Torque coupling device

Abstract

The invention relates to a torque coupling device (10) for a drive train of a vehicle, comprising a disconnect clutch (16) with a drive-side disconnect clutch input (20) rotatable about a pivot axis (18) and an output-side disconnect clutch output (22) connected to the disconnect clutch input (20) in a torque-transmitting manner depending on actuation, a locking clutch (24) of a differential lock (12) of a differential gear (14) with a locking clutch input (26) and a locking clutch output (28) connected to the locking clutch input (26) in a torque-transmitting manner depending on actuation, wherein the disconnect clutch (16) and the locking clutch (24) can be actuated depending on an actuation position (102, 112, 116) of an actuation element (62) of a common actuation device (74) movable for changing the actuation position (102, 112, 116).

Description

[0001] The invention relates to a torque coupling device according to the preamble of claim 1.

[0002] In DE 10 2021 134 205 A1 a differential lock in a differential gear is described, which has a housing connected on the drive side and rotatable about an axis of rotation and therein on the output side a first output component which can be connected to a first output shaft and a second output component which can be connected to a second output shaft.

[0003] The object of the present invention is to influence torque transmission in a vehicle's drivetrain in a flexible, space-saving, and cost-effective manner. The number of components of the torque coupling device is to be reduced. The torque coupling device itself is to be designed to be cost-effective and space-saving.

[0004] At least one of these tasks is solved by a torque coupling device with the features according to claim 1. This allows the torque coupling device to be designed cost-effectively and in a space-saving manner. The disconnecting clutch and the locking clutch can be actuated by the common actuating device.

[0005] The vehicle can be a motor vehicle or a truck.

[0006] The torque coupling device can comprise the locking clutch of the differential lock and the disconnect clutch as a single unit. The differential lock can be an electronic limited-slip differential (eLSD). The torque coupling device can include the differential gear associated with the differential lock and / or a torque vectoring module. The torque coupling device can be located on the differential gear. The differential gear can be an axle differential or a center differential, for example, of an all-wheel-drive system. The differential gear can be a bevel gear differential.

[0007] The torque coupling device can transmit drive power received from at least one drive element, for example an electric motor and / or combustion engine, in the direction of an output-side output component, for example to at least one vehicle axle and / or to at least one vehicle wheel of the vehicle.

[0008] The differential gear can have a differential housing on the drive side. The differential housing can be connected to at least one differential gear of the differential gear.

[0009] The disconnecting and / or locking coupling can be a friction coupling and / or a positive-locking coupling, in particular a jaw coupling. The disconnecting and / or locking coupling can be open without actuation force (normally-open coupling) or closed (normally-closed coupling).

[0010] Depending on the actuating position of the actuator, the disconnect clutch input can be connected to the disconnect clutch output in a torque-transmitting manner, in particular by friction and / or positive locking. The disconnect clutch output can be rotatably arranged about the axis of rotation. The disconnect clutch input can be arranged concentrically to the disconnect clutch output. The disconnect clutch can be arranged radially outside of the locking clutch and / or the actuator. The disconnect clutch can be effectively connected in series upstream of the locking clutch. Torque can only be transmitted via the locking clutch when the disconnect clutch is closed. The disconnect clutch can be effectively connected in series upstream of the differential gear. Torque can only be transmitted from the drive element to the differential gear when the disconnect clutch is closed.

[0011] Depending on the actuation position, the locking clutch input can be connected to the locking clutch output by transmitting torque, in particular by friction and / or positive locking. The locking clutch input can be rotationally fixed to the differential housing. The locking clutch input and the differential housing can be formed as a single unit. The locking clutch output can be rotationally fixed to at least one output gear that can be connected to an output shaft by means of a toothed connection. The locking clutch output and the output gear can be formed as a single unit. The locking clutch input and / or locking clutch output can be rotatably arranged about the axis of rotation. The locking clutch input can be arranged concentrically to the disconnect clutch input.

[0012] The locking clutch can be a friction clutch comprising at least one clutch plate for frictional connection between the locking clutch input and the locking clutch output. The at least one clutch plate and the actuating element can be arranged to overlap radially, at least partially.

[0013] The actuating device can include an actuator for moving the actuating element. The actuator can be a common actuator for both the disconnecting clutch and the locking clutch for moving the actuating element. This allows the actuator to actuate both the disconnecting clutch and the locking clutch.

[0014] The actuating element can transmit torque, which can be transmitted via the disconnect clutch, to the differential housing. The actuating element can be arranged in series between the disconnect clutch output and the differential housing, transmitting torque. The actuating element can be connected to the differential housing in a torque-transmitting manner. The actuating element can be connected to the locking clutch input or a component connected to it in a rotationally fixed and axially displaceable manner, in particular by positive locking. The actuating element can be axially displaceable relative to the disconnect clutch output or a component connected to it in a rotationally fixed manner. This allows the disconnect clutch to be pre-tensioned when actuated via the actuating element.Furthermore, the actuation of the disconnect clutch and the locking clutch can overlap during the movement of the actuating element to enable highly dynamic actuation processes. For example, the actuating element can be moved further even before the closing process of the disconnect clutch is fully completed, in order to shorten the time interval between the completion of the closing process of the disconnect clutch and the start of the actuation of the locking clutch, thus resulting in a certain degree of overlap between both processes, even though they are actually connected in series.

[0015] The actuating element can be effectively located outside of a torque transmission between the disconnect clutch output and the differential housing.

[0016] The actuating element can be movable against the restoring force of at least one spring element to change its actuating position. The spring element can be at least one disc spring or a coil spring. The spring element can be arranged on the actuating element.

[0017] The actuating element can be axially displaceable to change its actuating position. The actuating element can include at least one actuating bolt that is axially displaceable to change its actuating position. The actuating element can have several actuating bolts around its circumference. The actuating element, in particular at least one actuating bolt, can extend axially through the differential housing.

[0018] In a preferred embodiment of the invention, it is advantageous if the actuating element, acting as a common actuating element, is movable for actuating both the disconnecting clutch and the locking clutch by changing its actuating position. The actuating element can exert an actuating force on both the disconnecting clutch and the locking clutch. The actuating element can be movable in a constant direction, particularly an axial direction, for actuating both the disconnecting clutch and the locking clutch.

[0019] A preferred embodiment of the invention is advantageous in which, in a first actuation position, the disconnect clutch and the locking clutch are open. The restoring force of the spring element can act in the direction of the first actuation position. The first actuation position can refer to the axial direction, i.e., parallel to the axis of rotation.

[0020] In a specific embodiment of the invention, it is advantageous if, in a second actuation position, the disconnect clutch is closed and the locking clutch is open, and / or if, in a third actuation position, both the disconnect clutch and the locking clutch are closed. The disconnect clutch can already be closed when the locking clutch is closed, since the locking clutch of the differential lock only needs to be effective when torque is applied via the disconnect clutch. The second and third actuation positions can each refer to the axial direction, i.e., parallel to the axis of rotation.

[0021] The second and third actuation positions can be located in the same direction of the actuation movement, starting from the first actuation position.

[0022] In a preferred embodiment of the invention, it is advantageous if the actuating element is movable from the first actuating position, through the second actuating position, to the third actuating position. The first actuating position can be a first end position of the actuating element. The third actuating position can be a second end position of the actuating element, preferably axially opposite to the first end position.

[0023] In a specific embodiment of the invention, it is advantageous if the actuating device further comprises a rotary component that is rotatable to a limited extent relative to a connecting component and a ramp device with at least one rolling element that can roll along a ramp contour for converting a rotational movement of the rotary component into an axial movement of the actuating element. The rolling element can be arranged axially between the rotary component and the connecting component. The ramp contour can be formed on the rotary component and / or the connecting component. The connecting component can be axially movable depending on the rotational movement of the rotary component. The connecting component can be fixed in a non-rotating position relative to the axis of rotation. The actuating element can be rotatable about the axis of rotation relative to the connecting component. The actuating element can be coupled to the connecting component via at least one actuating bearing.The actuating force can be transferred from the connecting component to the actuating element via the actuating bearing.

[0024] In a preferred embodiment of the invention, it is advantageous if the ramp contour is designed with at least two stages, with at least one first rolling area spanned between a first rolling position and a second rolling position of the rolling element, and offset from the first rolling area, a second rolling area spanned between a third rolling position and a fourth rolling position of the rolling element. The two-stage subdivision can refer to a circumferential direction with respect to the axis of rotation. The second rolling area can be circumferentially offset from the first rolling area. The second rolling area can be directly adjacent to the first rolling area.

[0025] A preferred embodiment of the invention is advantageous in which the second actuation position is adjustable by the second rolling position of the rolling element, the third actuation position by the fourth rolling position of the rolling element, and the first actuation position by the first rolling position of the rolling element. The second and third rolling positions can be the same.

[0026] In a specific embodiment of the invention, it is advantageous if a rolling movement of the rolling element from the first rolling position to the fourth rolling position causes a movement of the actuating element from the first actuating position to the third actuating position. The second actuating position can be set at the second and / or third rolling position.

[0027] A preferred embodiment of the invention is advantageous in which the first rolling area has a first ramp angle of the ramp contour and the second rolling area has a second ramp angle of the ramp contour, wherein the first ramp angle is greater than the second ramp angle. This allows the disconnecting coupling to be closed more quickly than the locking coupling for the same rotational path of the rotating component relative to the connecting component. Furthermore, the disconnecting coupling can be held closed with low actuating force.

[0028] The first ramp angle can be a minimum, maximum, or average, and in particular, a constant, ramp angle. The second ramp angle can also be a minimum, maximum, or average, and in particular, a constant, ramp angle. For example, the first ramp angle could be 10° and the second ramp angle 1.5°.

[0029] Further advantages and advantageous embodiments of the invention will become apparent from the description of the figures and the illustrations. Character description

[0030] The invention is described in detail below with reference to the illustrations. These show, in detail: Fig. 1: A half-section of a torque coupling device in a special embodiment of the invention. Fig. 2: A cross-section of an actuating element of a torque coupling device in a further special embodiment of the invention. Fig. 3: A half-section of a torque coupling device in a further special embodiment of the invention. Fig. 4: A schematic representation of different actuation positions and associated rolling positions in a torque coupling device in a further special embodiment of the invention.

[0031] Fig. Figure 1 shows a half-section of a torque coupling device in a special embodiment of the invention. The torque coupling device 10 is arranged for torque transmission in a drive train of a vehicle and comprises a differential lock 12 and a differential gear 14, a disconnect clutch 16 with a drive-side disconnect clutch input 20 rotatable about an axis of rotation 18 and an output-side disconnect clutch output 22 rotatable about the axis of rotation 18 and connected to the disconnect clutch input 20 in a torque-transmitting manner depending on actuation, and a locking clutch 24 of the differential lock 12 with a drive-side locking clutch input 26 rotatable about the axis of rotation 18 and a locking clutch output 28 rotatable about the axis of rotation and connected to the locking clutch input 26 in a torque-transmitting manner depending on actuation.

[0032] The disconnect coupling input 20 is rotationally fixed to a drive gear 32, for example by welding. The drive gear 32 can transmit a drive-side torque from a drive element to the disconnect coupling input 20. The locking coupling input 26 is arranged radially inside the disconnect coupling input 20 and supported relative to it by a first bearing element 34 and a second bearing element 36.

[0033] A differential housing 30 is rotatably mounted about the axis of rotation 18 via a third bearing element 38 and a fourth bearing element 40. The third and fourth bearing elements 38, 40 can be fixed bearings. Optionally, an additional radial bearing 42 can be arranged next to the fourth bearing element 40. Alternatively, the third and fourth bearing elements 38, 40 can be configured as pre-tensioned bearings, and at least one axial bearing can optionally be arranged between the differential housing 30 and the disconnect clutch input 20.

[0034] The locking clutch input 26 and the differential housing 30 can be manufactured as a single unit. The locking clutch output 28 can be non-rotatably connected, in particular by welding, to a first output gear 44, which can be connected to an output shaft by means of a toothed connection. The first output gear 44 can be connected to a first output shaft in a torque-transmitting manner.

[0035] The differential gear 14 is designed as a bevel gear differential and comprises bevel gears 46, each of which is connected to the differential housing 30 via a differential pin 48 in a torque-transmitting manner. The bevel gears 46 are rotatable about their respective differential pins 48, and the differential pins 48 are fixedly connected to the differential housing 30. The bevel gears 46 mesh with the first output gear 44 and with a second output gear 50 arranged axially opposite the first output gear 44, which can be connected to a second output shaft in a torque-transmitting manner.

[0036] The first output gear 44 is rotatably mounted relative to the differential housing 30 via a first axial bearing 52 and the second output gear 50 is rotatably mounted relative to the differential housing 30 via a second axial bearing 54.

[0037] The locking clutch 24 comprises several clutch plates 56 for a frictional connection between the locking clutch input 26 and the locking clutch output 28. The clutch plates 56 include input-side clutch plates 58, which are rotationally fixed and axially displaceable to the locking clutch input 26, and output-side clutch plates 60, which are rotationally fixed and axially displaceable to the locking clutch output 28. When the locking clutch 24 is closed, the input-side clutch plates 58 and the output-side clutch plates 60 are frictionally connected to each other for torque transmission.

[0038] The disconnect clutch 16 can be actuated by an actuating element 62 with an actuating force. The actuating element 62 exerts an actuating force on an actuating plate 64 of the clutch plates 56. A maximum clearance between the clutch plates 56 when the locking clutch 24 is open is limited by an axial locking element 66 mounted on the differential housing 30, against which the actuating plate 64 abuts axially when the locking clutch 24 is open. The maximum clearance can also be adjusted by other suitable means.

[0039] The disconnect coupling 16 is designed as a positive-lock coupling, in particular as a jaw coupling. The disconnect coupling input 20 comprises an axial face toothing 68, which, when the disconnect coupling 16 is closed, is positively connected to a further axial face toothing 70 at the disconnect coupling output 22, which is axially opposite the axial face toothing 68.

[0040] The disconnect coupling 16 is arranged radially outside of the locking coupling 24 and the actuating element 62, and the locking coupling 24 and the actuating element 62 are arranged at least partially radially overlapping each other.

[0041] The disconnect clutch 16 and the locking clutch 24 can be actuated depending on the actuating position of the actuating element 62. The actuating element 62 is axially movable to change its actuating position. The actuating element 62 comprises several circumferentially offset actuating bolts 72 that extend through the differential housing 30. The actuating element 62, as a common actuating element 62 of a common actuating device 74, can be moved to actuate both the disconnect clutch 16 and the locking clutch 24 by changing its actuating position.

[0042] The actuating device 74 further comprises a rotary component 76 which is rotatable to a limited extent relative to a connecting component 78 and a ramp device 80 with at least one rolling element 82, for example a ball, which rolls along a ramp contour, for converting a rotational movement of the rotary component 76 into an axial movement of the connecting component 78 and, via an actuating bearing 84, into an axial movement as an actuating movement of the actuating element 62. The rolling element 82 is arranged axially between the rotary component 76 and the connecting component 78. The ramp contour can be formed on the rotary component 76 and / or the connecting component 78.

[0043] The actuating element 62 is axially displaceable via the actuating bearing 84, the connecting component 78, the ramp device 80, and the rotary component 76 to change the actuating position. The rotary component 76 is connected to an actuator of the actuating device 74 (not shown here) as a common actuator for actuating the disconnecting clutch 16 and the locking clutch 24.

[0044] The actuating element 62 transmits a torque, which can be transmitted via the disconnect clutch 16, to the differential housing 30 and thus also to the locking clutch input 26. The actuating element 62 is arranged in series between the disconnect clutch output 22 and the differential housing 30 in a torque-transmitting manner and is connected to the differential housing 30 via a toothed connection 86 in a torque-transmitting and axially displaceable manner.

[0045] The actuating element 62 comprises a pressure ring 88, which is axially spring-elastically mounted relative to the disconnecting clutch output 22 and is torque-transmittingly connected to the disconnecting clutch output 22. The axial elastic connection between the pressure ring 88 and the disconnecting clutch output 22 allows further actuating movement of the actuating element 62 to actuate the locking clutch 24, even when the disconnecting clutch 16 is already closed. The pressure ring 88 bears against the actuating bolt 72.

[0046] Fig. Figure 2 shows a cross-section of an actuating element of a torque coupling device in a further specific embodiment of the invention. The pressure ring 88 rests against the actuating bolt 72. The actuating movement, as an axial movement, occurs against the restoring force of at least one spring element 90. Several spring elements can be arranged, one spring element 90 on each actuating bolt 72. The spring element 90 is supported against the differential housing 30 and causes the actuating element 62 to return to an actuating position in which the disconnect clutch and the locking clutch are open.

[0047] Fig. Figure 3 shows a half-section of a torque coupling device in a further special embodiment of the invention. The torque coupling device 10 compensates for the Fig. 1 except for the following differences. The disconnect clutch output 22 is connected to the differential housing 30 via a toothed connection 92 in a torque-transmitting manner. The disconnect clutch output 22 is mounted axially displaceable on the differential housing 30.

[0048] The actuating element 62 further comprises an actuating piston 94, which is arranged between the pressure ring 88 and the disconnecting clutch output 22 for transmitting the actuating force. The disconnecting clutch output 22 has a detent device 96 with at least one detent element 98, in particular a ball. When the disconnecting clutch 16 is closed, the detent element 98 is arranged to engage in a radial recess 100 in the differential housing 30 and can thereby keep the disconnecting clutch 16 closed, reducing the actuating energy required by the actuating element 62.

[0049] Fig. Figure 4 shows a schematic representation of different actuation positions and associated rolling positions in a torque coupling device in a further specific embodiment of the invention. In a first actuation position 102 of the actuating element 62 in Fig. 4 a), in which the disconnecting clutch and the locking clutch are open, a first axial distance 104 exists between the rotating component 76 and the connecting component 78. A first limit actuation position 106, in which the disconnecting clutch is closed via the pressure ring 88, and a second limit actuation position 108, in which the locking clutch 24 is closed via the actuating bolt 72, are not yet reached axially in the first actuation position 102.

[0050] As in Fig. As shown in Figure 4 b), during an axial movement 110 of the actuating element 62 to change its actuating position, starting from the first actuating position 102, the actuating element 62 can assume a second actuating position 112, in which the first limit actuating position 106 for closing the disconnecting clutch by the pressure ring 88 is axially reached and the disconnecting clutch is closed. The second limit actuating position 108 for closing the locking clutch by the actuating piston 72 has not yet been axially reached. The locking clutch is therefore still open. In the second actuating position 112, there is a second axial distance 114 between the rotating component 76 and the connecting component 78, which is greater than the first axial distance.

[0051] With further axial movement 110 of the actuating element 62 starting from the second actuating position 112, accordingly Fig. 4 c) A third actuation position 116 is assumed, in which a third axial distance 117, larger than the second axial distance 114, exists between the rotating component 76 and the connecting component 78, and in which the second limit actuation position 108 of the locking clutch is also axially reached by the actuating bolt 72 and the locking clutch is closed, while the disconnecting clutch remains closed by the pressure ring 88. The first limit actuation position 106 of the disconnecting clutch is thereby axially exceeded by the pressure ring 88, which can be compensated for by an axially elastic connection between the actuating element 62 and the disconnecting clutch output.

[0052] The serial actuation of the disconnecting clutch and locking clutch is thus effected by the common actuating element 62. The disconnecting clutch can be actuated via the pressure ring 88 and the locking clutch via the actuating bolt 72.

[0053] How with regard to Fig. As explained in section 4 a), the ramp contour 118 on the rotating component 76 and on the connecting component 78 is designed in two stages, with at least one first rolling area 124 spanned between a first rolling position 120 and a second rolling position 122 of the rolling element 82, and offset from the first rolling area 124, a second rolling area 130 spanned between a third rolling position 126 and a fourth rolling position 128 of the rolling element 82. The second and third rolling positions 122 and 126 are identical. The first rolling area 124 has a first ramp angle 132 of the ramp contour 118, and the second rolling area 130 has a second ramp angle 134 of the ramp contour 118, the first ramp angle 132 being greater than the second ramp angle 134. The first ramp angle 132 can be, for example, 10° and the second ramp angle 134 can be 1.5°.

[0054] The first actuation position 102 is defined by the first rolling position 120 of the rolling element 82, the second actuation position 112 is defined by the second rolling position 122 of the rolling element 82, as shown in Fig. 4 b) shown and the third actuation position 116 is as in Fig. 4 c) shown by the fourth rolling position 128 of the rolling element 82 set.

[0055] The change of the rolling positions 120, 122, 128 is effected by a rolling movement 136 of the rolling element 82, which in turn is caused by a rotational movement 138 of the rotating component 76 relative to the connecting component 78. The rotational movement 138 of the rotating component 76 causes the rolling movement 136 of the rolling element 82 from the first rolling position 120 to the fourth rolling position 128 to actuate the actuating element 62 as an axial movement 110 from the first actuating position 102 to the fourth rolling position 128. Fig. 4 a) to the third actuation position 116 in Fig. 4 c). Reference symbol list 10 Torque coupling device 12 Differential lock 14 Differential gears 16 Disconnect coupling 18 Rotation axis 20 Disconnect coupling input 22 Disconnect coupling output 24 Locking coupling 26 Locking coupling input 28 Locking coupling output 30 Differential housings 32 Drive gear 34 first bearing element 36 second bearing element 38 third bearing element 40 fourth bearing element 42 radial bearings 44 first output gear 46 bevel gear 48 differential bolts 50 second output gear 52 first axial bearing 54 second axial bearing 56 Clutch plate 58 input-side clutch plate 60 output-side clutch plate 62 Actuating element 64 Actuating blade 66 Safety element 68 axial face teeth 70 additional axial face teeth 72 actuating bolts 74 Actuating device 76 Turned component 78 Connecting component 80 Ramp device 82 Rolling element 84 actuating bearings 86 gear teeth 88 Pressure ring 90 spring element 92 gear teeth 94 actuating pistons 96 Locking device 98 locking element 100 In-depth study 102 first actuation position 104 first axial distance 106 first limit actuation position 108 second limit actuation position 110 axial movement 112 second actuation position 114 second axial distance 116 third actuation position 117 third axial distance 118 Ramp contour 12 Differential lock 120 first rolling position 122 second rolling position 124 first roll-off area 126 third rolling position 128 fourth rolling position 130 second roll-off area 132 first ramp angle 134 second ramp angle 136 Rolling motion 138 Rotational movement QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2021 134 205 A1

[0002]

Claims

Torque coupling device (10) for a drive train of a vehicle, comprising a disconnecting clutch (16) with a drive-side disconnecting clutch input (20) rotatable about a pivot axis (18) and an output-side disconnecting clutch output (22) connected to the disconnecting clutch input (20) in a torque-transmitting manner depending on actuation, a locking clutch (24) of a differential lock (12) of a differential gear (14) with a locking clutch input (26) and a locking clutch output (28) connected to the locking clutch input (26) in a torque-transmitting manner depending on actuation, characterized in that the disconnecting clutch (16) and the locking clutch (24) can be actuated depending on an actuation position (102, 112, 116) of an actuation element (62) of a common actuation device (74) movable for changing the actuation position (102, 112, 116). Torque coupling device (10) according to claim 1, characterized in that the actuating element (62) is movable as a common actuating element (62) for actuating both the disconnecting clutch (16) and the locking clutch (24) by changing the actuating position (102, 112, 116). Torque coupling device (10) according to claim 1 or 2, characterized in that in a first actuation position (102) the disconnecting clutch (16) and the locking clutch (24) are open. Torque coupling device (10) according to claim 3, characterized in that in a second actuation position (112) the disconnecting clutch (16) is closed and the locking clutch (24) is open and / or in a third actuation position (116) the disconnecting clutch (16) and the locking clutch (24) are closed. Torque coupling device (10) according to claims 3 and 4, characterized in that the actuating element (62) is movable from the first actuating position (102) via the second actuating position (112) to the third actuating position (116). Torque coupling device (10) according to one of the preceding claims, characterized in that the actuating device (74) further comprises a rotary component (76) which is rotatable to a limited extent relative to a connecting component (78) and a ramp device (80) with at least one rolling element (82) which can be rolled along a ramp contour (118) for converting a rotational movement (138) of the rotary component (76) into an axial movement (110) of the actuating element (62). Torque coupling device (10) according to claim 6, characterized in that the ramp contour (118) is designed in at least two stages, with at least one first rolling area (124) stretched between a first rolling position (120) and a second rolling position (122) of the rolling element (82) and offset to the first rolling area (124) a second rolling area (130) stretched between a third rolling position (126) and a fourth rolling position (128) of the rolling element (82). Torque coupling device (10) according to claim 7, characterized in that the second actuation position (112) is adjustable by the second rolling position (122) of the rolling element (82), the third actuation position (116) by the fourth rolling position (128) of the rolling element (82) and the first actuation position (102) by the first rolling position (120) of the rolling element (82). Torque coupling device (10) according to claim 7 or 8, characterized in that a rolling movement (136) of the rolling element (82) from the first rolling position (120) to the fourth rolling position (128) causes a movement of the actuating element (62) from the first actuating position (102) to the third actuating position (116). Torque coupling device (10) according to one of claims 7 to 9, characterized in that the first rolling area (124) has a first ramp angle (132) of the ramp contour (118) and the second rolling area (130) has a second ramp angle (134) of the ramp contour (118), wherein the first ramp angle (132) is greater than the second ramp angle (134).

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