effect on the design freedom of the sleeve part, which can be optimized in terms of installation space and stress.

[0012] According to one embodiment, the actuating element has a flange portion which comprises a pressure surface and has a radial overlap with the through-opening or the force transmission element, and a centering section which extends axially from the radially outer end of the flange portion and surrounds the housing portion. Due to this configuration, the actuating element also remains free, i.e. separate from the sleeve portion of the housing portion, which has the aforementioned advantages with regard to the design of the housing portion.

[0013] The centering section of the actuating element can have an inner circumferential surface which can be guided axially movably on the outer circumferential surface of the housing part. This means that the actuating element is radially centered relative to the housing part via the centering section extending in the axial direction and is guided axially movably. The centering section can be sleeve-shaped, i.e. have a circumferentially closed wall, or can include several guide elements distributed on the circumference and extending in the axial direction, which are clamped around the housing.

[0014] According to one embodiment, a receiving space for the spring element is formed between a flange portion of the actuating element and a side wall of the housing portion. The receiving space can have an axial extension that is greater than the minimum axial distance between a support surface of the actuating element and a side surface of the housing. This means that the axial length of the spring does not influence the arrangement of the actuating element, resulting in an overall axially compact design. The receiving space is preferably arranged radially outside, i.e. outside, the through-opening and / or the force transmission element extending therethrough.

[0015] The spring element can have any design suitable for moving the actuating element backward in the initial direction, counter to the operating direction of the setting ring. For example, the spring can be annular, arranged coaxially with the actuating element and radially held on the circumferential surface of the actuating element. In order to prevent sticking, the spring is arranged to have radial play relative to the circumferential surface of the portion defining the receiving space. The annular spring can be held radially outward relative to the inner circumferential surface of the centering section or radially inward relative to the outer circumferential surface of the shoulder of the housing or the sleeve protrusion (respectively the flange portion). In particular, the spring element can be designed as a wave spring or a disc spring, although other designs are also possible, such as several helical springs distributed around the circumference.

[0016] According to one embodiment, the axial bearing can be arranged between the setting ring and the actuating element. The axial bearing (which can also be called a thrust bearing) transmits axial forces between the setting ring and the actuating element both in the closing direction and in the opening direction. At the same time, the axial bearing decouples the relative rotational movement of the two elements relative to each other. The axial bearing can be radially supported on the outer side of the actuating element so that a radial gap is radially formed on the inner side between the bearing and the housing. In order to accommodate the axial bearing, the actuating element can have an axially protruding collar in which the axial bearing is accommodated. Optionally, a washer can also be arranged between the actuating element and the axial bearing. The washer can be radially supported on the outer side of the actuating element via the collar. By designing the actuating element to have an external collar (respectively a sleeve) for centering on the housing and / or a collar for the axial bearing, the actuating ring is additionally strengthened and the elastic deformation caused by the force of the actuating ring is reduced. This leads to an improved response behavior of the clutch and forms a favorable load-bearing mode on the circumference during power transmission. This leads to a particularly long service life of the bearing.

[0017] According to one embodiment, the support ring of the ball ramp mechanism can be rotationally driven by a drive source, while the setting ring is rotationally fixed and axially movable. However, it is to be understood that other embodiments are also possible, for example, the setting ring is rotationally driven and axially movable, while the support disk is rotationally fixed and axially supported. The support ring and the setting ring have ball grooves whose depth varies in the circumferential direction on their facing end faces. The ball ramp mechanism can be designed so that the center of the ball retained in the ball groove has a radial overlap with the axial bearing and / or the support bearing for the support ring. This results in a favorable axial force transmission with a low tilting moment.

[0018] According to one embodiment, the sleeve-shaped part of the housing part has a bearing seat, on which the rotary bearing for the support ring is mounted. The housing part comprises a concave transition section between the axial side face and the bearing surface of the sleeve part, which extends axially from the side face at least as far as the setting ring. The transition section has a free outer face, preferably at least as far as the support ring, which means that no components are mounted on the housing part between the side face and the support ring or the support bearing. Thus, this section of the housing part, which is subjected to high forces during operation, can be designed to optimize the stresses, which also has a favorable effect on the service life of the arrangement.

[0019] In a further specification, the minimum outer diameter of the concave transition portion can be smaller than the outer diameter of the bearing seat for the rotating bearing. Alternatively or additionally, the concave transition portion can have a curvature, the radius of which is at least 0.5 times the minimum axial distance between the setting ring and the flange portion of the housing part, in particular at least 0.6 times the minimum axial distance. Alternatively or additionally, the minimum outer diameter of the concave transition portion can be smaller than the radius of the outer toothing, i.e. the outer ridge of the coupling hub. By one or more of these specifications, the load on the housing part in this section can be reduced.

[0020] The above object is also achieved by a differential assembly, which comprises: a differential transmission having a differential case, which can be rotatably driven about a rotation axis; a plurality of differential gears, which are rotatably supported in the differential case about a gear axis extending at a certain angle to the rotation axis; and a first sideshaft gear and an opposite second sideshaft gear, which are mounted in the differential case, coaxial with the rotation axis and meshingly engaged with the differential gear; a friction plate clutch, which has an outer plate and an inner plate, the outer plate is connected to the differential case in a rotationally fixed and axially movable manner, and the inner plate is connected to one of the first sideshaft gear and the second sideshaft gear in a rotationally fixed and axially movable manner, wherein the plate pack formed by the outer plate and the inner plate can be axially loaded via a pressure plate; and an actuator assembly designed according to one or more of the above embodiments. The differential case comprises a housing portion, on which the ball ramp assembly is arranged. A plurality of force transmission elements are arranged around the circumference, which extend axially through the through opening of the housing part in order to transmit the axial movement of the setting ring to the pressure plate of the disk package. The annular actuating element is particularly arranged between the setting ring and the force transmission element, and the force transmission element contacts the contact surface of the actuating element.

[0021] According to a first embodiment, the friction disk clutch and the ball ramp mechanism can be arranged on opposite sides of the differential case relative to a plane spanned by the differential gear axis. The circumferentially distributed force transmission elements extend axially through the differential case, respectively through the set section of the differential case and are axially guided therein. The differential case preferably comprises a first bearing seat and a second bearing seat for rotatably mounting in the differential housing via suitable bearing elements. The drive gear is firmly connected to the differential case for introducing torque. Preferably, the minimum axial distance between the first bearing seat and the second bearing seat is less than the median tooth diameter of the drive gear.

[0022] According to a second embodiment, the friction disk clutch and the ball ramp mechanism can be arranged on the same side of the differential case relative to the plane spanned by the differential gear axis. In this embodiment, the circumferentially distributed force transmission elements are shorter and extend through the side wall of the differential case and are axially guided therein. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The preferred embodiments are explained below with reference to the figures of the accompanying drawings. In this article:

[0024] Figure 1A shows a longitudinal section through an actuator assembly according to the invention, for example for a controllable friction disk clutch;

[0025] Figure 1B Shown from Figure 1A An exploded perspective view of an actuator assembly;

[0026] Figure 2A The first embodiment is shown in longitudinal section in a first sectional plane. Figure 1A and 1B The differential assembly of the actuator assembly shown;

[0027] Figure 2B Shown from Figure 2A A perspective view of a differential assembly;

[0028] Figure 2C The second sectional plane shows the longitudinal section from Figure 2A Differential assembly;

[0029] Figure 2D Shown from Figure 2A An exploded perspective view of a differential assembly;

[0030] Figure 3 The longitudinal section shows the second embodiment according to Figure 1A and 1B A differential assembly of an actuator assembly; and

[0031] Figure 4An actuator assembly according to the invention in a modified embodiment is shown in half longitudinal section. DETAILED DESCRIPTION

[0032] Described below Figure 1A and 1B An actuator assembly 2 according to the invention is shown, which may be used, for example, for actuating and / or operating a friction plate clutch in a motor vehicle transmission system.

[0033] The actuator assembly has a housing part 3 and a controllable ball ramp mechanism 4, which is arranged coaxially with the housing part and can be driven by a schematically illustrated drive source 9. The housing part 3 can be, for example, part of a gearbox or clutch housing and comprises, in particular, a sleeve-shaped part 5 and a flange-shaped part 6, which can also be simply referred to as a sleeve or flange part. The flange-shaped part 6 extends radially outwards from the sleeve-shaped part 5 and forms a side wall of the housing.

[0034] The ball ramp assembly 4 comprises a support ring 7 which is axially supported against the housing part 3 and a setting ring 8 which is axially movable relative to the support ring. In the present embodiment, the support ring 7 is rotatably driven by a drive source 9, while the setting ring 8 is held in a rotationally fixed manner by an anti-rotation element 55. For actuation, the support ring 7 has a toothed segment 10 into which a pinion 12 can engage for rotational drive. It is to be understood that other designs are also possible, for example with a rotatably driven setting ring or other forms of torque transmission, such as by a rack or spindle drive.

[0035] Each of the support ring 7 and the setting ring 8 has a plurality of ball grooves 15, 16 extending in the circumferential direction on the end faces 13, 14 facing each other, and a ball is guided in each ball groove. The balls are arranged in a cross-sectional plane different from that shown, and therefore cannot be seen here. The ball grooves 15, 16 are designed so that the rotational motion introduced into the support ring 7 by the drive source is converted into the axial motion of the setting ring 8, which can also be called an actuating ring. For this purpose, the setting ring 8 and the support ring 7 can each have a reduced depth in the same circumferential direction in a plan view seen on the end face. However, a design in which only one of the two disks has a ball groove is also possible. In the present case, the setting ring 8 is radially supported exclusively via balls relative to the support ring 7. Therefore, a radial bearing relative to the housing portion 3 is not required, so that in particular the sleeve-shaped portion 5 can be advantageously designed with respect to the loads occurring during operation.

[0036] The annular actuating element 17 is arranged to transmit forces between the ball ramp mechanism 4 and the component to be actuated. The actuating element 17 is held or arranged coaxially and axially movably on the guide section of the housing part 3 with the ball ramp mechanism 4. In more detail, the actuating element 17 has a flange portion 18 and a centering portion 19, the flange portion 18 is particularly used for axial force transmission, and the centering portion 19 is particularly used to center the actuating element 17 on the housing part 3.

[0037] The flange portion 18, which can also be referred to as an actuating portion, is axially supported on one side against the setting ring 8 and on the other side against a component to be actuated, such as a clutch. Thus, the axial movement of the setting ring 8 is transmitted to the component via the actuating element 17. It is to be understood that, on the one hand, one or more elements may be interposed between the setting ring 8 and the actuating element 17 and, on the other hand, one or more elements may be interposed between the actuating element and the component to be actuated. For particularly good axial force transmission, the flange portion 18 may have at least partial radial overlap with the ball grooves 15, 16 and / or the balls of the ball ramp mechanism 4.

[0038] The centering portion 19 extends from the radially outer end of the flange portion 18 in the axial direction and engages around the outer guide surface 20 of the housing part 3. The centering portion 19 of the actuating element 17 can in particular have an inner circumferential surface 22, which is guided axially movably on the outer circumferential surface of the housing part 3. Therefore, the outer circumferential surface forms the guide surface 20 for the actuating element 17 on the housing part. In general, the actuating element 17 is radially centered relative to the housing part 3 via the centering portion extending in the axial direction and is guided axially movably. The centering portion 19 is in particular designed in the shape of a sleeve, i.e. with a circumferentially closed wall, but other designs are also possible, for example with several circumferentially distributed retaining elements. With the centering portion 19, the actuating element 17 is advantageously radially centered on the outside and therefore does not contact the housing part 3 radially on the inside. Therefore, the housing part 3 can be designed to be load-optimized.

[0039] The actuator assembly 2 further comprises a spring element 23, which is arranged axially between the housing part 3 and the actuating element 17, so as to exert an elastic restoring force on the actuating element 17, which counteracts the actuating force of the ball ramp mechanism 4. The spring element 23 is designed in the present case as a wave spring arranged coaxially with the actuating element, wherein it is to be understood that other spring shapes as return springs are also possible. The spring element 23 is accommodated and / or radially retained in a receiving space 24 radially outside the flange part 18 and radially inside the centering part 19. Axially, the spring element 23 is arranged between the actuating element 17 and the side wall 25 of the housing part 3. The receiving space 24 has an axial extension greater than the minimum axial distance between the actuating face 26 of the actuating element and the side wall 25, respectively the side of the housing. For this purpose, the actuating element 17 has an offset portion 27 radially outside the actuating portion, which is axially offset relative to the actuating portion in the direction of the setting ring 8. However, alternative designs are also possible in which the flange portion 18 is stepless up to the centering portion 19, but the housing part 3 has a recess or step radially on the outside. Preferably, the receiving space 24 and / or the spring element 23 are arranged radially outside the actuating surface 26 of the actuating element 17 and functionally parallel to the actuating surface 26.

[0040] In the present embodiment, the forces are transmitted between the setting ring 8 and the actuating element 17 via an optional axial bearing 28, i.e. a thrust bearing. The axial bearing 28 is arranged coaxially with the ball ramp mechanism 4; it transmits the axial forces and decouples the relative rotational movement. The axial bearing 28 is supported radially relative to the actuating element 17. For this purpose, the actuating element 17 has an axially protruding, in particular circumferential collar 29 on its side facing the setting ring 8, which forms a recess 32 for the axial bearing 28. An optional washer 30 is also arranged between the actuating element 17 and the axial bearing 28. The washer 30 is also accommodated in the recess 32 formed by the circumferential collar.

[0041] By designing the actuating element 17 with a centering portion 19 (respectively an outer collar) on the side facing the housing, and / or with a collar section 29 (respectively an inner collar) on the side facing the ramp mechanism 4, a high level of rigidity is achieved and force-induced elastic deformations of the actuating element are reduced. This results in an improved response behavior of the clutch actuated thereby and in a favorable contact or load pattern on the circumference during power transmission.

[0042] The actuating element 17, the washer 30, the axial bearing 28, the support ring 7 and the setting ring 8 are radially spaced apart from the outer face 36 of the sleeve-shaped part 5 of the housing part. The support ring 7 of the ball ramp mechanism is axially supported against the sleeve part 5 of the housing part 3. The housing part 3 has a bearing seat 33, on which a rotary bearing 34 is mounted, which is particularly designed as a combined axial / radial bearing. The bearing 34 is axially supported against the sleeve-shaped part 5 by a retaining ring 54, although other designs are also possible. The housing part 3 has a concave transition section 35 between the flange-shaped part 6 and the bearing seat 33, which extends axially from the side as far as approximately the support ring 7. The transition section 35 has a free outer face 36, i.e., between the side and the rotary bearing 34, no components are arranged or mounted on the housing part 3. The minimum outer diameter D35 of the concave transition section 35 can be smaller than the outer diameter D33 of the bearing seat 33 for the rotary bearing 34. Optionally, the concave transition portion 35 may have a curvature whose radius R is at least 0.5 times the minimum axial distance L between the setting ring 8 and the flange portion 6 of the housing part 3, in particular at least 0.6 times the minimum axial distance L. These configurations help to reduce the loads on the housing part 3 in this section.

[0043] The actuator assembly 2 is particularly suitable for controlling a clutch for a transmission system of a motor vehicle, wherein the clutch can be arranged inside the housing part 3 and the actuator can be arranged outside the housing part 3. The actuator is reset (respectively restored) via a spring element 23, which is functionally arranged outside the force flow formed between the actuating element 17 and the clutch. This results in a particularly compact design.

[0044] Described below Figures 2A to 2D A differential assembly 37 according to the invention is shown, which has a friction disc clutch 41 that can be controlled by the actuator assembly 2 according to the invention. The controllable friction disc clutch provides limited slip in the differential assembly. The differential assembly may also be referred to as a differential arrangement or a differential unit or a limited slip differential.

[0045] The differential assembly 37, which can be driven by a drive shaft (not shown), is designed to transmit and / or distribute the introduced rotational movement to the two side shafts. The differential assembly 37 comprises a differential case 38, which is rotatably mounted about the axis of rotation A in a stationary differential housing (not shown) by means of suitable bearings. The differential case 38 consists of two parts and comprises a housing part 3 and a cover part 39, which are connected to each other at a connecting flange 40. A crown gear (not shown) which can be driven by a drive shaft of the motor vehicle can be attached to the connecting flange 40.

[0046] In the differential case 38, a plurality of differential gears 42 are rotatably mounted on pins or bolts 43 arranged perpendicular to the axis of rotation A, which pins or bolts 43 respectively rotate with the differential case 38 around the orbit. The differential gears 42 mesh with two sideshaft gears 44, 44', which in turn are connected to the associated sideshaft in a rotationally fixed manner. For this purpose, the sideshaft gears 44, 44' respectively have shaft splines 45, 45', into which the connecting journals of the associated sideshaft can engage in a rotationally fixed manner. The differential gears 42 and the sideshaft gears 44, 44' together form a differential gear set for transmitting torque from the differential case 38 to the two sideshafts. In order to accommodate the expansion forces, low-friction thrust washers 46, 46', which can also be called sliding washers, are provided between the sideshaft gears and the differential case 38.

[0047] In order to control the locking effect of the differential, a friction plate clutch 41 is provided, which is arranged in the cover part 39, but is not limited thereto. The clutch comprises an outer plate 47, which is connected to the differential case 38 in a form-fitting manner, i.e. in a rotationally fixed and axially movable manner, and an inner plate 48, which is connected to one of the two sideshaft gears 44' in a rotationally fixed and axially movable manner. The plate package formed by the outer and inner plates can be loaded axially via a pressure plate 49. The pressure is applied by means of Figure 1A and 1B 1 and 2. The actuator assembly 2 shown is controlled, to which reference is made in this respect to its description. The force is transmitted from the actuator to the pressure plate 49 via several force transmission elements 50 distributed around the circumference. The force transmission element is designed in particular as a bolt, which extends axially through a through hole 52 in the housing part 3. At one end, the bolt bears axially against the actuating element 17 and, at the other end, against the pressure plate 49. The axial movement of the setting ring 8 is transmitted to the pressure plate 49 via the thrust bearing, the actuating element and the force transmission element.

[0048] The pressure plate 49 acts on the plate pack, which reduces the differential movement between the sideshaft gear 44' and the differential case 38, and thus also between the two sideshaft gears 44, 44'. By correspondingly controlling the ball ramp mechanism 4, the torque that can be transmitted by the friction plate clutch 41 can be variably adjusted or controlled as required. The clutch can be completely open, so that the two sideshaft gears can rotate freely relative to each other ("open" differential), or completely closed, so that the balancing movement of the sideshaft gears is completely blocked ("closed" differential), or it can be operated in any intermediate state, so that the balancing movement between the sideshaft gears is partially blocked.

[0049] exist Figures 2A to 2DIn the embodiment shown, the friction disk clutch 41 and the ball ramp mechanism 4 are arranged on opposite sides of the differential case 38 relative to a plane E spanned by the differential gear axis B. Circumferentially distributed force transmission elements 50 extend axially through a fitting part 51 of the differential case 38 and are guided therein in an axially movable manner.

[0050] At its opposite ends, the differential case 38 comprises a first bearing seat 53 and a second bearing seat 53'. Corresponding bearings can be mounted to these bearing seats, with which the differential case 38 can be rotatably supported in a differential housing (not shown). The minimum axial distance L53 between the two bearings and / or bearing seats can be smaller than the average tooth diameter of the drive flange. The actuating element 17 is arranged at the end of the set section of the differential case 38 in an axially movable manner. The spring element and the axial bearing are accommodated in the actuating element. In general, the actuator assembly 2 according to the present invention in combination with the differential leads to particularly compact dimensions.

[0051] Figure 3 A differential assembly 37 is shown with a second embodiment of an actuator assembly 2 according to the invention. In terms of structure and mode of operation, this corresponds essentially to that shown in FIG. 2 , to which reference is made in this respect to the description. Identical and / or corresponding components are provided with the same reference numerals as in FIG. 2 .

[0052] In contrast to the above-described embodiment, the friction disk clutch 41 and the ball ramp mechanism 4 are arranged on the same side relative to the plane E spanned by the differential gear axis B in the differential case 38. In this embodiment, the circumferentially distributed force transmission elements 50 are shorter and extend axially through the side wall of the differential case 38. In this embodiment, the actuating element 17 is also arranged so that its centering portion 19 can be axially displaced on the outside of the differential case 38. In this embodiment, the differential case 38 comprises a pot-shaped housing part 39, in which the differential and the clutch are accommodated, and a housing part 3, which is formed as a cover part here. The housing part 3 has a connecting flange 56, which is inserted into a sleeve protrusion 57 of the pot-shaped housing part 39 and is firmly connected to the sleeve protrusion 57, in particular by means of a welded joint 58, but not limited thereto. In terms of its structure and mode of operation, the actuator assembly 2 corresponds to the actuator assembly shown in Figures 1 and 2, and reference is made to its description in this regard.

[0053] Figure 4 An actuator assembly 2 according to the invention is shown in a modified embodiment. This corresponds largely to the above Figure 1A to 1B The embodiments shown in , in this respect reference is made to the description thereof. Identical and / or corresponding details are provided with the same reference numerals as in the previous figures.

[0054] The only difference is that Figure 4The annular spring element 23 in the embodiment shown is not radially held on the inner circumference in the centering portion 19 of the actuating element 17, but on the outer circumference 11 of the shoulder 59 of the housing part 3. As in the above-described embodiments, the spring element 23 is arranged in the receiving space 24, in particular with radial play.

[0055] It is to be understood that the actuator assembly 2 (and accordingly the arrangement) according to the invention is not limited to the above-mentioned applications, but can be used in any other device in the transmission system of a motor vehicle. For example, the actuator assembly 2 according to the invention can also be used to actuate a suspended clutch or a so-called dual clutch arrangement, which does not require a differential.

[0056] Reference numerals list

[0057] 2 Actuator assembly

[0058] 3. Shell

[0059] 4-Ball Ramp Mechanism

[0060] 5 Sleeve-shaped part

[0061] 6 Flange part

[0062] 7 Support ring

[0063] 8 Setting ring

[0064] 9. Drive source

[0065] 10 Toothed segment

[0066] 11 Circumferential surface

[0067] 12 Small gear

[0068] 13 End face (7)

[0069] 14 End face (8)

[0070] 15 Ball slots (7)

[0071] 16 Ball slots (8)

[0072] 17 Actuating element

[0073] 18 Flange part

[0074] 19 Centering

[0075] 20 Guide surface

[0076] 21 Outer circumference

[0077] 22 Inner circumference

[0078] 23 Spring element

[0079] 24 Receiving Space

[0080] 25 Sidewall

[0081] 26 Actuation surface

[0082] 27 Offset

[0083] 28 Axial bearing

[0084] 29 Collar

[0085] 30 Washer

[0086] 31 Differential transmission

[0087] 32 recess

[0088] 33 Bearing seat

[0089] 34 Swivel bearing

[0090] 35 Transition

[0091] 36 Outside

[0092] 37 Differential assembly

[0093] 38 Differential case

[0094] 39 Shell / cover

[0095] 40 Connection flange

[0096] 41 Friction plate clutch

[0097] 42 Differential gear

[0098] 43 Bolt

[0099] 44,44' sideshaft gear

[0100] 45 Shaft spline

[0101] 46 Thrust washer

[0102] 47 Foreign disk

[0103] 48 inner plate

[0104] 49 Platen

[0105] 50 Force transmission element

[0106] 51 Set Part

[0107] 52 Through opening

[0108] 53,53' Bearing Seat

[0109] 54 Retaining ring

[0110] 55 Anti-rotation element

[0111] 56 Connection flange

[0112] 57 sleeve protrusion

[0113] 58 Connection / welding joint

[0114] 59 Shoulder

[0115] A Rotation axis

[0116] B Differential gear axis

[0117] E-Plane

[0118] L distance

[0119] R Radius

Claims

1. An actuator assembly, in particular for operating a friction disc clutch in a motor vehicle transmission system, comprising: A housing portion (3) having a sleeve-shaped portion (5) and a flange-shaped portion (6); A ball ramp mechanism (4) having a support ring (7) axially supported against the housing part (3) and an axially movable setting ring (8), wherein at least the support ring (7) is radially spaced apart from an outer surface (36) of the sleeve-shaped part (5) of the housing part (3), an actuating element (17) which is held coaxially with the ball ramp mechanism (4) on the flange-shaped part (6) of the housing part (3) in an axially displaceable manner, wherein an annular gap is formed between the outer surface (36) of the sleeve-shaped part (5) and the actuating element (17), wherein the actuating element (17) is at least indirectly axially supported against the setting ring (8) on one side and has an actuating surface (26) for acting on a friction disk clutch (41) on the other side, A spring element (23) is arranged radially outside an actuating surface (26) of the actuating element (17) and axially between the housing portion (3) and the actuating element (17) so as to exert an elastic restoring force on the actuating element (17) that is opposite to the actuating force of the ball ramp mechanism (4).

2. The actuator assembly according to claim 1, Features The flange-shaped portion (6) has a plurality of axial through openings (52) around the circumference, The actuating element (17) comprises a flange portion (18) and a centering portion (19), wherein the flange portion comprises an actuating surface (26) and has a radial overlap with the through opening (52), and the centering portion extends from the radial outer end of the flange portion (18) in the axial direction and surrounds the housing portion (3).

3. The actuator assembly according to claim 1 or 2, Features The centering part (19) has an inner circumferential surface (22) which is guided on an outer circumferential surface (21) of the housing part (3) in an axially displaceable manner.

4. An actuator assembly according to any one of claims 1 to 3, Features A receiving space (24) for the spring element (23) is formed between a flange portion (18) of the actuating element (17) and a side wall (25) of the housing portion (3), the receiving space (24) being arranged radially outside the axial through-opening (52).

5. An actuator assembly according to any one of claims 1 to 4, Features The spring element (23) is annular in shape and is radially held on the circumferential surface of the actuating element (17) or the housing (3).

6. An actuator assembly according to any one of claims 1 to 5, Features The spring element (23) is designed in the form of a wave spring.

7. An actuator assembly according to any one of claims 1 to 6, Features The support ring (7) can be rotatably driven by a drive source, and the setting ring (8) is held in a rotationally fixed and axially movable manner, wherein the support ring (7) and the setting ring (8) respectively have a plurality of ball grooves (15, 16) extending in the circumferential direction on their end faces (13, 14) facing each other, and a ball is guided in each ball groove, wherein the ball grooves (15, 16) are designed so that the rotational movement introduced into the support ring (7) is converted into the axial movement of the setting ring (8), Therein, an axial bearing (28) is arranged axially between the setting ring (8) and the actuating element (17), wherein the actuating element (17) has an axially protruding collar (29) against which the axial bearing (28) is radially supported.

8. The actuator assembly according to claim 7, Features The center point of the ball received in the ball groove (15, 16) has a radial overlap with the axial bearing (28).

9. An actuator assembly according to any one of claims 1 to 8, Features The sleeve-shaped part (5) of the housing part (3) has a bearing seat (33), on which a rotary bearing (34) for the support ring (7) is positioned, wherein the housing part (3) has a concave transition part (35) between the flange-shaped part (6) and the bearing seat (33) of the sleeve-shaped part (5), and the concave transition part extends axially from the side of the flange-shaped part (6) at least as far as the setting ring (8).

10. The actuator assembly according to claim 9, Features The minimum outer diameter (D35) of the concave transition portion (35) is smaller than the outer diameter (D33) of the bearing seat (33) for the rotary bearing (34), and / or The concave transition portion (35) has a curvature, the radius (R) of which is at least 0.5 times the minimum axial distance (L) between the setting ring (8) and the side wall of the housing part (3), in particular at least 0.6 times the minimum axial distance (L).

11. A differential assembly (37) comprising: A differential transmission device (31) comprises a differential case (38) rotatably driven about a rotation axis (A), a plurality of differential gears (42) rotatably supported in the differential case (38) about a gear axis (B) extending at a certain angle to the rotation axis (A), and a first side shaft gear (44) and an opposite second side shaft gear (44'), wherein the first side shaft gear (44) and the opposite second side shaft gear (44') are coaxially mounted in the differential case (38) with the rotation axis (A) and engage with the differential gears (42), A friction plate clutch (41) having an outer plate (47) and an inner plate (48), wherein the outer plate (47) is connected to the differential case (38) in a rotationally fixed and axially movable manner, and the inner plate (48) is connected to one of the first sideshaft gear (44) and the second sideshaft gear (44') in a rotationally fixed and axially movable manner, wherein the plate package formed by the outer plate (47) and the inner plate (48) can be axially loaded via a pressure plate (49), Features An actuating assembly (2) according to any one of claims 1 to 10, wherein the differential case (38) comprises a housing portion (3), the actuating assembly (2) being arranged on the housing portion, Therein, a plurality of force transmission elements (50) are provided distributed on the circumference, and the force transmission elements extend axially through a through opening (52) of the housing part (3) so as to transmit the axial movement of the setting ring (8) to the pressure plate (49) of the disk package.

12. The differential assembly according to claim 11, Features The actuating element (17) is arranged between the setting ring (8) and the force transmission element (50), wherein the force transmission element (50) is in contact with a contact surface of the actuating element (17).

13. The differential assembly according to claim 11 or 12, Features The friction plate clutch (41) and the ball ramp mechanism (4) are arranged on opposite sides of the differential case (38) relative to a plane (E) spanned by the differential gear axis (B), wherein circumferentially distributed force transmission elements (50) extend axially through the differential case (38) and are axially guided therein.

14. A differential assembly according to any one of claims 11 to 13, Features The differential case (38) has a first bearing seat (53) and a second bearing seat (53') so as to be rotatably mounted in a stationary differential housing via bearing elements. The differential case (38) has a connecting flange (40) to which the drive gear can be securely connected for introducing torque. Wherein, the minimum axial distance (L53) between the first bearing seat (53) and the second bearing seat (53') is smaller than the average diameter (D) of the connecting flange (40) or the driving gear.

15. A differential assembly according to any one of claims 11 to 14, Features The friction plate clutch (41) and the ball ramp mechanism (4) are arranged on the same side of the differential case (38) relative to a plane (E) spanned by the differential gear axis (B), wherein circumferentially distributed force transmission elements (50) extend axially through the side wall of the differential case (38) and are axially guided therein.

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