Actuator assembly for friction multi-plate clutch, and differential assembly including such actuator assembly
Patent Information
- Application Number
- JP2024143105
- Authority / Receiving Office
- JP · JP
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2023-08-25
- Filing Date
- 2024-08-23
- Publication Date
- 2025-03-07
Smart Images
Figure 2025031692000001_ABST
Abstract
Description
[Technical field]
[0001] The invention relates to an actuator assembly for operating a controllable friction multi-plate clutch, in particular for locking a differential transmission, and further to a differential assembly equipped with such an actuator assembly.
[0002] Friction multi-plate clutches are used, for example, in lockable differentials, in which a locking moment is generated between the differential case and one of the side shaft gears, and thus indirectly between both side shaft gears, by operating the clutch. In this way, the torque introduced into the differential case can be effectively generated in both side shaft gears, even if no counter moment is applied to one of the side shaft gears. Differentials of this type can be used in motor vehicles as an axle differential between the two driving wheels of one drive axle or as a center differential between two drive axles. Such differentials are also sold by the applicant under the name "Electronic Controlled Torque Manager" (ETM registered trademark).
[0003] In the differential transmission known from WO 2005 / 064206, the differential case has a cup-shaped case part in which the side shaft gears and the compensation gears are accommodated. The differential case further has a cup-shaped cover attached to this case part, in which the friction plates of the multi-plate clutch are accommodated. To actuate the multi-plate clutch, a ball ramp mechanism is provided, which is arranged outside the differential case in a sleeve part of the cover. The ball ramp mechanism converts the rotational movement into an axial movement, which is transmitted to the pressure plates of the multi-plate clutch via a number of circumferentially distributed actuating elements. The actuating elements extend axially through openings in the cover.
[0004] From US6537172 a differential transmission is known with a controllable friction clutch, which is arranged axially adjacent to one of the output gears and can be operated between an engaged state, i.e. a state in which the relative rotation between the output gear and the differential case is reduced, and a disengaged state. The friction clutch can be controlled by an electromagnetically operable ball ramp actuator, which is arranged adjacent to the opposite output gear. A number of elongated engagement portions are provided, distributed over the entire circumference, which extend axially from the ball ramp actuator through the differential case to the friction clutch, so that the ramp action of the ball ramp actuator is transmitted axially to the friction clutch.
[0005] From WO 2007 / 071314 a differential assembly is known for variable torque distribution between two shafts in a motor vehicle power train, with two friction clutches each controllable by a ball ramp assembly which can be operated by a common actuator.
[0006] From EP 3 354 920 A1 a transmission assembly is known which has a friction multi-plate clutch which can be controlled by means of a ball ramp assembly.
[0007] From DE 10 2014 113 937 a power train is known with a longitudinal drive shaft which can be optionally connected or disconnected by a clutch. The pre-connected clutch includes a friction plate unit and is operable by a ramp assembly.
[0008] The object of the present invention is to provide an actuator assembly for operating a friction multi-plate clutch, which is simple and compact in design, and which is particularly controllable. The invention furthermore relates to a differential assembly equipped with such an actuator assembly.
[0009] In order to achieve this object, an actuator assembly is proposed which comprises: a housing part with a sleeve-shaped part and a flange-shaped part; a ball ramp mechanism with an axially supported support disk and an axially movable actuating disk, at least one of which can be driven to rotate by a drive source, the introduced rotational movement being converted into an axial movement of the actuating disk, at least the support disk being spaced radially from an outer surface of the sleeve part of the housing part; an operating element which is axially movable and held in the flange part of the housing part coaxially to the ball ramp mechanism, an annular gap being formed between the outer surface of the sleeve part and the annular operating element, the annular operating element being axially supported on one side at least indirectly on the actuating disk and on the other side having an operating surface for pressing the friction multi-plate clutch; and at least one spring element which is arranged radially outside the operating surface of the operating element and between the housing part and the operating element in the axial direction in order to apply to the annular operating element a spring-elastic return force opposite to the operating force of the ball ramp mechanism.
[0010] The actuator assembly is particularly suitable for controlling the transferable torque of a friction multi-plate clutch arranged in the power train of a motor vehicle; the actuator assembly may also be called an "axial adjuster". The clutch may be arranged inside the housing, the actuator outside the housing. To operate the clutch, force transmission elements, for example pins or studs, may be arranged in the housing. Such force transmission elements extend through through-openings in the housing in order to transmit the actuating forces from the actuator to the clutch. These through-openings may extend through flange-shaped parts forming the side walls of the housing. The actuator is returned via spring elements, in which case one or more spring elements may of course be provided. The spring elements are functionally arranged outside the force transmission path formed between the actuating element and the clutch, in particular radially outside the through-openings or the force transmission elements extending through these through-openings. This reduces the construction space between the housing and the actuating element by the space required for the springs.
[0011] The ball ramp mechanism can be driven to rotate by a drive source, for example a controllable electric motor, and is designed to convert the introduced rotational movement into an axial movement. For this purpose, the working disk and the support disk can each have the same circumferential depth reduction in plan view relative to the end face. A ball is accommodated in each pair of ball grooves located opposite each other, via which the working disk and the support disk are axially supported relative to each other. In this case, the working disk is preferably supported radially relative to the support disk only via the balls. Since no separate radial support for the working disk is required, an annular gap can be formed between the outer surface of the sleeve part and the working disk. This advantageously has a favorable effect on the free construction space for the sleeve part, which can be constructed in an optimized manner in terms of construction space and stresses. The working disk and the support disk are formed in an annular shape and can also be called "working ring" and "support ring".
[0012] According to one embodiment, the operating element has a flange part including a pressure surface and having a radial overlap with the through opening or the force transmission element, and a centering part extending axially from the radially outer end of the flange part and surrounding the housing part, whereby the operating element is also freely positioned with respect to the sleeve part of the housing part, which provides the above-mentioned advantages with regard to the construction of the housing part.
[0013] The centering part of the operating element may have an inner circumferential surface which may be guided axially along the outer circumferential surface of the housing part. The operating element is thus radially centered and axially movably guided relative to the housing part via the axially extending centering part. The centering part may be sleeve-shaped, i.e. with an annular closed wall, or may comprise a number of axially extending guide elements distributed over the entire circumference, which surround the housing.
[0014] According to one embodiment, a receiving space for the spring element is formed between the flange of the operating element and the end wall of the housing part. In this case, the receiving space may have an axial extension greater than the minimum axial distance between the support surface of the operating element and the end face of the housing. In this way, the axial construction length of the spring does not influence the arrangement of the operating element, so that an overall axially compact design is obtained. The receiving space is preferably arranged radially outside the through-openings or the force transmission elements extending through these through-openings.
[0015] The spring element may have any design suitable for returning the operating element to its initial direction again in a direction opposite to the acting direction of the actuation disk. For example, the spring may be annular, arranged coaxially with respect to the operating element and held radially on the circumference of the operating element. To avoid jamming, the spring is arranged with radial play with respect to the circumference of the part defining the receiving space. In this case, the annular spring may be held radially outwardly with respect to the inner circumference of the centering part or radially inwardly with respect to the outer circumference of a shoulder or sleeve-shaped attachment on the housing or flange part. In particular, the spring element may be designed as a wave spring or a disc spring, in which case other designs are also possible, for example a number of coil springs distributed over the entire circumference.
[0016] According to one embodiment, a thrust bearing may be arranged between the actuation disk and the operating element. The thrust bearing transmits axial forces between the actuation disk and the operating element, and in the closing and opening directions. At the same time, the thrust bearing blocks the relative rotational movement of both elements relative to one another. The thrust bearing may be supported on the radial outside on the operating element, so that on the radial inside an annular gap is formed between the bearing and the housing. To accommodate the thrust bearing, the operating element may have an axially protruding collar, in which the thrust bearing is accommodated. Optionally, a washer may also be provided between the operating element and the thrust bearing. The washer may be supported radially on the outside of the operating element via a collar or a collar. By forming the operating element with an outer collar for centering in the housing or with a collar for the thrust bearing, the operating ring is additionally reinforced and the elastic deformation of the operating ring due to forces is reduced. This leads to improved response characteristics of the clutch and a favorable support pattern over the entire circumference during force transmission. This results in a particularly long service life for the bearings.
[0017] According to one embodiment, the support disk of the ball ramp mechanism can be driven to rotate by a drive source, whereas the working disk is non-rotatable and axially movable. However, other configurations are of course possible, for example, the working disk can be driven to rotate and axially movable, whereas the support disk is non-rotatable and axially supported. The support disk and the working disk have ball grooves on their mutually facing end faces, the depth of which varies in the circumferential direction. The ball ramp mechanism can be designed in such a way that the center points of the balls accommodated in the ball grooves have a radial overlap with the thrust bearing and / or the support bearing for the support ring. This results in an advantageous axial force transmission with only a small tilting moment.
[0018] According to one embodiment, the sleeve-shaped part of the housing part has a bearing seat on which a rotary bearing for the support ring rests. The housing part has a concave transition between the axial side surface and the bearing surface of the sleeve part, which transition extends axially from the side surface at least to the operating ring. This transition preferably has a free outer surface at least up to the supporting ring, i.e. no components are supported on the housing part between the end face and the supporting ring or supporting bearing. This section of the housing part, which is subject to high forces during operation, can therefore be designed or designed in an optimized manner in terms of stresses. This is also in favor of the service life of the assembly.
[0019] In a further specific configuration, the smallest outside diameter of the concave transition may be smaller than the outside diameter of the bearing seat for the rolling bearing. In an alternative or supplementary configuration, the concave transition may have a curvature with a radius corresponding to at least 0.5 times the smallest axial distance between the working disc and the flange of the housing part, in particular at least 0.6 times the smallest axial distance. In a further alternative or supplementary configuration, the smallest outside diameter of the concave transition may be smaller than the radius of the outer teeth on the clutch hub. One or more of these specific configurations may reduce the load on the housing part in this section.
[0020] The above-mentioned problems are further addressed by providing a differential transmission assembly comprising: The problem is solved by a differential transmission device comprising: a differential case that can be driven to rotate about a rotation axis, a plurality of differential gears supported in the differential case to be rotatable about gear axes extending at an angle to the rotation axis, a first side shaft gear supported in the differential case coaxially with the rotation axis and in tooth-row engagement with the differential gears, and a second side shaft gear located on the opposite side; a friction multi-plate clutch including outer friction plates connected to the differential case so as to be immovable relative to the differential case and axially movable, and an inner friction plate connected to one of the first and second side shaft gears so as to be immovable relative to the first and second side shaft gears and axially movable, wherein a friction plate unit formed from the outer friction plates and the inner friction plates can be axially pressurized via a pressure plate; and an actuator assembly formed according to one or more of the above-mentioned embodiments. In this case, the differential case comprises a housing part, in which the ball ramp mechanism is arranged. For transmitting the axial movement of the actuation discs to the pressure plates of the friction plate unit, a number of force transmission elements are provided distributed over the entire circumference, which extend axially through through-openings in the housing part. An annular operating element is arranged in particular between the actuation discs and the force transmission elements, the force transmission elements bearing against abutment surfaces provided on the operating element. A differential transmission assembly may also be called "differential assembly" or "differential unit" for short.
[0021] According to a first embodiment, the friction multi-plate clutch and the ball ramp mechanism may be arranged on opposite sides of the differential case with respect to a plane formed containing the differential gear axis. The circumferentially distributed force transmission elements extend axially through the differential case or the outer peripheral wall of the differential case and are guided axially therein. In order to be rotatably supported in the differential housing via suitable bearing elements, the differential case preferably comprises a first bearing seat and a second bearing seat. In order to introduce the torque, a drive gear is rigidly connected to the differential case. Preferably, the minimum axial distance between the first bearing seat and the second bearing seat is smaller than the average tooth diameter of the drive gear.
[0022] According to a second embodiment, the friction multi-plate clutch and the ball ramp mechanism can be arranged on the same side of the differential case with respect to a plane formed containing the differential gear axis, in which case the circumferentially distributed force transmission elements are shorter and extend through the side wall of the differential case and are axially guided therein.
[0023] Advantageous embodiments are explained below with reference to the drawings. [Brief description of the drawings]
[0024] [Figure 1A] 1 is a longitudinal section through an actuator assembly according to the invention, for example for a controllable friction multi-plate clutch; [Figure 1B] FIG. 1B is a perspective exploded view of the actuator assembly shown in FIG. 1A. [Figure 2A] FIG. 2 is a longitudinal cross-sectional view taken along a first cutting plane of a first embodiment of a differential assembly including the actuator assembly shown in FIGS. 1A and 1B. [Figure 2B]FIG. 2B is a perspective view of the differential assembly shown in FIG. 2A. [Figure 2C] 2B is a longitudinal cross-sectional view of the differential assembly shown in FIG. 2A taken along a second cutting plane. [Figure 2D] FIG. 2B is a perspective exploded view of the differential assembly shown in FIG. 2A. [Diagram 3] FIG. 2 is a longitudinal cross-sectional view showing a second embodiment of a differential assembly including the actuator assembly shown in FIGS. 1A and 1B. [Figure 4] FIG. 11 is a half-cut longitudinal sectional view showing a modified embodiment of an actuator assembly according to the present invention.
[0025] 1A and 1B, which are discussed together below, show an actuator assembly 2 according to the present invention, which may be used, for example, to operate a friction multi-plate clutch in the powertrain of a motor vehicle.
[0026] The actuator assembly comprises a housing part 3 and a controllable ball ramp mechanism 4. The ball ramp mechanism 4 is arranged coaxially relative to the housing part and is drivable by a diagrammatically illustrated drive source 9. The housing part 3 may be, for example, part of a transmission housing or a clutch housing and includes, in particular, a sleeve-shaped part 5 and a flange-shaped part 6. The flange-shaped part 6 extends radially outwardly from the sleeve-shaped part 5 and forms a side wall of the housing.
[0027] The ball ramp mechanism 4 comprises a support disk 7, which is axially supported on the housing part 3, and an actuating disk 8 which is axially movable relative to the support disk. In the present embodiment, the support disk 7 can be driven to rotate by a drive source 9, whereas the actuating disk 8 is held non-rotatable relative to it via anti-rotation means 55. For operation, the support disk 7 has a toothed segment 10, with which a pinion 12 can engage for rotational drive. Of course, other configurations are also possible, for example with a rotatingly drivable actuating disk or with other forms of torque transmission, for example with a rack or spindle gearing.
[0028] The support disk 7 and the working disk 8 have, respectively, on their mutually facing end faces 13, 14, a number of circumferentially extending ball grooves 15, 16 in which a ball is guided in each case. The balls are located in a different section plane and are therefore not visible in the drawing. The ball grooves 15, 16 are designed in such a way that the rotational movement introduced by the drive source into the support disk 7 is converted into an axial movement of the working disk 8. For this purpose, the working disk 8 and the support disk 7 may each have the same circumferential depth reduction in a plan view relative to the end faces. However, it is also possible for only one of the two disks to have ball grooves. In this embodiment, the working disk 8 is radially supported relative to the support disk 7 only via the balls. Thus, no radial support relative to the housing part 3 is required, so that the sleeve-shaped part 5 in particular can be designed advantageously with respect to the loads occurring during operation.
[0029] For the force transmission between the ball ramp mechanism 4 and the component to be operated, an annular operating element 17 is provided. The operating element 17 is held coaxially with respect to the ball ramp mechanism 4 and axially movable in a guide provided in the housing part 3. In a further specific embodiment, the operating element 17 has a flange portion 18, which is used in particular for the axial force transmission, and a centering portion 19, which is used in particular for centering the operating element 17 in the housing part 3.
[0030] The flange part 18, which may also be referred to as the actuating part, is supported axially on the actuating disk 8 on one side and on the component to be actuated, for example a clutch, on the other side. The axial movement of the actuating disk 8 is therefore transmitted to these components via the actuating element 17. Of course, one or more elements may also be intermediately connected between the actuating disk 8 and the actuating element 17 and between the actuating element and the component to be actuated. For a particularly good force transmission in the axial direction, the flange part 18 may at least partially have a radial overlap with the ball grooves 15, 16 or with the balls of the ball ramp mechanism 4.
[0031] The centering portion 19 extends axially from the radially outer end of the flange portion 18 and surrounds an outer guide surface 20 provided on the housing part 3. The centering portion 19 of the operating element 17 may in particular have an inner circumferential surface 22, which is guided axially movable along the outer circumferential surface of the housing part 3. This outer circumferential surface thus forms the guide surface 20 for the operating element 17 in the housing part. Overall, the operating element 17 is radially centered and axially movable relative to the housing part 3 via the axially extending centering portion. The centering portion 19 is in particular configured in a sleeve-like manner, i.e. formed by an annular closed wall, in which case other configurations are also possible, for example with several circumferentially distributed retaining elements. By means of the centering portion 19, the operating element 17 is advantageously centered radially outward and is therefore freely located radially inward relative to the housing part 3. The housing part 3 can thus be configured in an optimized manner with respect to loads.
[0032] The actuator assembly 2 further comprises a spring element 23, which is arranged axially between the housing part 3 and the operating element 17, so that a spring-elastic return force acting against the operating force of the ball ramp mechanism 4 is applied to the operating element 17. The spring element 23 is in this case designed as a wave spring and arranged coaxially with respect to the operating element. Of course, other spring shapes are also possible as return springs. The spring element 23 is accommodated or radially held in a receiving chamber 24 radially outside the flange part 18 and radially inside the centering part 19. In the axial direction, the spring element 23 is arranged between the operating element 17 and an end wall 25 of the housing part 3. The receiving chamber 24 has an axial extension that is greater than the minimum axial distance between the operating surface 26 of the operating element and the end wall 25 or end face of the housing. For this purpose, the operating element 17 has a bend 27 on the radial outside of the operating part, which is offset axially in the direction of the actuation disk 8 relative to the operating part. However, alternative configurations are also possible, in which the flange part 18 is formed without a step up to the centering part 19, but instead the housing part 3 has a recess or a step on the radial outside. Preferably, the receiving space 24 or the spring element 23 is arranged radially outside the operating surface 26 of the operating element 17 and functionally parallel to it.
[0033] The force transmission between the actuation disk 8 and the operating element 17 takes place in this embodiment via an optional thrust bearing 28, which is arranged coaxially with respect to the ball ramp mechanism 4, i.e. the thrust bearing 28 transmits axial forces and blocks relative rotational movements. The thrust bearing 28 is supported radially with respect to the operating element 17. For this purpose, the side of the operating element 17 facing the actuation disk 8 has an axially projecting, in particular annular, collar 29, which forms a recess 32 for the thrust bearing 28. An optional washer 30 is further provided between the operating element 17 and the thrust bearing 28. The washer 30 is likewise accommodated in the recess 32 formed by the annular collar.
[0034] Due to the configuration of the operating element 17 with the centering portion 19 or outer flange on the side facing the housing and / or the collar portion 29 or inner flange on the side facing the ramp mechanism 4, a high rigidity is achieved and the force-induced elastic deformation of the operating element is reduced. This results in improved response characteristics of the clutch which can be operated thereby and in a favourable support pattern all around during force transmission.
[0035] The operating element 17, the washer 30, the thrust bearing 28, the support disk 7 and the actuation disk 8 are arranged at a radial distance from the outer surface 36 of the sleeve-shaped part 5 of the housing part. The support disk 7 of the ball ramp mechanism is supported axially in the sleeve-shaped part 5 of the housing part 3. The housing part 3 has a bearing seat 33 on which a rotary bearing 34 rests. The rotary bearing 34 is in particular designed as a combined thrust / radial bearing. The bearing 34 is supported axially in the sleeve-shaped part 5 by a retaining ring 54, in which case other configurations are possible. The housing part 3 has a concave transition 35 between the flange-shaped part 6 and the bearing seat 33, which transition 35 extends axially from the lateral surface approximately to the support disk 7. The transition 35 has a free outer surface 36, i.e. no components are arranged or supported in the housing part 3 between the lateral surface and the rotary bearing 34. The minimum outer diameter D35 of the concave transition 35 may be smaller than the outer diameter D33 of the bearing seat 33 for the rotary bearing 34. Optionally, the concave transition 35 may have a curvature with a radius R corresponding to at least 0.5 times the minimum axial distance L between the working disc 8 and the flange 6 of the housing part 3, in particular to at least 0.6 times the minimum axial distance L. This configuration contributes to reducing the load on the housing part 3 in this section.
[0036] The actuator assembly 2 is particularly suitable for controlling a clutch for the powertrain of a motor vehicle, where the clutch can be arranged inside the housing part 3 and the actuator outside the housing part 3. The return of the actuator takes place via a spring element 23, which is functionally arranged outside the force transmission path formed between the actuating element 17 and the clutch, thereby achieving a particularly compact construction.
[0037] 2A to 2D, which will be described together below, show a differential assembly 37 according to the invention, which includes a friction multi-plate clutch 41 which is controllable by an actuator assembly 2 according to the invention.
[0038] A differential assembly 37, which can be driven by a drive shaft (not shown), is formed to transmit or distribute the introduced rotational motion to two side shafts. The differential assembly 37 includes a differential case 38, which can be rotatably supported by suitable bearings about a rotation axis A in a fixed differential housing (not shown). The differential case 38 is formed in two parts and includes a housing part 3 and a cover part 39, which are connected to each other at a connecting flange 40. A bevel ring gear (not shown) can be attached to the connecting flange 40. The bevel ring gear can be driven by the drive shaft of the vehicle.
[0039] In the differential case 38, differential gears 42 are rotatably supported on pins 43 arranged at right angles to the rotation axis A, which rotate together with the differential case 38. The differential gears 42 mesh with two side shaft gears 44, 44', which can be connected to the associated side shafts in a rotation-tight manner. For this purpose, the side shaft gears 44, 44' have shaft toothings 45, 45', into which connecting pins on the associated side shafts can be engaged in a rotation-tight manner. The differential gears 42 and the side shaft gears 44, 44' together form a differential gear set for torque transmission from the differential case 38 to the two side shafts. To receive the opening force, low-friction stopper disks 46, 46' are provided between the side shaft gears and the differential case 38, respectively; these stopper disks 46, 46' may also be called slide disks.
[0040] To control the locking action of the differential, a friction multi-plate clutch 41 is provided, which is arranged in the cover part 39, but is not limited thereto. It comprises a number of outer friction plates 47 connected in a form-locking manner or in a rotation-resistant manner but axially movable to the differential case 38, and a number of inner friction plates 48 connected in a rotation-resistant manner but axially movable to one of the side shaft gears 44'. The friction plate unit formed by the outer and inner friction plates can be axially pressurized via a pressure plate 49. The pressing force is controlled by the actuator assembly 2, which is shown in FIGS. 1A and 1B. In this regard, reference is made to the description of FIGS. 1A and 1B. The force is transmitted from the actuator to the pressure plate 49 via a number of force transmission elements 50 distributed over the entire circumference. These force transmission elements are in particular formed as pins which run axially through through-openings 52 in the housing part 3. One end of these pins is axially supported on the actuating element 17 and the other end on the pressure plate 49. The axial movement of the actuating disk 8 is transmitted to the pressure plate 49 via a thrust bearing, the actuating element and a force transmission element.
[0041] The pressure plate 49 presses the friction plate unit, which reduces the compensating movement between the side shaft gear 44' and the differential case 38 and thus also between the two side shaft gears 44, 44'. The torque that can be transmitted by the friction multi-plate clutch 41 can be variably adjusted as required by a corresponding control of the ball ramp mechanism 4. The clutch can be fully opened or closed or operated in any intermediate state, whereby when the clutch is fully opened the side shaft gears can rotate freely relative to each other ("open" differential), when the clutch is fully closed the compensating movement of the side shaft gears is fully locked ("closed" differential) and when the clutch is operated in any intermediate state the compensating movement between the side shaft gears is partially locked.
[0042] 2A to 2D, the friction multi-plate clutch 41 and the ball ramp mechanism 4 are arranged on opposite sides of the differential case 38 with respect to a plane E formed to include the differential gear axis B. The circumferentially distributed force transmission elements 50 extend axially through an outer peripheral wall 51 of the differential case 38 and are guided in this wall 51 so as to be axially movable.
[0043] The opposite ends of the differential case 38 comprise a first bearing seat 53 and a second bearing seat 53', on which corresponding bearings can be fitted. With the aid of these bearings, the differential case 38 can be rotatably supported in a differential housing (not shown). The minimum axial distance L53 between the two bearings or the two bearing seats can be smaller than the average tooth diameter of the drive flange. The actuating element 17 is arranged axially displaceably at the end of the outer peripheral wall of the differential case 38. A spring element and a thrust bearing are accommodated in this actuating element. Overall, the actuator assembly 2 according to the invention, together with the differential, allows a particularly compact construction size to be achieved.
[0044] Figure 3 shows a differential assembly 37 in a second embodiment with an actuator assembly 2 according to the invention, which in terms of construction and functioning essentially corresponds to the differential assembly shown in figure 2, to which reference is made in this respect, whereby identical or corresponding components are provided with the same reference numerals as in figure 2.
[0045] In contrast to the previous embodiment, in this embodiment the friction multi-plate clutch 41 and the ball ramp mechanism 4 are arranged on the same side in the differential case 38 with respect to a plane E formed containing the differential gear axis B. 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 too the centering part 19 of the actuating element 17 is arranged axially displaceable on the outer surface of the differential case 38. The differential case 38 in this embodiment comprises a pot-shaped housing part 39 in which the differential and the clutch are accommodated. The differential case 38 further comprises a housing part 3 which in this case is formed as a cover part. The housing part 3 has a connecting flange 56 which extends into a sleeve-shaped attachment 57 in the pot-shaped housing part 39 and is firmly connected to this, in particular, but not exclusively, by means of a welded seam 58. In terms of construction and function, the actuator assembly 2 corresponds to the one shown in figures 1 and 2. In this regard, reference is made to the description of figures 1 and 2.
[0046] In Fig. 4, a variant embodiment of the actuator assembly 2 according to the invention is shown, which corresponds fully to the embodiment shown in Fig. 1A-1B above. In this respect, reference is made to the description of Fig. 1A and 1B, whereby the same components or individual components which correspond to one another are provided with the same reference numerals as in the above figures.
[0047] The only difference is that the annular spring element 23 is not held in the embodiment shown in Fig. 4 against an inner circumference of the centering part 19 of the operating element 17, but radially against an outer circumference 11 of a shoulder 59 of the housing part 3. As in the previous embodiment, the spring element 23 is arranged in the receiving chamber 24, in particular with radial play.
[0048] Of course, the actuator assembly 2 according to the invention is not limited to the above-described applications but can be used in any other device in the power train of a motor vehicle, for example, the actuator assembly 2 according to the invention can also be used to operate a "twin star clutch assembly" in which a hang-on clutch or a differential is not required. [Explanation of symbols]
[0049] 2 Actuator Assembly 3 Housing part 4. Ball Ramp Mechanism 5 Sleeve-shaped part 6 Flange type part 7 Support Disc 8 Working Disc 9. Power Source 10 Dentition Segment 11 Peripheral surface 12 Pinion 13 End face (7) 14 End face (8) 15 Ball groove(7) 16 Ball groove(8) 17 Operational Elements 18 Flange 19 Centering section 20 Guide Surface 21 Outer circumference 22 Inner surface 23 Spring elements 24 Containment Room 25 End wall 26 Operation surface 27 Bend 28 Thrust bearing 29 Color 30 Washer 31 Differential transmission 32 Recess 33 Bearing seat 34 Rotary bearing 35 Transition 36 Exterior 37 Differential assembly 38 Differential case 39 Cover part / housing part 40 Connection flange 41 Friction multi-plate clutch 42 Differential gear 43 pin 44,44' Side shaft gear 45 Shaft Tooth Row 46 Stopper disk 47 Outer friction plate 48 Inner friction plate 49 Pressing plate 50 Force transmission elements 51 Outer wall 52 Through hole 53,53' bearing seat 54 Retainer ring 55 Anti-rotation means 56 Connection flange 57 Sleeve type attachment part 58 Joint 59 Shoulder A Rotation axis B Differential gear axis E plane L spacing R radius
Claims
1. An actuator assembly for operating a friction multi-plate clutch, particularly in a power train of a motor vehicle, comprising: a housing part (3) with a sleeve-shaped part (5) and a flange-shaped part (6); a ball ramp mechanism (4) comprising a support disk (7) axially supported in said housing part (3) and an actuation disk (8) which is axially movable, at least said support disk (7) being radially spaced from an outer surface (36) of said sleeve-shaped portion (5) of said housing part (3); an operating element (17) held axially movably in the flange-shaped part (6) of the housing part (3) coaxially with respect to the ball ramp mechanism (4), an annular gap being formed between an outer surface (36) of the sleeve-shaped part (5) and the operating element (17), the operating element (17) being axially supported at least indirectly on the working disk (8) on one side and having an operating surface (26) for pressing a friction multi-plate clutch (41) on the other side; a spring element (23) arranged radially outside the operating surface (26) of the operating element (17) and axially between the housing part (3) and the operating element (17) for applying a spring-elastic return force to the operating element (17) in a direction opposite to the operating force of the ball ramp mechanism (4); an actuator assembly including:
2. The flange-shaped portion (6) has a plurality of axial through-openings (52) around its entire circumference, the operating element (17) has a flange portion (18) having the operating surface (26) and having a radial overlap with the through opening (52), and a centering portion (19) extending axially from a radially outer end of the flange portion (18) and surrounding the housing part (3); The actuator assembly of claim 1 .
3. 3. An actuator assembly according to claim 1 or 2, characterized in that the centering part (19) has an inner peripheral surface (22) which is axially movable guided along an outer peripheral surface (21) of the housing part (3).
4. 4. The actuator assembly according to claim 1, wherein a chamber (24) for the spring element (23) is formed between the flange portion (18) of the operating element (17) and an end wall (25) of the housing part (3), the chamber (24) being arranged radially outside the through opening (52).
5. 5. The actuator assembly according to claim 1, wherein the spring element (23) is annular and is held radially on a circumferential surface of the operating element (17) or the housing (3).
6. 6. An actuator assembly according to claim 1, wherein the spring element (23) is formed in the form of a wave spring.
7. the support disk (7) can be driven to rotate by a drive source, the working disk (8) is held non-rotatable relative to the support disk (7) and axially movable, the support disk (7) and the working disk (8) have a plurality of circumferentially extending ball grooves (15, 16) on their mutually facing end faces (13, 14), one ball is guided in each of the ball grooves (15, 16), and the ball grooves (15, 16) are formed in such a way that a rotational motion introduced into the support disk (7) is converted into an axial motion of the working disk (8); a thrust bearing (28) is arranged axially between the actuation disk (8) and the operating element (17), the operating element (17) having an axially protruding collar (29) on which the thrust bearing (28) is radially supported; An actuator assembly according to any one of claims 1 to 6.
8. 8. An actuator assembly according to claim 7, characterized in that the centre points of the balls housed in the ball grooves (15, 16) have a radial overlap with the thrust bearing (28).
9. 9. An actuator assembly according to claim 1, characterized in that the sleeve-shaped portion (5) of the housing part (3) has a bearing seat (33) on which a rotary bearing (34) for the support disk (7) is mounted, and the housing part (3) has a concave transition (35) between the flange-shaped portion (6) and the bearing seat (33) of the sleeve-shaped portion (5), which transition (35) extends axially from a side surface of the flange-shaped portion (6) at least to the working disk (8).
10. 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 rolling bearing (34); and / or the concave transition portion (35) has a curvature with a radius (R) corresponding to at least 0.5 times the minimum axial distance (L) between the working disk (8) and the side wall of the housing part (3), in particular to at least 0.6 times the minimum axial distance (L); The actuator assembly of claim 9 .
11. A differential transmission assembly (37) comprising: a differential transmission (31) including a differential case (38) drivable to rotate 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 an angle to the rotation axis (A), a first side shaft gear (44) supported coaxially with the rotation axis (A) in the differential case (38) and in tooth-row engagement with the differential gears (42), and a second side shaft gear (44') located on the opposite side; a friction multi-plate clutch (41) including an outer friction plate (47) connected to the differential case (38) so as to be non-rotatable relative to the differential case and axially movable, and an inner friction plate (48) connected to one of the first side shaft gear (44) and the second side shaft gear (44') so as to be non-rotatable relative to the differential case and axially movable, wherein a friction plate unit formed of the outer friction plate (47) and the inner friction plate (48) can be pressed in the axial direction via a pressure plate (49); A differential transmission assembly (37) comprising: The axial adjustment device (2) according to any one of claims 1 to 10 is provided, the differential case (38) includes the housing part (3), and the axial adjustment device (2) is arranged in the housing part (3), a plurality of force transmission elements (50) are provided, distributed over the entire circumference, for transmitting the axial movement of the working disc (8) to the pressure plate (49) of the friction plate unit, the force transmission elements (50) extending axially through the through openings (52) in the housing part (3); A differential transmission assembly (37).
12. 12. A differential transmission assembly as claimed in claim 11, characterized in that the annular operating element (17) is arranged between the actuation disk (8) and the force transmission element (50), the force transmission element (50) abutting against an abutment surface provided on the operating element (17).
13. 13. A differential transmission assembly according to claim 11 or 12, characterized in that the friction multi-plate clutch (41) and the ball ramp mechanism (4) are arranged on opposite sides of the differential case (38) with respect to a plane (E) formed to include the differential gear axis (B), and the circumferentially distributed force transmission elements (50) extend axially through the differential case (38) and are axially guided therein.
14. The differential case (38) has a first bearing seat (53) and a second bearing seat (53') for being rotatably supported in a fixed differential housing by means of bearing elements, The differential case (38) has a connection flange (40) to which a drive gear for introducing torque can be firmly connected; 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; A differential transmission assembly according to any one of claims 11 to 13, characterized in that
15. 15. A differential transmission assembly according to claim 11, characterized in that the friction multi-plate clutch (41) and the ball ramp mechanism (4) are arranged on the same side of the differential case (38) with respect to a plane (E) formed to include the differential gear axis (B), and the circumferentially distributed force transmission elements (50) extend axially through a side wall of the differential case (38) and are axially guided therein.