Clutch assembly

Abstract

The invention relates to a kind of clutch assemblies, it includes: at least one controllable friction clutch (3,3 '), the friction clutch is used to carry out the variable torque transmission between clutch input component (4,4 ') and clutch output component (5,5 '), hydraulic actuator assembly (6), the actuator assembly is used to manipulate friction clutch (3,3 '), wherein, actuator assembly (6) has hydraulic pump (10), hydraulic chamber (12,12 ') and backflow element (13) with shield (11), in the hydraulic chamber, the hydraulic pressure for friction clutch (3,3 ') is constructed by means of hydraulic pump (10), when not manipulating hydraulic pump (10), hydraulic liquid can flow from hydraulic chamber (12,12 ') to shell space (8) via the backflow element, wherein, hydraulic liquid (9) defines the filling level (F) in shell space (8);Wherein, in the stationary state, the exit opening (14) of backflow element (13) is below the filling level (F) of hydraulic liquid (9).

Description

Technical Field

[0001] The present invention relates to a hydraulically operable clutch assembly, particularly a clutch assembly for the drive system of a motor vehicle. Background Technology

[0002] A shaft module with two separate friction plate clutches is known from EP 1282560 A2. For torque introduction, an angular transmission device is provided that rotates and drives the hollow shaft. The friction plate clutches are located at the ends of the hollow shaft and can be operated by means of electrically motor-operated ball ramp assemblies.

[0003] According to US2010 / 0094519 A1, corresponding to DE 102009005378 A1, an all-wheel drive system for a motor vehicle is known, having a permanently driven front axle and a rear axle that can be driven as needed. Torque distribution between the front and rear axles is performed via a distribution transmission (which can be controlled by an electronic adjustment unit) with friction plate clutches and a longitudinal drive shaft. At the rear axle, the introduced torque can be transmitted to the two side axles by means of a second friction plate clutch.

[0004] A hydraulic actuation assembly for engaging a drive shaft in a drive system of a motor vehicle is known from WO2010081743 A1. The hydraulic actuation assembly includes a pump for generating hydraulic pressure, a pressure reservoir, and two hydraulic operating units for actuating a corresponding associated clutch.

[0005] An electric drive device for driving a drive shaft of a motor vehicle is known from WO2017157479A1. The electric drive device includes a motor, a transmission unit, and a dual-clutch unit. The dual-clutch unit includes two plates that can be individually operated by means of corresponding hydraulic actuators to transmit torque to corresponding side shafts.

[0006] A drive system having an electric motor and two side shafts is known from WO 2019 / 174716 A9, each side shaft having a controllable friction clutch for adjusting the transmittable torque.

[0007] In hydraulic actuator systems, the necessary volumetric flow can be achieved by a motor-pump unit through motor speed regulation or current regulation. Systems with speed regulation are particularly used in units sold by the applicant under the names "Booster Rear Drive Unit" or "Twin AWD". Systems with current regulation are particularly used in units sold by the applicant under the name "Twinster". Depending on the design of the hydraulic regulation system, fluctuations in hydraulic pressure can occur due to foaming in the hydraulic fluid. This can lead to inaccuracies in torque distribution within the vehicle's drive system. Summary of the Invention

[0008] Therefore, the object of the present invention is to provide a hydraulically operable clutch assembly, particularly for torque transmission in the drive system of a motor vehicle, which ensures precise torque adjustment, especially in the case of prolonged operation.

[0009] To address this task, a clutch assembly, particularly for a drive system of a motor vehicle, is proposed, comprising: at least one controllable friction clutch having a clutch input component and a clutch output component; a hydraulic actuator assembly having a hydraulic pump, a hydraulic chamber connected thereto (in which hydraulic pressure for loading the controllable friction clutch can be constructed by the hydraulic pump), and a return element with a shield, through which hydraulic fluid can flow from the hydraulic chamber into a reservoir, wherein, in a static state, the hydraulic fluid defines a fill level in the reservoir; wherein, in a static state, the exit opening of the return element is located below the fill level of the hydraulic fluid.

[0010] The advantage of this clutch assembly lies in the fact that, due to the design of the hydraulic system with return elements and shielding components, the tendency of the hydraulic fluid to foam is reduced, thus maintaining the hydraulic pressure at least to a large extent constant with a constant drive pump. This allows for precise quantification of the friction clutch's operating force even during prolonged operation, or the maintenance of the theoretical torque to be transmitted without pressure drop. Overall, the clutch assembly thus provides precise and targeted torque adjustment at the relevant drive system and correspondingly high driving stability, especially under prolonged clutch operation.

[0011] Clutch assemblies with controllable friction clutches are particularly used in the drive systems of motor vehicles to transmit torque to a rear-mounted drive shaft as needed and under driving conditions. Here, the friction clutch can be operated by an actuator in an open position where no torque is transmitted, a closed position where full torque is transmitted, and an intermediate position for variable torque transmission. For example, such a clutch assembly may have a clutch to transmit torque to or within a rear-mounted drive shaft as needed. The clutch assembly may also be designed with two clutches to transmit torque from the drive shaft to two side shafts or to adjust the torque according to the amount.

[0012] According to one embodiment, a lubricant is provided for lubricating and / or cooling (multiple) controllable friction clutches, wherein the lubricant for (multiple) friction clutches and the hydraulic fluid for the actuator assembly are different and hydraulically separated fluids. The hydraulic system for lubricating and cooling (multiple) friction clutches and the hydraulic system for operating (multiple) friction clutches are implemented independently of each other, and the corresponding hydraulic chambers are sealed to each other.

[0013] For example, the hydraulic fluid in the reservoir of the actuator assembly in a static state can be less than 400 ml and / or greater than 200 ml. In the installed state of the clutch assembly, the hydraulic chamber or reservoir can be designed to taper downwards. The horizontal cross-sectional area of ​​the lower region of the reservoir can be smaller than the horizontal cross-sectional area of ​​the upper region of the reservoir. The suction area of ​​the hydraulic pump is preferably located at the lowest point of the hydraulic system, thereby ensuring reliable hydraulic pumping action even when the vehicle is in an inclined position. When the vehicle is on a straight and / or inclined plane, in the installed state, the exit opening of the return element leads into the lower region of the preferred reservoir and / or at least 10 mm below the preferred hydraulic fluid filling height.

[0014] The hydraulic pump can be designed as a unidirectional pump, driven in the direction of rotation to deliver hydraulic fluid. When the pump is shut off, the hydraulic system becomes depressurized, and the hydraulic fluid can flow out through a baffle and a return channel into the depressurized housing space. Alternatively, the hydraulic pump can be designed as a bidirectional pump, delivering hydraulic fluid from a reservoir to a friction clutch in the first direction of rotation to engage the friction clutch in the closed direction, and delivering hydraulic fluid back from the friction clutch to the reservoir in the second direction of rotation to disengage the friction clutch.

[0015] In one embodiment, the return element can be connected to the upper housing section or a return line formed therein, allowing liquid to flow downwards from the cavity into the return element and then out through it to the pressureless housing section or reservoir below. Here, a higher pressure exists in the hydraulic chamber, which the hydraulic fluid uses to flow into the return element. Preferably, an impact wall is provided in the reservoir, allowing the hydraulic fluid flowing out of the return element at a higher flow velocity to impact against this wall, thereby minimizing the tendency to foam. The hydraulic energy present in the form of higher pressure in front of the baffle is converted into a higher flow velocity by the baffle. The hydraulic fluid impacts the impact wall at a higher velocity, where the reservoir is in a near-pressureless state or ambient pressure.

[0016] The reflux element can be designed in a sleeve or tubular shape. The exit opening and / or channel of the reflux element can have a diameter that is at least six times larger than the minimum opening diameter of the baffle. The flow velocity through the reflux element can be less than or equal to 30 m / s. For example, the pressure drop between the inlet and outlet openings of the reflux element can be less than 5 bar.

[0017] According to one feasible embodiment, the return element may have a laterally exiting opening, wherein the axis of the lateral opening may be angled between 45° and 135° with the longitudinal axis of the tubular return element. In this embodiment, the free end of the return element is preferably closed. For this purpose, a closure may be provided at the return element, against which the incoming hydraulic fluid impinges at a higher flow velocity and then flows out through the lateral opening at a lower flow velocity. In this embodiment, a baffle is preferably arranged close to the upper housing section above it so that fluid flows through the baffle into the channel.

[0018] According to an alternative embodiment, the reflux element may have an end-side exit opening with a hole in which a shield is arranged, i.e., away from the upper housing section located above it. Here, no lateral opening is provided. In this embodiment, the exit opening of the reflux element is preferably oriented in the direction of the housing wall serving as an impact plate in the reservoir. The distance between the exit opening and the housing wall is preferably between 1 mm and 5 mm.

[0019] The length of the channel is preferably at least twice the diameter of the channel and / or the diameter of the opening. For example, the diameter of the channel can be between 3.5 mm and 10 mm.

[0020] The hydraulic pump can be designed in such a way that it can generate hydraulic pressure greater than 25 bar.

[0021] An exemplary embodiment for distributing torque introduced by a longitudinal drive shaft to two side shafts may include an angular transmission device, particularly with a drive pinion driven by the longitudinal drive shaft and a crown gear (or crown wheel, i.e., Tellerrad) meshing therewith, which may be arranged coaxially with two friction clutches. A first friction clutch is configured to transmit a first torque to a first side shaft, and a second friction clutch is configured to transmit a second torque to a second side shaft. In this embodiment, a stopper acts as an adjusting element in the hydraulic system, wherein the pressure generated by the pump and the stopper acts equally on both clutches. In this way, the two clutches transmit torque, thereby achieving a lateral locking function between the two side shafts.

[0022] Especially considering the lateral locking function of the "Twin AWD" (Twin All Wheel Drive Unit), a constant hydraulic pressure is required as the output variable when the actuator motor operates at a constant speed (input variable) for an extended period. This clutch assembly is well-suited for such applications because it allows the hydraulic pressure to be kept constant. In this way, the operating force acting on the two friction clutches and therefore the torque to be transmitted can also be kept constant. Pressure drop in the hydraulic system is effectively avoided when the actuator motor operates at a constant speed. Attached Figure Description

[0023] Preferred embodiments are described below with reference to the accompanying drawings. Wherein:

[0024] Figure 1 The components according to the present invention are illustrated in schematic diagram;

[0025] Figure 2 It shows the manipulation based on Figure 1 The component is an exemplary chart showing the trend of pressure over time;

[0026] Figure 3 The components according to the invention are illustrated in a modified embodiment.

[0027] Figure 4A It shows according to Figure 4B The cutting lines 4A-4A in another embodiment of the component according to the invention;

[0028] Figure 4B The diagram shows the section line 4B-4B. Figure 4A Components in;

[0029] Figure 4C The section plane passing through the axis is shown. Figure 4A and Figure 4B Components;

[0030] Figure 5 A cross-sectional view shows components according to the invention in another modified embodiment;

[0031] Figure 6A A cross-sectional view shows components according to the invention in another modified embodiment;

[0032] Figure 6B A detailed enlarged view shows Figure 6A The reflux element in the middle. Detailed Implementation

[0033] Figure 1 A clutch assembly 2 according to a first embodiment of the present invention is shown, wherein, Figure 2 A diagram illustrating an exemplary pressure distribution with such a clutch assembly is shown. These two diagrams will be described together below.

[0034] The clutch assembly 2 includes a controllable friction clutch 3 for torque transmission between a clutch input component 4 and a clutch output component 5, a hydraulic actuator assembly 6 for operating or controlling the friction clutch 3, and a housing 7 in which a reservoir 8 is filled with hydraulic fluid 9. Such a clutch assembly 2 with a controllable friction clutch 3 can be used, in particular, in the drive system of a motor vehicle to transmit torque to a rear-mounted drivetrain as needed and under driving conditions.

[0035] Actuator assembly 6 includes a hydraulic pump 10, a hydraulic chamber 12 (in which hydraulic pressure is built up when the hydraulic pump is operated to load a controllable friction clutch 3), and a return element 13 with a shield 11. The return element 13 is hydraulically connected to the hydraulic chamber 12, allowing fluid to flow from the chamber through the return element into a pressureless housing space or reservoir 8 located below it. The exit opening 14 of the return element 13 is located below the fill level F of the hydraulic fluid 9. Optionally, a housing wall 16 may be provided, against which the hydraulic fluid flowing out of the return element 13 at a higher flow rate can impact. This achieves a particularly low tendency to foam.

[0036] exist Figure 2 An exemplary pressure trend Pa of the component according to the invention with respect to time t is shown. It can be seen that when pump 10 is activated or the rotational speed n is suddenly increased, the pressure build-up from pressure 0 to the target pressure Pt occurs very rapidly, i.e., within a time window that can be particularly less than 200 milliseconds. Furthermore, it can be seen that after the target pressure Pt is rapidly reached, the pressure Pa remains stable or nearly constant at a constant rotational speed n and does not decrease with respect to time t. No uncontrolled pressure drop that could occur due to air bubbles present in the oil will occur.

[0037] Further details of the hydraulic assembly are described below, and these details are optional. A filter 18 may be provided in the line 17 between the actuator 6 and the baffle 11. A greater pressure exists before the baffle 11 than after it in the flow direction. The return element 13 may be designed in a sleeve or tubular shape, wherein the opening diameter of the baffle 11 is smaller than the inner diameter of the return element 13 or its exit opening 14, particularly less than one-sixth of the inner diameter. For example, the flow velocity through the return element may be less than or equal to 30 m / s. For example, the pressure drop between the inlet and outlet openings of the return element may be less than 5 bar. The hydraulic actuator assembly 6 may be designed for the total volume of the hydraulic fluid, which, in a static state, may be, for example, less than 400 ml and greater than 200 ml in the reservoir 8.

[0038] Hydraulic pump 10 is currently designed as a unidirectional pump, which can be driven in the rotational direction by a controllable motor 15 to deliver hydraulic fluid from the oil pan to the hydraulic chamber 12. The necessary volumetric flow can be achieved by controlling the rotational speed of the pump motor 15. A filter 19 may optionally be installed in the supply line between the oil pan and pump 10. When pump 10 is shut off, the hydraulic system becomes depressurized, and hydraulic fluid 9 can flow out via the baffle 11 and return passage 13 into the depressurized reservoir 8 or oil pan. Additionally, oil can also flow out via pump 10, i.e., due to the back pressure present in the system causing the pump to passively reverse after shutdown, and the oil flows back against the active delivery direction. The unit consisting of pump 10 and motor 15 can also be referred to as a motor-pump unit. However, implementations without a separate drive unit are also possible, for example, in which the pump is passively driven via a rotating drive shaft in the vehicle's drive system. According to another embodiment not shown here, the hydraulic pump can also be designed as a bidirectional pump that delivers hydraulic fluid into the hydraulic chamber 12 when driven in the first rotational direction to operate the clutch 3 in the closed direction, and delivers hydraulic fluid out of the hydraulic chamber 12 when driven in the opposite rotational direction to operate the clutch 3 in the open direction.

[0039] The actuator assembly 6 may further include a piston cylinder unit 20 having a hydraulic chamber 12 and an adjusting piston 22 movably disposed within the hydraulic chamber 12. The adjusting piston 22 is connected to the actuation element 23 of the friction clutch 3. The piston 22 is moved in the direction of the actuation element 23 by pressure loading the hydraulic chamber 12, causing the clutch to transmit torque. The desired torque can be variably adjusted as needed via the hydraulic pressure generated by the pump 10. Currently, the piston cylinder unit includes a spring 24 that loads the piston 22 against the hydraulic pressure of the pump 10, or is preloaded against the piston. When the pump 10 is disengaged, the spring 24 compresses the piston 22 in the direction of the hydraulic chamber 12, thereby disengaging the clutch 3 again.

[0040] Figure 3 A clutch assembly 2 according to the invention is shown in a slightly modified embodiment, which corresponds to the maximum extent to Figure 1 The implementation scheme is described above. In this regard, reference can be made to the commonalities. Here, identical or corresponding details are given the same reference numerals. The only difference is that, according to... Figure 2 In the embodiment, the actuator assembly 6 has a second adjustment unit 20' for operating the second clutch 3'. Both adjustment units 20, 20' are hydraulically connected to the pump 10 and are loaded by the pump with hydraulic pressure. The clutch assembly 2 with two friction clutches 3, 3' can be used in power branch units for torque transmission from the input shaft to the two output shafts. Here, the two adjustment units 20, 20' of the two clutches 3, 3' are loaded with the same pressure, so that the same torque exists at the two side shafts.

[0041] Figures 4A to 4C A clutch assembly 2 according to the invention is shown in another embodiment, which generally corresponds to the one according to [the invention]. Figure 3 Schematic embodiments. In this regard, reference is made to the above description in terms of commonalities, wherein the same or corresponding details are given the same reference numerals.

[0042] exist Figures 4A to 4C The components shown include an input shaft 25 having a connecting element 26 for introducing torque and a drive pinion 27 for driving an intermediate shaft. The input shaft 25 is rotatably supported in the housing 7 about a rotation axis A25 by means of support devices 28 and 28'. The pinion 27 meshes with a crown gear 29, which is anti-rotatably connected to the intermediate shaft 30. The pinion and crown gear together constitute an angular transmission device. The intermediate shaft 30 is rotatably supported about a rotation axis A30 by means of support devices 32, 32', which intersects the rotation axis A25 of the input shaft at a distance. A first end of the intermediate shaft 30 is drivenly connected to a first controllable friction clutch 3 for torque transmission to a first side shaft (not shown). A second end of the intermediate shaft 30 is drivenly connected to a second controllable friction clutch 3' to drive a second side shaft (not shown). The clutches 3 and 3' are designed identically in structure and function; therefore, only one is described representatively below.

[0043] The friction clutches 3, 3' have a clutch input component 4, 4' anti-rotationally connected to an intermediate shaft 30 and a clutch output component 5, 5' connectable to an associated side shaft for torque transmission, as well as a plate assembly 35, 35' for torque transmission between the input and output components. The plate assemblies 35, 35' each include an inner plate anti-rotationally and axially movable with respect to the clutch input component 4, 4' and an outer plate anti-rotationally and axially movable with respect to the clutch output component 5, 5', the inner and outer plates being arranged alternately axially. The clutch output component 5, 5' is designed as a clutch basket or outer plate holder with a shaft section 33, 33' rotatably supported in the housing 7 via corresponding support devices 34, 34'.

[0044] Each of the two clutches 3, 3' can be operated by the associated adjusting unit 20, 20', which is jointly hydraulically operated by pump 10. Since the same hydraulic pressure exists at both adjusting units 20, 20', the two clutches 3, 3' transmit the same torque to the corresponding side shafts. The two adjusting units 20, 20' are designed identically in structure and function, and therefore both are described together below.

[0045] As in Figure 1 and Figure 3 As schematically shown, the adjustment units 20, 20' are functionally similarly constructed. They are hydraulically actuated and each includes annular pistons 22, 22', which are axially movable within corresponding annular hydraulic chambers 12, 12' of the housing 7. The hydraulic chambers 12, 12' are hydraulically connected to the pump 10 via corresponding lines 21, thereby generating hydraulic pressure in the hydraulic chambers 12, 12' when the pump is operated, causing the pistons 22, 22' housed therein to move axially in the lateral direction. The axial force transmitted by the pistons 22, 22' is transmitted to the corresponding actuating elements 23, 23' via axial bearings 36, 36'. The axial bearings 36, 36' serve to decouple the actuating elements 23, 23', which rotate with the clutch output components 5, 5', from the rotational arrangement of the adjustment units 20, 20' or pistons 22, 22' within the housing 7. To return the actuators 6,6' or pistons 22,22' to their original positions, return springs 24,24' can be provided. The return springs 24,24' are arranged such that, without actuating the actuators, they load the pistons 22,22' axially away from the plate group 25,25', thereby disengaging the corresponding clutches 3,3'.

[0046] If pump 10 is shut off, the pressure in hydraulic chambers 12, 12' drops, and the hydraulic fluid flows back to reservoir 8 via line 17 and return element 13. Especially Figure 4AAs can be seen, in the installed state of the clutch assembly 2, the reservoir 8 has a downwardly tapering region 37, in which the exit opening 14 of the return element 13 is arranged. The horizontal cross-sectional area in this lower region 37 of the housing space 8 is smaller than the horizontal cross-sectional area in the upper region 38 of the housing space. In the installed state, the exit opening 14 of the return element is located at least 10 mm, preferably at least 20 mm below the hydraulic fluid filling level F. Furthermore, the exit opening 14 is oriented in the direction of the opposing impact wall 16, thereby stopping the outflowing hydraulic fluid. The suction region 39 of the hydraulic pump 10 is located at the lowest point of the hydraulic system, thereby ensuring reliable hydraulic pumping even when the vehicle is tilted. The volume of hydraulic fluid in the reservoir 8 can be less than 400 ml and greater than 200 ml.

[0047] In the current embodiment, the baffle 11 is arranged in the upper section of the return element 13, particularly near or within the upper housing section, to the supply section 17 of the baffle 11 or the adjustment unit 20, 20'. The opening diameter of the baffle 11 is significantly smaller than the inner diameter of the return element 13 or its exit opening 14, for example, less than one-sixth of the inner diameter. The flow velocity of the hydraulic fluid through the subsequent return element 13 can be less than 30 m / s, wherein the pressure drop between the inlet and outlet openings of the return element can be less than 5 bar.

[0048] exist Figure 5 The image shows a clutch assembly 2 according to the invention in a modified embodiment, which corresponds to the embodiment according to [the original text]. Figures 4A to 4C The implementation method. In this regard, reference is made to the above description in terms of commonalities, wherein the same or corresponding details are given the same reference numerals.

[0049] according to Figure 5 One feature of this embodiment is that the return element 13 is designed to be relatively short and extends into the upper region 38 of the reservoir 8. Here, the exit opening 14 points in the direction of the impact wall 16 and is arranged at a small distance from the impact wall, which may be, for example, less than 5 mm. The baffle 11 can be arranged accordingly in the lower section of the return element 13, and in particular in a hole at the free end of the return element. In this embodiment, hydraulic fluid flows through the channel 41 of the return element 13 to the baffle 11, and flows through the baffle against the impact wall 16 to the unpressurized reservoir 8 at a high flow rate. All remaining details correspond to the following... Figures 4A to 4C The implementation scheme is described herein.

[0050] exist Figure 6AThe image shows a clutch assembly 2 according to the invention in another modified embodiment, which corresponds to the embodiment according to [the original text]. Figures 4A to 4C or Figure 5 The implementation method. In this regard, reference is made to the above description in terms of commonalities, wherein the same or corresponding details are given the same reference numerals.

[0051] The basic shape of the reflux element 13 is the same as that in Figure 5 The basic shape is designed similarly, meaning that the return element 13 also flows into the upper region 38 of the reservoir 8. According to... Figure 6A Another feature of the implementation scheme is that the shielding element 11 is arranged in the upper section of the return element 13, and the return element 13 (which is in Figure 6B (As shown in detail) It has a lateral exit opening 14. The axis of the lateral opening extends perpendicularly to, and is not restricted by, the longitudinal axis of the return element 13. The free end of the return element 13 is closed by means of a closure 40, which is disposed in the hole on the end side of the return element. In this embodiment, the hydraulic fluid exiting from the baffle 11 impacts the closure 40 at a higher flow velocity so that it then flows out through the lateral opening 14 at a lower flow velocity. Here, the oil flow from the return element 13 to the baffle 11 is guided in a controlled manner through the lateral discharge hole into the housing space, where the oil is allowed to settle and unclog. All remaining details correspond to the following: Figure 3 The implementation plan is described herein.

[0052] The advantage of the clutch assembly shown in the above figure is that it reduces the tendency of the hydraulic fluid to foam, thereby keeping the hydraulic pressure at least to a maximum extent constant while maintaining a constant drive pump 10. This allows for precise quantification of the operating force of the friction clutches 3,3' even during prolonged continuous operation, or the maintenance of the theoretical torque to be transmitted without pressure drop. Overall, the clutch assembly 2 thus provides rapid, precise, and targeted torque adjustment at the relevant drive system and correspondingly higher driving stability, especially during prolonged clutch operation.

[0053] List of reference numerals

[0054] 2 Clutch Assembly

[0055] 3 Friction Clutch

[0056] 4. Clutch input components

[0057] 5. Clutch output components

[0058] 6 actuator assembly

[0059] 7. Shell

[0060] 8. Shell space

[0061] 9 Hydraulic fluid

[0062] 10 hydraulic pumps

[0063] 11 shielding parts

[0064] 12 hydraulic chambers

[0065] 13 Reflux Components

[0066] 14. Leave the opening

[0067] 15 motors

[0068] 16 Impact Wall

[0069] Route 17

[0070] 18 filters

[0071] 19 filters

[0072] 20 piston cylinder unit

[0073] Route 21

[0074] 22,22' pistons

[0075] 23,23' Manipulation Link

[0076] 24,24' spring

[0077] 25 input axes

[0078] 26 connecting elements

[0079] 27 drive pinion

[0080] 28 Supporting devices

[0081] 29 crown gears

[0082] 30 intermediate shaft

[0083] 32 Support devices

[0084] 33,33' axis section

[0085] 34, 34' support devices

[0086] 35,35' thin film group

[0087] 36, 36' Axial Bearings

[0088] 37 Shell Area

[0089] 38 shell area

[0090] 39 suction areas

[0091] 40 closure

[0092] 41 channels

[0093] Axis A

[0094] D diameter

[0095] F Fill Level

[0096] n rotation speed

[0097] P pressure

[0098] t time

Claims

1. A clutch assembly for a drive system of a motor vehicle, comprising: At least one controllable friction clutch (3,3') for transmitting variable torque between a clutch input component (4,4') and a clutch output component (5,5'); A hydraulic actuator assembly (6) for operating the friction clutch (3, 3'), wherein the actuator assembly (6) has a hydraulic pump (10), a hydraulic chamber (12, 12') hydraulically connected to the hydraulic pump (10), and a return element (13) with a shield (11), wherein hydraulic fluid can flow from the hydraulic chamber (12, 12') into the housing space (8) via the return element, wherein the hydraulic fluid (9) defines the fill level (F) in the housing space (8) in a static state; The feature is that, in a static state, the exit opening (14) of the return element (13) is located below the filling level (F) of the hydraulic fluid (9); The reflux element (13) has a channel (41) and the reflux element (13) has a lateral exit opening (14) that branches laterally from the channel.

2. The clutch assembly according to claim 1, Its features are, The controllable friction clutch (3,3') is provided with a lubricant for lubricating and / or cooling the friction clutch (3,3'), wherein the lubricant of the friction clutch (3,3') and the hydraulic fluid (9) of the actuator assembly (6) are different and hydraulically separated from each other.

3. The clutch assembly according to claim 1, Its features are, The exit opening (14) of the return element (13) is located in the lower region (37) of the housing space (8) and / or at least 10 mm below the filling level (F) of the hydraulic fluid (9).

4. The clutch assembly according to claim 1, Its features are, The flow velocity in the return element (13) behind the shield (11) is less than or equal to 30 m / s, wherein the flow velocity in the region of the shield (11) is greater than 60 m / s.

5. The clutch assembly according to any one of claims 1 to 3, Its features are, The pressure drop in the return element (13) between the shield (11) and the exit opening (14) is less than 5 bar.

6. The clutch assembly according to any one of claims 1 to 3, Its features are, In a static state, the volume of the hydraulic fluid (9) in the housing space (8) is less than 400 ml and greater than 200 ml.

7. The clutch assembly according to any one of claims 1 to 3, Its features are, During operation, the hydraulic pump (10) delivers the hydraulic fluid (9) to the adjustment unit (20,20') of the friction clutch (3,3') to load the friction clutch (3,3') in the closing direction, and in the non-operational state, the hydraulic fluid can flow from the adjustment unit (20,20') back into the housing space (8) to open the friction clutch (3,3').

8. The clutch assembly according to any one of claims 1 to 3, Its features are, The return element (13) is designed in a tubular shape, wherein the shield (11) is arranged in the return element (13).

9. The clutch assembly according to any one of claims 1 to 3, Its features are, The channel (41) has a diameter (D41) that is at least three times larger than the minimum opening diameter (D11) of the shield (11).

10. The clutch assembly according to claim 9, Its features are, The diameter is between 3.5 mm and 10 mm.

11. The clutch assembly according to claim 1, Its features are, The shield (11) is arranged in the channel (41) above the lateral exit opening (14), and a closure (40) is provided at the end of the channel (41) below the lateral exit opening (14).

12. The clutch assembly according to claim 11, Its features are, The length of the channel (41) between the shield (11) and the closure (40) is at least twice the diameter (D41) of the channel (41) and the exit opening (14).

13. The clutch assembly according to any one of claims 1 to 3, Its features are, The shield (11) is arranged in the lower section of the return element (13) and is placed in a hole at the free end of the return element (13).

14. The clutch assembly according to any one of claims 1 to 3, Its features are, The hydraulic pump (10) is designed such that it can generate a hydraulic pressure greater than 25 bar.

15. The clutch assembly according to any one of claims 1 to 3, Its features are, In the installed state of the clutch assembly (2), the housing space (8) tapers downward, such that the horizontal cross-sectional area in the lower region (37) of the housing space (8) is smaller than the horizontal cross-sectional area in the upper region (38) of the housing space (8).

16. The clutch assembly according to any one of claims 1 to 3, Its features are, The exit opening (14) of the return element (13) is oriented in the direction of the housing wall (16), wherein the distance between the exit opening (14) and the housing wall (16) is between 1 mm and 5 mm.

17. The clutch assembly according to any one of claims 1 to 3, Its features are, The device is provided with a first controllable friction clutch (3,3') for transmitting a first torque to a first side shaft, and a second controllable friction clutch (3,3') for transmitting a second torque to a second side shaft.

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