Actuating actuator for actuating a separating clutch of a hybrid module and hybrid module with the actuating actuator

Abstract

Actuating actuator (10) for actuating a separating clutch (4) of a hybrid module (5), with a housing (12) and a piston (11) which is axially displaceable relative to the housing (12), wherein a pressure chamber (15) filled with a hydraulic fluid is formed between the piston (11) and the housing (12), wherein the piston (11) can be acted upon by an actuating force (F1) generated as a function of a hydraulic pressure in the pressure chamber (15), with a shaft (31) connected to the housing (12) in a rotationally fixed manner, wherein the shaft (31) has a supply channel (16) fluidically connected to the pressure chamber (15) for supplying the pressure chamber with the hydraulic fluid, with a return device (17), wherein the return device (17) has at least one return spring (18) which applies a return force (F2) to the piston (11) counteracting the actuating force (F1), with a compensation device (30) for at least partially compensating a centrifugal force-induced change in the actuating force (F1) due to a pressure change in the pressure chamber (15), wherein the compensation device (30) has at least one centrifugal mass (21) which can be radially deflected under the influence of centrifugal force and which is operatively connected to the return spring (18) in such a way that, depending on the radial deflection of the centrifugal mass (21), a compensation force (F3) is generated by changing a preload of the return spring (18), characterized in that the centrifugal mass (21) is operatively connected to the return spring (18) via a ramp geometry (23), wherein the return spring (18) is deformed in the axial direction in the event of a radial deflection of the centrifugal mass (21) via the ramp geometry (23) in order to change the preload force.

Description

[0001] The invention relates to an actuating actuator having the features of the preamble of claim 1. Furthermore, the invention relates to a hybrid module having the actuating actuator.

[0002] A hybrid vehicle's drivetrain comprises a combination of an internal combustion engine and an electric motor, whereby the vehicle can be powered by the electric motor in a purely electric drive mode and by the internal combustion engine and the electric motor in a combined drive mode. For this purpose, a separating clutch, also known as a K0 clutch, is usually arranged between the electric motor and the internal combustion engine to separate the internal combustion engine from the electric motor and the rest of the hybrid vehicle's drivetrain. In a purely electric drive mode, the first separating clutch is opened and the internal combustion engine is decoupled, so that the drive torque of the hybrid vehicle is generated solely by the electric motor. The separating clutch should be implemented in a way that takes up as little space as possible. With various transmissions, it is also possible to supply the separating clutch directly with oil from the transmission.

[0003] The document DE 10 2019 122 920 A1 discloses a hybrid module for a drive train of a motor vehicle, comprising a separating clutch for coupling an input-side drive shaft, in particular a crankshaft, an internal combustion engine for mechanically driving the motor vehicle with an output-side intermediate shaft, in particular a rotor shaft, an electric machine for electrically driving the motor vehicle, and an actuating device for actuating the separating clutch that can be rotated with the drive shaft or the intermediate shaft. The actuating device has a pressure chamber that can be connected to a pressure source for providing a hydraulic actuating pressure that can be built up with the aid of a hydraulic medium to actuate the separating clutch, and a compensation device for at least partially compensating for a pressure change in the pressure chamber caused by centrifugal forces acting on the hydraulic medium.An actuator according to the preamble of claim 1 is disclosed in DE 10 2019 130 179 A1. Further prior art can be found in DE 10 2020 121 623 A1.

[0004] The invention is based on the object of proposing an actuating actuator which is characterized by a compact design and high operational reliability.

[0005] This object is achieved by an actuating actuator having the features of claim 1 and a hybrid module having the features of claim 9. Preferred or advantageous embodiments of the invention emerge from the subclaims, the following description and / or the attached figures.

[0006] The subject matter of the invention is an actuating actuator designed and / or suitable for actuating a separating clutch of a hybrid module. In particular, the actuating actuator serves to transmit an actuating force to the separating clutch in order to selectively close or open the separating clutch. Particularly preferably, the actuating actuator is hydraulically actuated.

[0007] The actuator has a housing. In particular, the housing is designed as a hollow cylindrical and / or annular, especially cylinder-hat-shaped housing. The housing can be designed, for example, as a cast, plastic, or sheet metal housing.

[0008] The actuating actuator has a piston that is axially displaceable relative to the housing. In particular, when the actuating actuator is actuated, the piston is axially displaceable in the axial direction with respect to a main axis from a basic position into an actuating position. A pressure chamber filled with hydraulic fluid is formed between the piston and the housing, wherein the piston can be actuated by an actuating force generated in the pressure chamber as a function of a hydraulic pressure. In particular, the piston is displaced into the actuating position under the action of the actuating force. The pressure chamber is preferably formed between the housing and the piston in the axial direction. The pressure chamber is preferably designed as an annular space that is delimited in one axial direction by the piston and in an axially opposite direction by the housing.In particular, the piston is designed as a cylindrical pot, which is supported radially on an outer circumference of the housing and / or accommodates the housing. Particularly preferably, the actuating piston and the housing are arranged coaxially and / or concentrically with respect to the main axis.

[0009] The actuator has a shaft connected to the housing in a rotationally fixed manner. In particular, the shaft is coupled to a rotor of an electric machine, in particular for the electric drive of a motor vehicle. Alternatively, the shaft forms the rotor of the electric machine. The housing preferably has a central through-opening, in particular a bore, through which the shaft is guided. The housing can be connected to the shaft in a form-fitting and / or force-fitting and / or material-fitting manner, at least in the circumferential direction.

[0010] The shaft has a supply channel that is fluidically connected to the pressure chamber and is designed and / or suitable for supplying the pressure chamber with hydraulic fluid. In particular, the supply channel is integrated and / or incorporated into the shaft. Alternatively, the supply channel is co-formed and / or delimited by the shaft, with the shaft preferably being designed as a hollow shaft for this purpose.

[0011] The actuating actuator further comprises a return device. The return device serves to automatically return the piston from the actuating position to the home position. For this purpose, the return device comprises at least or precisely one return spring, which applies a return force to the piston that counteracts the actuating force. Preferably, the piston is axially displaceable, depending on the actuating pressure in the pressure chamber, against the return force in order to actuate the separating clutch. Preferably, the return force is defined by a spring force of the at least one return spring. The return spring is preferably supported outside the pressure chamber in the axial direction, on the one hand on the housing and on the other hand on the actuating piston.In particular, the return device has a plurality of return springs, wherein the return springs are evenly distributed in the circumferential direction and / or lie on a common pitch circle diameter.

[0012] The actuating actuator has a compensation device that is designed and / or suitable for at least partially compensating a centrifugal force-induced change in the actuating force due to a pressure change in the pressure chamber. In particular, the pressure change upon rotation of the shaft is caused by centrifugal forces acting on the hydraulic fluid, which drive the hydraulic fluid radially outward. The compensation device functions to at least partially compensate for a centrifugal force-induced component of the pressure in the pressure chamber, so that the actuation of the actuating device is independent of the current speed or at least the extent of the centrifugal force-induced dependence on the current speed is reduced.For this purpose, the compensation device can apply a compensation force to the actuating piston, the amount of which is dependent on the centrifugal force, so that the centrifugal force-dependent forces cancel each other out completely or at least partially, preferably at least largely.

[0013] Within the scope of the invention, it is proposed that the compensation device has at least or exactly one centrifugal mass which can be radially deflected under the influence of centrifugal force and which is operatively connected to the return spring in such a way that, depending on the radial deflection of the centrifugal mass, the compensation force is generated by changing a preload force of the return spring. In particular, the centrifugal mass is displaced radially outwards depending on the speed and / or above a certain speed. The return spring is preferably preloaded proportionally to the radial deflection of the centrifugal mass and / or depending on a radial position of the centrifugal mass. The amount of the resulting compensation force, in particular spring force, can be adjusted such that it corresponds to the force additionally applied to the piston as a result of the speed-dependent pressure change.Preferably, the return spring is compressed or shrunk during a radial movement of the centrifugal mass in the axial direction relative to the main axis, resulting in an increase in the spring force as the compensation force. Specifically, the return device comprises several centrifugal masses, wherein the centrifugal masses are evenly distributed in the circumferential direction and / or lie on a common pitch diameter. Specifically, each return spring can be assigned a separate centrifugal mass.

[0014] The invention is based on the finding that co-rotating actuating actuators have the advantage that the actuating force can be supported internally. This allows very high contact forces to be exerted. At high speeds, the hydraulic fluid in the pressure chamber is forced radially outwards due to centrifugal force. This puts increased pressure on the piston, whereby the pressure in the pressure chamber increases due to centrifugal force, depending on the current speed, above the originally intended actuating pressure. In so-called "normally open" clutches (the clutch is actively pressed shut to close it), this can lead to the clutch closing unintentionally or to the clutch no longer being able to be opened at high speeds. In addition, the speed-dependent pressure increase impairs the controllability of the clutch system.

[0015] The centrifugal mass mechanically compensates for the speed-dependent force curve on the piston described above. Ideally, this eliminates any resulting force on the piston, significantly improving the operational reliability and controllability of the actuating actuator. Furthermore, the interaction of the centrifugal mass with the return device results in a particularly compact and component-reduced design of the actuating actuator, which is also characterized by a particularly robust construction.

[0016] According to the invention, the centrifugal mass is operatively connected to the return spring via a ramp geometry, wherein the return spring is deformed via the ramp geometry to change the preload force upon radial deflection of the centrifugal mass. For this purpose, a radial movement of the centrifugal mass is preferably converted into an axial movement on the return spring via the ramp geometry. Particularly preferably, the return spring is tensioned when the centrifugal mass is displaced radially outwards and relaxed when the centrifugal mass is displaced radially inwards. In other words, a deflection of the centrifugal mass based on the radially acting centrifugal force is converted or transformed via the ramp geometry into the corresponding axially acting deformation of the return spring depending on the radial deflection.Thus, an actuator is proposed which is characterized by a particularly simple and compact design.

[0017] In a further specific embodiment, the compensation device comprises a ramp plate having a ramp geometry. The return spring is supported on a first axial end face on the ramp plate, while the centrifugal mass is displaceable on a second axial end face in the radial direction relative to the ramp plate along the ramp geometry. In particular, the ramp plate is arranged axially between the centrifugal mass and the return spring. In principle, a separate ramp plate can be assigned to each centrifugal mass. Alternatively, however, the multiple centrifugal masses can also interact via a common ramp plate. For example, the ramp plate is designed to be annular and / or circumferential to the main axis. Particularly preferably, the ramp plate is designed as a formed part or is formed by forming.Thus, an actuator is proposed which is characterized by a particularly simple and cost-effective design.

[0018] In a further development, the ramp geometry has a ramp profile that rises in the radial direction. When the centrifugal mass moves radially along the ramp geometry, an axial movement of the ramp plate is thus implemented. More precisely, the ramp plate is moved axially in the direction of the return spring due to the ramp geometry when the centrifugal mass is driven radially outwards under the influence of centrifugal force. In principle, the ramp plate can be conical and / or concave when viewed in cross-section. Alternatively, the ramp plate has a radial section and a radially adjoining ramp section. The ramp geometry preferably has an inclined surface which is angled relative to a radial plane of the main axis at an inclination angle of more than 10 degrees, preferably more than 30 degrees, in particular more than 50 degrees.The centrifugal mass preferably has a counter surface complementary to the ramp geometry, in particular the inclined surface. For example, at least the inclined surface and / or the counter surface are designed as a sliding surface. Thus, a ramp plate is proposed which, depending on the ramp geometry, can impart a correspondingly high centrifugal force-induced compensation force to the piston.

[0019] In a further specific embodiment, it is provided that the housing has a radial wall section which is designed and / or suitable for axially delimiting the pressure chamber. The centrifugal mass is arranged outside the pressure chamber on an outer side of the wall section. In particular, the centrifugal mass is mounted on the wall section so as to be movable, in particular displaceable, in the radial direction. The wall section preferably extends in a radial plane of the main axis. Optionally, the housing has a cylindrical section extending axially to the main axis, wherein the wall section adjoins the cylindrical section in the radial direction. The housing is connected to or supported by the shaft via the cylindrical section.Optionally, the wall section preferably has a circumferential receiving groove on its outer diameter for receiving a sealing device, wherein the piston rests sealingly against the wall section via the sealing device. For this purpose, the sealing device comprises at least one sealing ring, in particular a piston sealing ring, which is received in the receiving groove. Optionally, the piston can be slidably supported on the wall section via one or more additional sliding rings. Thus, an actuating actuator is proposed which is characterized by simple components and particularly simple assembly. Furthermore, an actuating actuator with a small, in particular axial, installation space requirement is proposed.

[0020] In a further specific embodiment, the centrifugal mass is guided in a straight line in the radial direction in a guide groove formed on the wall section and / or the ramp plate. The centrifugal mass preferably has a guide section that engages with the guide groove. For example, the centrifugal mass is held in the guide groove in a form-fitting manner in the axial direction and / or in the circumferential direction via the guide section. For this purpose, the guide groove can be designed, for example, as a T-slot and the guide section as a corresponding T-slot nut. The guide groove can thus ensure secure guidance of the centrifugal mass in the radial direction.

[0021] In a further embodiment, the piston has a radially inwardly directed support section, wherein the return spring is axially supported on the piston via the support section outside the pressure chamber. In particular, the return spring is fixedly mounted or supported on the wall section in the axial direction. In other words, the support section forms a spring seat for the return spring. The support section preferably extends in a radial plane of the main axis and / or is aligned in the same direction or parallel to the wall section. In the simplest embodiment, the support section can be formed by a formed material section, in particular a collar, of the piston. Alternatively, the support section is formed by a separate component, in particular an annular disk, which is mounted at least axially fixedly on the piston.By supporting the return spring on the support section, a reliable transmission of the compensation force to the piston can be ensured and a compact design of the actuating actuator can be realized.

[0022] In a further specific implementation, the return spring is designed as a compression spring which is supported under preload in the axial direction on the one hand on the ramp plate and on the other hand on the support section. In other words, the centrifugal mass, the ramp plate and the return spring are arranged in the axial direction between the wall section and the support section. In the sense of the invention, a compression spring is understood to be a spring which transmits or impresses a compressive force as the restoring force onto the piston in the axial direction. The return spring can for this purpose be designed, for example, as a helical compression spring or a leaf spring. Thus, a return spring is proposed which is characterized by a robust and cost-effective design.

[0023] In a further development, the return device is provided with a further return spring which applies a further return force to the piston. The further return spring is supported in the axial direction on the one hand on the housing and on the other hand on the piston. The further return spring can be used in addition to the return spring in order to increase the return force independently of the speed. In particular, the further return spring is supported for this purpose in the axial direction directly on the housing, in particular in the cylinder section, and in the opposite axial direction directly on the piston, in particular the support section. The further return spring can, for example, be designed as a further compression spring, in particular a disc spring, which is arranged coaxially and / or concentrically to the shaft with respect to the main axis.Thus, an actuator is proposed which is characterized by a particularly high operational reliability.

[0024] Another subject matter of the invention relates to a hybrid module for a drive train of a motor vehicle. In particular, the hybrid module operates between an internal combustion engine, in particular a combustion engine, and a transmission. The hybrid module has a separating clutch—often also referred to as a K0 clutch—which is designed and / or suitable for coupling an input-side drive shaft, in particular a crankshaft, of the internal combustion engine to an output-side intermediate shaft, in particular a rotor shaft, of an electric machine. In particular, a torque can be transmitted from the internal combustion engine to the hybrid module via the separating clutch, or the hybrid module can be separated from the internal combustion engine. The hybrid module has an actuating actuator for actuating the separating clutch, as already described above.In particular, the shaft is formed by the intermediate shaft, in particular the rotor shaft, wherein the actuating actuator rotates with the intermediate shaft or is connected in a rotationally fixed manner.

[0025] Further features, advantages, and effects of the invention will become apparent from the following description of preferred embodiments of the invention. These show: Fig. 1 a schematic representation of a drive train with a hybrid module as an embodiment of the invention, Fig. 2 a schematic representation of an actuating actuator for the hybrid module according to Fig. 1.

[0026] Fig. Figure 1 shows a simplified schematic representation of a drive train 1 for a vehicle, in particular a hybrid vehicle. The drive train 1 comprises an internal combustion engine 2, in particular a combustion engine, and an electric machine 3, in particular an electric motor. A separating clutch 4 is arranged between the internal combustion engine 2 and the electric machine 3. The separating clutch 4 and the electric machine 3 together form a hybrid module 5.

[0027] The electric motor 3 is connected, for example, via a dual clutch (not shown), to a transmission 6, in particular two sub-transmissions with different gear ratios. The transmission 6 transmits or converts a torque generated by the internal combustion engine 2 and / or the electric motor 3 to at least one driven wheel 7 of the vehicle.

[0028] The electric machine 3 has a rotatable rotor 8 and a stationary stator 9, wherein the rotor 8 is rotationally fixedly connected to a shaft 31. For this purpose, the shaft 31 can be coupled to a rotor shaft of the electric machine 3 or can itself form the rotor shaft for the rotor 8 of the electric machine 3. Furthermore, the shaft 31 can be coupled to a transmission input shaft of the transmission 6 or can form the transmission input shaft. The internal combustion engine 2 has a crankshaft 32, which can be connected or is connected to the shaft 31 via the separating clutch 4 in a torque-transmitting manner.

[0029] The hybrid module 5 has an actuating actuator 10, only indicated schematically here, which serves to hydraulically actuate the separating clutch. For example, the separating clutch 4 is open in a non-actuated state ("normally open clutch") and is actively closed by the actuating actuator 10 to close it. In purely electric motor operation, the separating clutch 4 is open and the internal combustion engine 2 is separated from the power flow. In hybrid operation, the separating clutch 4 is closed and the internal combustion engine 2 is drive-coupled to the hybrid module 5. The electric motor 3 can then be used, for example, to provide supporting torque and to recuperate braking energy.

[0030] Fig.Figure 2 shows the actuating actuator 10 in a schematic sectional view along a main axis 100. The main axis 100 is defined by a rotational axis of the shaft 31. The actuating actuator 10 has a piston 11 and a housing 12, which are arranged coaxially and / or concentrically with respect to the main axis 100. The actuating actuator 10 is thus designed as a concentric slave cylinder, also called a "CSC."

[0031] The piston 11 is designed in the form of a cylindrical pot, which is radially supported with its inner circumference on a wall section 20 of the housing 12 via at least one sealing device 13. The housing 12 is thus arranged or accommodated radially within the piston 11, which is designed as a cylindrical pot. For this purpose, the wall section 20 extends circumferentially to the main axis 100 in a radial plane and has a circumferential receiving groove 14 on its outer circumference, in which the sealing device 13 is positively received. For example, the sealing device 13 can comprise one or more sealing and / or sliding rings.

[0032] Between the piston 11 and the housing 12, a pressure chamber 15 filled with hydraulic fluid is formed, which is delimited with respect to the main axis 100 in an axial direction 103 by the piston 11 and in an axial opposite direction 104 by the housing 12, in particular the wall section 20. The pressure chamber 15 is designed as an annular space surrounding the main axis 100. To build up hydraulic pressure in the pressure chamber 15, the pressure chamber 15 is supplied with hydraulic fluid via a supply channel 16 provided in the shaft 31, whereby an actuating force F1 is generated as a function of a hydraulic pressure in the pressure chamber 15. For example, the shaft 31 is designed as a hollow shaft for this purpose.

[0033] Upon actuation, the hydraulic pressure in the pressure chamber 15 is increased, whereby the piston 11 is axially displaced from a basic position 101 into an actuating position 102 depending on the resulting actuating force F1 acting on the piston 11. In the actuating position 102, the actuating force F1 is transmitted to the separating clutch 4, so that the separating clutch 4 is closed.

[0034] The actuating actuator 10 has a return device 17, wherein the return device 17 applies a return force F2 to the piston 11 counter to the actuating force F1 in the direction of the home position 101. For this purpose, the return device 17 has at least one return spring 18, which is axially supported between the piston 11 and the housing 12. For example, the return spring 18 is formed by a leaf spring assembly, wherein the return force F2 is defined by a spring force applied by the leaf spring assembly.

[0035] The housing 12 is connected to the shaft 31 in a rotationally fixed manner, so that the actuating actuator 10 rotates with the shaft 31 during operation. For this purpose, the housing 12 has a cylindrical section 19, which adjoins the wall section 20 in the axial opposite direction 104. The cylindrical section 19 is connected to the shaft 31 at least in the circumferential direction in a form-fitting manner, e.g. via a spline, and / or a force-fitting manner, e.g. via a press fit. Furthermore, the housing 12 can be fixed to the shaft 31 in the axial direction, for example in a form-fitting or material-fitting manner. For example, the housing 12 is made in one piece, e.g. from a cast.

[0036] A co-rotating actuating actuator 10 has the advantage that the actuating force F1 can be supported internally. This allows for very high contact forces to be exerted. At high speeds, the hydraulic fluid in the pressure chamber 15 is forced radially outward due to centrifugal force, increasing the pressure acting on the piston 11 and thus the actuating force F1. This can lead to the separating clutch 4 being closed unintentionally or the internal combustion engine 2 no longer being able to be disengaged at high speeds. Furthermore, the speed-dependent pressure increase impairs the controllability of the actuating actuator 10.

[0037] In order to compensate for the pressure increase caused by centrifugal force on the hydraulic fluid in the pressure chamber 15 as the speed of the shaft 31 increases, the actuating actuator 10 has a compensation device 30 which, depending on the speed of the shaft 31, imposes a compensation force F3 on the piston 11 that counteracts the actuating force F1. For this purpose, the compensation device 30 is operatively connected to the return device 17 in such a way that the compensation force F3 is generated by a change in the preload and thus by a change in the spring force of the return spring 18. The centrifugal force-induced force components acting on the piston 11 and the compensation force F3 can completely or at least largely cancel each other out.

[0038] For this purpose, the compensation device 30 has at least one centrifugal mass 21, which is mounted on the wall section 20 outside the pressure chamber 15 or on an end face facing away from the pressure chamber 15 and is movable in the radial direction. Furthermore, the compensation device 30 has a ramp plate 22 with a ramp geometry 23, via which the centrifugal mass 21 interacts with the return spring 18. The ramp plate 22 has a radial section 24 and an adjoining ramp section 25, wherein the ramp section 25 is angled relative to the radial section 24 to form the ramp geometry 23. The ramp geometry 23 is formed by an inclined surface which has an ascending profile in the radial direction. The centrifugal mass 21 has a shape complementary to the ramp geometry 23, wherein the centrifugal mass 21 and the ramp plate 25 are supported on one another in a sliding manner in the radial direction.The centrifugal mass 21 is guided in a straight line in the radial direction on the wall section 20 or, alternatively, on the ramp plate 24 via at least one guide groove 26. For this purpose, the guide groove 26 is designed as a radially extending groove, with the centrifugal mass 21 having at least one guide section 27 that engages with the guide groove 26. The guide section 27 is received in the guide groove 26 in a form-fitting manner in the circumferential direction in order to guide the centrifugal mass 21 straight or linearly in the radial direction.

[0039] The return spring 18 is supported on a side facing away from the centrifugal mass 21 in the axial direction 103 on the ramp plate 22, in particular the radial section 24, and in an axially opposite direction 104 via a support section 28 on the piston 11. The support section 28 is designed, for example, as an annular disc, which is axially fixed to the piston 11, e.g., by a retaining ring, and extends parallel to the wall section 20.

[0040] Above a certain speed, the centrifugal mass 21 shifts radially outward relative to the ramp plate 22 along the ramp geometry 23, similar to a centrifugal clutch (speed-controlled). Due to the rising ramp profile, a radial movement of the centrifugal mass 21 is converted into an axial movement of the ramp plate 22 in the opposite axial direction 104, whereby the return spring 18 is further preloaded. The amount of the resulting compensation force F3 can be adjusted via the ramp geometry 23 of the ramp plate 24 so that it corresponds to the force components due to the speed-dependent pressure increase in the pressure chamber 15. For example, the speed-dependent compensation force F3 and the force components resulting from the pressure increase can be adjusted to one another such that they have the same amount at every speed and cancel each other out.Depending on the ramp geometry 23 of the ramp plate 22, a compensation force F3 counteracting the centrifugal force is generated by increasing the spring force of the return spring 18. Thus, the actuating force F1 is essentially independent of the rotational speed of the shaft 31 and the resulting centrifugal forces.

[0041] Should a greater return force F2 be necessary to push or hold the piston 11 in its home position 101, an additional return spring 29 can be added as part of the return device 17 between the housing 12 and the piston 11 or between the cylinder section 19 and the support section 28. The invention thus describes a mechanical compensation of the speed-dependent force curve on the piston 11 described above, which is characterized by a particularly compact design and a robust construction. List of reference symbols 1 drivetrain 2 internal combustion engine 3 electric machine 4 Separating clutch 5 Hybrid module 6 gearboxes 7 tires 8 Rotor 9 Stator 10 Actuator 11 pistons 12 housings 13 Sealing device 14 mounting groove 15 pressure chamber 16 supply channel 17 Reset device 18 Return spring 19 Cylinder section 20 wall section 31 Wave 32 Crankshaft 100 Main axis 101 Basic position 102 Operating position 103 axial direction 104 axial opposite direction F1 actuation force F2 restoring force F3 Compensation force

Claims

[1] Actuating actuator (10) for actuating a separating clutch (4) of a hybrid module (5), with a housing (12) and a piston (11) which is axially displaceable relative to the housing (12), wherein a pressure chamber (15) filled with a hydraulic fluid is formed between the piston (11) and the housing (12), wherein the piston (11) can be acted upon by an actuating force (F1) generated as a function of a hydraulic pressure in the pressure chamber (15), with a shaft (31) connected to the housing (12) in a rotationally fixed manner, wherein the shaft (31) has a supply channel (16) fluidically connected to the pressure chamber (15) for supplying the pressure chamber with the hydraulic fluid, with a return device (17), wherein the return device (17) has at least one return spring (18) which applies a return force (F2) to the piston (11) counteracting the actuating force (F1), with a compensation device (30) for at least partially compensating a centrifugal force-induced change in the actuating force (F1) due to a pressure change in the pressure chamber (15), wherein the compensation device (30) has at least one centrifugal mass (21) which can be radially deflected under the influence of centrifugal force and which is operatively connected to the return spring (18) in such a way that, depending on the radial deflection of the centrifugal mass (21), a compensation force (F3) is generated by changing a preload of the return spring (18), characterized by that the centrifugal mass (21) is operatively connected to the return spring (18) via a ramp geometry (23), wherein the return spring (18) is deformed in the axial direction in the event of a radial deflection of the centrifugal mass (21) via the ramp geometry (23) in order to change the preload force. [2] Actuating actuator (10) according to claim 1, characterized bythat the compensation device (30) has a ramp plate (22) with the ramp geometry (23), wherein the return spring (18) is supported on a first axial end face on the ramp plate (22) and wherein the centrifugal mass (21) is displaceable on a second axial end face in the radial direction relative to the ramp plate (22) along the ramp geometry (23). [3] Actuating actuator (10) according to claim 2, characterized by that the ramp geometry (23) has a ramp profile which rises in the radial direction, wherein an axial movement of the ramp plate (24) is implemented upon a radial deflection of the centrifugal mass (21) along the ramp geometry (23). [4] Actuating actuator (10) according to claim 3 characterized bythat the housing (12) has a radial wall section (20) for axially delimiting the pressure chamber (15), wherein the centrifugal mass (21) is arranged outside the pressure chamber (15) on an axial end face of the wall section (20). [5] Actuating actuator (10) according to claim 4, characterized by that the centrifugal mass (21) is guided straight in the radial direction in a guide groove (26) formed on the wall section (20) and / or the ramp plate (22). [6] Actuating actuator (10) according to claim 5 characterized by that the piston (11) has a radially inwardly directed support section (28), wherein the return spring (18) is supported axially on the piston (11) outside the pressure chamber (15) via the support section (28). [7] Actuating actuator (10) according to claim 6, characterized bythat the return spring (18) is designed as a compression spring which is supported under a prestress in the axial direction on the one hand on the ramp plate (22) and on the other hand on the support section (28). [8] Actuating actuator (10) according to one of the preceding claims, characterized by that the return device (17) has a further return spring (29) which applies a further return force to the piston (11), wherein the further return spring (29) is supported in the axial direction on the one hand on the housing (12) and on the other hand on the piston (11). [9] Hybrid module (5) for a drive train (1) of a motor vehicle, with a separating clutch (4) for coupling an input-side drive shaft, in particular a crankshaft (32), of an internal combustion engine (2) with an output-side intermediate shaft, in particular a shaft (31), of an electric machine (3), characterized byan actuating actuator (10) for actuating the separating clutch (4) according to one of the preceding claims.

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