Actuating device with a spring device and clutch
The actuating device addresses inefficiencies in rotational movement by using a ramp and spring system to translate and assist rotational movement, reducing loads and optimizing space and cost in vehicle drivetrains.
Patent Information
- Authority / Receiving Office
- DE · DE
- Patent Type
- Applications
- Current Assignee / Owner
- SCHAEFFLER TECHNOLOGIES AG & CO KG
- Filing Date
- 2024-11-14
- Publication Date
- 2026-05-21
AI Technical Summary
Existing actuating devices in vehicles are not designed to efficiently manage rotational movement, reduce operational loads, and minimize space and cost while maintaining quiet operation.
An actuating device with a ramp device and spring device that translates rotational movement into axial movement, utilizing rolling elements and a helical spring to assist and brake rotational movement, reducing loads and optimizing space and cost.
The device effectively reduces torque requirements, supports rotational movement, and minimizes operational loads while being compact and cost-effective, enhancing vehicle drivetrain performance.
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Abstract
Description
[0001] The invention relates to an actuating device according to the preamble of claim 1. The invention further relates to a clutch.
[0002] German patent application DE 10 2014 221 197 A1 describes a clutch actuation device with a ramp device comprising a first ramp on a ramp ring and a second ramp on a pressure plate, with a ball positioned between the first and second ramps. A relative rotation between the first and second ramps causes an axial movement of the pressure plate relative to the ramp ring.
[0003] The object of the present invention is to influence the rotational movement of the actuating device in a torque-effective manner. Furthermore, the loads acting on the actuating device during operation are to be reduced. The actuating device is to be designed to be space-saving and cost-effective. The actuating device is also to be able to operate more quietly.
[0004] At least one of these tasks is solved by an actuating device with the features according to claim 1. This allows the actuating device to be designed in a space-saving and cost-effective manner, and reduces the loads on the components during operation. The torque required to rotate the first actuating element can be reduced, and the return movement of the first actuating element can be supported and slowed.
[0005] The actuating device can be arranged in a vehicle, in particular in a drive train of the vehicle.
[0006] The ramp contour can be formed on an intermediate component connected to the first or second actuating element, or directly on the first or second actuating element. The ramp contour can be formed on an axial side surface of the first or second actuating element. The ramp contour can extend over a constant mean diameter on the first or second actuating element.
[0007] The rolling element can be a ball, a conical roller, or a cylindrical roller.
[0008] Depending on the rotational position of the first actuating element, the second actuating element can transmit an axial force via the ramp device. The rotational position can be defined as the angle of rotation of the first actuating element relative to the second actuating element with respect to the axis of rotation. The first actuating element can be rotated relative to the second actuating element about the axis of rotation, thereby changing its rotational position.
[0009] The spring device can consist of only a single spring element. The spring force assisting the rotational movement and the spring force acting as a brake can each be produced, in particular exclusively, by compression of the spring element.
[0010] The first actuating element can be rotated relative to the second actuating element by an actuator.
[0011] In a preferred embodiment of the invention, it is advantageous if the spring device is pivotably connected to the first actuating element at a first connection position and to the second actuating element at a second connection position. The first connection position can be formed by a first pivot joint. The second connection position can be formed by a second pivot joint. The first connection position can be arranged radially inside or radially outside of the second connection position.
[0012] A preferred embodiment of the invention is advantageous in which, at least in the first, second, and / or third rotational position, the first connection position is offset radially and / or circumferentially relative to the second connection position. The immediate distance between the first and second connection positions can depend on the respective rotational position. A radial distance between the first and second connection positions can be constant regardless of the rotational position. In the first, second, and / or third rotational position, the direction of the immediate distance can be angled relative to the radial direction.
[0013] A preferred embodiment of the invention is advantageous in which, at the first rotational position, the first connection position is circumferentially offset relative to the second connection position in the second direction of rotation, and / or at the second rotational position, the first connection position is circumferentially offset relative to the second connection position in the first direction of rotation. In a further rotational position located between the first and second rotational positions, the first and second connection positions can be aligned radially with each other, meaning they have the same circumferential position.
[0014] In a particular embodiment of the invention, it is advantageous if the spring element is a helical spring arranged between a first spring contact area, which is displaceable along a spring axis of the spring element relative to the first attachment position, and a second spring contact area, which is also displaceable along a spring axis of the spring element relative to the second attachment position. The spring axis can be oriented at an angle relative to the radial direction in the first, second, and / or third rotational position.
[0015] In a specific embodiment of the invention, it is advantageous if the spring device, when the first and second attachment positions are directly separated, counteracts further approximation of the first and second attachment positions by the spring force when the first and second attachment positions are directly separated, and counteracts further displacement of the first and second attachment positions by the spring force when the second attachment position is directly separated. The first and second direct distances can be the same or different. The second direct distance can be greater than the first direct distance.
[0016] In an advantageous embodiment of the invention, the first rotational position is located between the second and third rotational positions. With respect to a radial direction originating from the second attachment position, the first and third rotational positions can be located in one circumferential direction, and the second rotational position in the opposite circumferential direction.
[0017] In a particular embodiment of the invention, it is advantageous if the spring force, in the first rotational position, comprises a tangential component acting in the direction of the second rotation, and in the second rotational position, a tangential component acting in the direction of the first rotation. In a further rotational position lying between the first and second rotational positions, the spring force can be oriented radially and have no tangential component.
[0018] Furthermore, within the scope of the invention, a clutch actuation device with the features of claim 9 is proposed to solve at least one of the aforementioned problems. The actuation force can correspond to the axial force or be dependent on it by means of a transmission.
[0019] The clutch actuation device can be located in the drivetrain of a vehicle. The vehicle can be a motor vehicle, a two-wheeled vehicle, or a truck.
[0020] The actuator can be electric, hydraulic, and / or pneumatic. The actuator can provide the actuating torque on a rotatable shaft. At least one transmission stage can be effective between the actuator and the first actuating element. The transmission stage can comprise at least one single-stage or multi-stage planetary gear set, a multi-stage spur gear set, a crown gear set, and / or a worm gear. The actuating torque exerted on the first actuating element by the actuator can therefore be greater than the actuating torque of the actuator itself.
[0021] Furthermore, within the scope of the invention, a clutch with the features of claim 10 is proposed to solve at least one of the aforementioned problems. The actuation of the clutch can depend on a rotational position of the first actuating element relative to the second actuating element.
[0022] The second actuating element can actuate the friction area indirectly, that is, via at least one further actuating component, in particular a pressure plate. The second actuating element can actuate the friction area directly, that is, by contacting at least one friction lamella of the friction area.
[0023] The clutch can be located in the drivetrain of a vehicle. The vehicle can be a motor vehicle, a two-wheeled vehicle, or a truck.
[0024] The clutch can be actuated in either an open or closed position, depending on the axial force of the actuating device when an actuating force is applied. The clutch can be a normally-open clutch, which, when an actuating force is applied, can be actuated into a closed position where torque can be transmitted across the friction area. Alternatively, the clutch can be a normally-closed clutch, which, when an actuating force is applied, can be actuated into an open position where torque transmission across the friction area is interrupted.
[0025] The clutch can be arranged in a limited-slip differential. The clutch can be a starting clutch or a dual clutch. Compared to the actuator's required actuation torque, the clutch can transmit a torque that is at least one order of magnitude, preferably at least three orders of magnitude, higher. For example, the actuator's actuation torque can be 0.5 Nm and the torque transmittable via the clutch can be 2000 Nm.
[0026] Further advantages and advantageous embodiments of the invention will become apparent from the description of the figures and the illustrations. Character description
[0027] The invention is described in detail below with reference to the illustrations. These show, in detail: Fig. 1: An actuating device in a special embodiment of the invention. Fig. 2: An actuating device in a further special embodiment of the invention. Fig. 3: A spring device for different rotational positions of an actuating device in a further special embodiment of the invention. Fig. 4: The spring device made of Fig. 3 with braking spring force. Fig. 5: A torque curve through the spring force of a spring device of an actuating device in a further special embodiment of the invention.
[0028] Fig. Figure 1 shows an actuating device in a specific embodiment of the invention. The actuating device 10 is arranged as a clutch actuating device 11 for providing an axial force 12, particularly in a drive train of a vehicle, and comprises a first actuating element 16 rotatable about a pivot axis 14 by an actuator and a second actuating element 18, in particular a friction area, for example of a clutch, which can be subjected to an actuating force depending on the axial force 12. The first and second actuating elements 16, 18 are arranged opposite each other in the axial direction 20 and are preferably disc-shaped.
[0029] Furthermore, a ramp device 22 with several rolling elements 26, each capable of rolling along ramp contours 24, is arranged between the first and second actuating elements 16, 18 to translate a relative rotary movement into an axial movement of the first actuating element 16 relative to the second actuating element 18. The rolling element 26 is preferably a ball. A total of five such ramp contours 24 and rolling elements 26 are arranged circumferentially offset. The ramp contours 24 comprise a first ramp contour 28 on the first actuating element 16 and a second ramp contour 30 on the second actuating element 18.
[0030] The rolling elements 26 are secured to a locking element 32. The locking element 32 includes a recess 34 for each rolling element 26, into which the rolling element 26 is inserted. This ensures that each rolling element 26 has the same relative position to the respective ramp contour 24 and thus the same contact angle. The locking element 32 is arranged axially between the first and second actuating elements 16, 18.
[0031] At least one ramp contour 24 for each rolling element 26 has a ramp that rises in the axial direction 20 with increasing circumferential position, by which, during a rotational movement of the first actuating element 16 relative to the second actuating element 18, the first and second actuating elements 16, 18 are moved axially away from each other. Thus, a rotational movement of the first actuating element 16 relative to the second actuating element 18 can cause an axial movement of the second actuating element 18 and the axial force 12 on the second actuating element 18.
[0032] Fig. Figure 2 shows an actuating device in a further specific embodiment of the invention. The actuating device 10 comprises the rotatable first actuating element 16 and the preferably rotationally fixed second actuating element 18. The first actuating element 16 can be rotated about the axis of rotation 14 by changing a rotational position φ relative to the second actuating element 18.
[0033] Furthermore, a spring device 36 with at least one spring element 38 designed as a helical spring is effectively arranged between the first and second actuating elements 16, 18. The spring device 36 assists the relative rotational movement of the first actuating element 16 in a second direction of rotation 42 at at least one first rotational position φ1 and the relative rotational movement of the first actuating element 16 in a first direction of rotation 40 at at least one second rotational position φ2, each with a spring force 44. The spring device 36 is pivotably connected to the first actuating element 16 at a first connection position 46 and to the second actuating element 18 at a second connection position 48.
[0034] In the first and second rotational positions φ1, φ2 of the first actuating element 16, the first and second connection positions 46, 48 are radially and circumferentially offset from each other. In the first rotational position φ1, the first connection position 46 is circumferentially offset from the second connection position 48 in the second direction of rotation 42, and in the second rotational position φ2, the first connection position 46 is circumferentially offset from the second connection position 48 in the first direction of rotation 40.
[0035] The spring force 44 comprises, at the first rotational position φ1, a tangential component 50 acting in the direction of the second rotational direction 42, and at the second rotational position φ2, a tangential component 52 acting in the direction of the first rotational direction 40. The spring force 44 is angled relative to the radial direction at the first and second rotational positions φ1, φ2, and can therefore exhibit the tangential component 50, 52 that supports the respective rotational movement.
[0036] In a further rotation position between the first and second rotation positions φ1, φ2 (not shown here), the spring element 38 is radially oriented, meaning that a spring axis 54 of the helical spring runs in the radial direction. The spring force 44 is also radially oriented and has no tangential component.
[0037] If, for example, the first actuating element 16 is rotated from the first rotational position φ1 in the first direction of rotation 40, then the tangential component 50 of the spring force 44 runs harmonically over the rotational positions φ, meaning that during the rotational movement in the first direction of rotation 40, the tangential component 50 acts up to the next rotational position φ in the second direction of rotation 42, until it disappears at the next rotational position and during further rotational movement from the next rotational position to the second rotational position φ2, the opposite occurs, namely in the direction of the first direction of rotation 40.
[0038] This reversal of the direction of force of the spring force 44 acting on the first actuating element 16, caused by this tilting spring function, has the advantage of causing the return of the first actuating element 16 rotated by the actuator in rotational positions φ, for example between the first rotational position φ1 and the next rotational position φ, and of increasing the rotational movement in the first direction of rotation 40 in rotational positions φ between the next rotational position φ and, for example, the second rotational position φ2.
[0039] Fig. Figure 3 shows a spring device in different rotational positions of an actuating device in a further special embodiment of the invention. Fig. 3 a) The spring device 36 is shown in a neutral rotational position φ0, in which the spring element 38 is force-free and no spring force is exerted. The spring element 38 is designed as a helical spring. The spring device 36 comprises a first connection element 57 having the first connection position 46 as a first pivot joint 56, which is connected via the first connection position 46 to the first actuating element (not shown here). Furthermore, the spring device 36 comprises a second connection element 59 having the second connection position 48 as a second pivot joint 58, which is connected via the second connection position 48 to the second actuating element (not shown here).
[0040] Furthermore, the spring device 36 comprises a first sleeve 62, which forms a radially outer first spring contact area 64 for the coil spring, and a second sleeve 66 attached to the second connecting element 59. The first sleeve 62 is displaceable relative to the second sleeve 66 along a displacement direction 68 parallel to the spring axis 54.
[0041] An inner sleeve 70, located within the first and second sleeves 62, 66, forms a radially inner second spring contact area 72 for the coil spring, opposite the first spring contact area 64 with respect to the spring axis 54. The inner sleeve 70 is displaceable relative to the first sleeve 62, the second sleeve 66, the first connecting element 57, and the second connecting element 59 along the displacement direction 68 and without collision to the first connecting position 46. The inner sleeve 70 is guided between a pin 74 of the first connecting element 57 and a pin 76 of the second connecting element 59.
[0042] The first and second sleeves 62, 66 have stop elements 78 that limit the maximum displacement of the first sleeve 62 relative to the second sleeve 66. The inner sleeve 70 has a drive element 80 with which, when the first connecting element 57 is displaced away from the second connecting element 59, the inner sleeve 70 is displaced along with it, thus also displacing the inner sleeve 70 away from the second connecting element 59. In the opposite direction of displacement of the first connecting element 57 towards the second connecting element 59, the drive element 80 is decoupled from the first connecting element 57, and the inner sleeve 70 remains stationary relative to the second connecting element 59.
[0043] This allows the spring device 36 to counteract a further mutual approach of the first to the second connection position 46, 48 with the spring force at an immediate distance 82 of the first connection position 46 from the second connection position 48 below a first immediate distance 84, which is present here at the neutral rotation position φ0, and above a second immediate distance, which is a distance 86 of the stop means 78 of the first and second sleeve 62, 66 from each other above the first immediate distance 82, to counteract a further mutual movement away from the first from the second connection position 46, 48.
[0044] In Fig. 3 b) The first actuating element is rotated further in the first direction of rotation 40 relative to the neutral rotational position φ0 and has a first rotational position φ1 relative to the second actuating element. The radial distance 87 between the first and second connection positions 46, 48 remains constant regardless of the rotational position, while the immediate distance 82 is smaller than the first immediate distance from Fig. 3 a). The first connection position 46 is thus closer to the second connection position 48 with respect to the immediate distance 82. The spring element 38 exerts a spring force 44 on the first connection element 57, which, with a tangential component, supports the rotational movement in the second direction of rotation 42.
[0045] After the first actuating element has been rotated a further 40 degrees in the first direction of rotation, it can be used as described in Fig. 3 c) shown to have a second rotation position φ2 in which the spring element 38 exerts a spring force 44 on the first connecting element 57, which with a tangential component supports the rotational movement in the first direction of rotation 40.
[0046] Fig. 4 shows the spring device Fig. 3. Under braking spring force. The spring device 36 acts upon at least the first actuating element, which is moved by a rotary motion in the second direction of rotation 42 and is thereby assisted by the spring force of the spring device 36 and continues to move in the second direction of rotation 42, with a counteracting braking spring force 90 at a third rotary position φ3 in order to brake the rotary motion of the first actuating element in the second direction of rotation 42. The inner sleeve 70 is displaced relative to the second connecting element 59 and the inner sleeve 70 is connected to the first connecting element 57 via the drive element 80.
[0047] This allows the spring device 36 to counteract further mutual displacement above a second immediate distance between the first attachment position 46 and the second attachment position 48, thus preventing further separation of the first and second attachment elements 57, 59.
[0048] Fig. Figure 5 shows a torque curve due to the spring force of a spring device of an actuating device in a further specific embodiment of the invention. The spring force of the spring device, with its tangential component, causes a torque M on the first actuating element, which is represented here by the rotational position φ.
[0049] A rotational position φ of 0° corresponds, for example, to a contact point of the actuating device, which is designed, in particular, as a clutch actuating device. At a rotational position φ of -8° up to a rotational position φ of approximately -4° of the first actuating element relative to the second actuating element, the torque M is zero, meaning the spring force of the spring device is zero. This range lies, in particular, between the rotational positions where the immediate distance between the first and second connection positions is the first immediate distance and the second immediate distance.
[0050] From a rotational position φ of -4°, the harmonious progression of the torque M generated by the spring device with its tilting spring function is evident as the rotational position φ increases in the first direction of rotation 40°, i.e., when the clutch is engaged, up to a rotational position φ of 10°, at which point the spring device exerts a radially oriented spring force, resulting in zero torque. From this point onward, the torque M provided by the spring device assists the rotational movement in the first direction of rotation 40°, as indicated by negative torque values.
[0051] During the rotational movement in the second direction of rotation 42 and from the rotational position φ of -8° the spring force of the spring device acts as a braking force that increases linearly, recognizable by the negative torque M. Reference symbol list 10 Actuating device 11 Clutch actuation device 12 Axial force 14 axis of rotation 16 first actuating element 18 second actuating element 20 axial direction 22 Ramp device 24 Ramp contour 26 Rolling element 28 first ramp contour 30 second ramp contour 32 locking element 34 recess 36 Spring device 38 Spring element 40 first direction of rotation 42 second direction of rotation 44 spring force 46 first connection position 48 second connection position 50 tangential component 52 tangential component 54 Spring axle 56 first pivot joint 57 first connecting element 58 second pivot joint 59 second connecting element 62 first sleeve 64 first spring mounting area 66 second sleeve 68 Direction of movement 70 Inner sleeve 72 second spring mounting area 74 cones 76 cones 78 Lifting equipment 80 Drive element 82 immediate distance 84 first immediate distance 86 distance 87 radial spacing 88 third turning position 90 braking spring force φ Rotation position φ0 neutral rotation position φ1 first rotation position φ2 second rotation position φ3 third rotation position M torque 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 2014 221 197 A1
[0002]
Claims
Actuating device (10) comprising a first actuating element (16) rotatable about a rotational axis (14), a second actuating element (18), a ramp device (22) effective between the first and second actuating elements (16, 18) with at least one rolling element (26) rollable on a ramp contour (24) for translating a relative rotational movement that can change the rotational position (φ) of the first actuating element (16) relative to the second actuating element (18) into a relative axial movement of the first actuating element (16) relative to the second actuating element (18), characterized in that a spring device (36) is effectively arranged between the first and second actuating elements (16, 18) and has at least one spring element (38),which, in at least one first rotational position (φ1), supports the relative rotational movement of the first actuating element (16) in a second direction of rotation (42) and, in at least one second rotational position (φ2), supports the relative rotational movement of the first actuating element (16) in a first direction of rotation (40), each with a spring force (44), and which, in at least one third rotational position (φ3), provides a braking spring force (90) that counteracts the rotational movement in a second direction of rotation (42) opposite to the first direction of rotation (40). Actuating device (10) according to claim 1, characterized in that the spring device (36) is pivotably connected at a first attachment position (46) to the first actuating element (16) and at a second attachment position (48) to the second actuating element (18). Actuating device (10) according to claim 2 , characterized in that at least in the first, second and / or third rotational position (φ1,φ2,φ3) the first connection position (46) is radially and / or circumferentially offset relative to the second connection position (48). Actuating device (10) according to claim 2 or 3, characterized in that in the first rotation position (φ1) the first connection position (46) is offset circumferentially in the second direction of rotation (42) relative to the second connection position (48) and / or in the second rotation position (φ2) the first connection position (46) is offset circumferentially in the first direction of rotation (40) relative to the second connection position (48). Actuating device (10) according to one of claims 2 to 4, characterized in that the spring element (38) is a coil spring which is arranged between a first spring contact area (64) which is displaceable along a spring axis (54) of the spring element (38) relative to the first attachment position (46) and a second spring contact area (72) which is displaceable along a spring axis (54) of the spring element (38) relative to the second attachment position (48). Actuating device (10) according to one of claims 2 to 5, characterized in that the spring device (36) counteracts a further mutual approach of the first to the second connection position (46, 48) by the spring force (44) at a direct distance (82) of the first connection position (46) from the second connection position (48) below a first direct distance (84) and counteracts a further mutual movement away of the first from the second connection position (46, 48) by the spring force (44) above a second direct distance. Actuating device (10) according to one of the preceding claims, characterized in that the first rotational position (φ1) lies between the second and third rotational positions (φ2, φ3). Actuating device (10) according to one of the preceding claims, characterized in that the spring force (44) in the first rotation position (φ1) comprises a tangential component (50) acting in the direction of the second rotation direction (42) and in the second rotation position (φ2) comprises a tangential component (52) acting in the direction of the first rotation direction (40). Clutch actuation device (11) for actuating a clutch, comprising an actuating device (10) according to one of the preceding claims for actuating the clutch depending on the rotational position of the first actuating element (16) and an actuator connected to the first actuating element (16) and allowing the first actuating element (16) to be rotated relative to the second actuating element (18). Clutch for a drive train of a vehicle, comprising a friction area for torque transmission depending on an actuating force on the friction area and a clutch actuating device (11) according to claim 9 for applying an actuating force to the friction area.