Clutch assembly with at least two pressure connectors, drive train with the clutch assembly, and method for compensating for pressure pulsations

Abstract

A clutch assembly (4) is proposed for a drive train (1) of a vehicle with a first and a second shaft (5), (6) which are arranged coaxially to one another in relation to a main axis (100), with a clutch device (10), wherein the first and the second shaft (5), (6) can be connected fixedly to one another for conjoint rotation via the clutch device (10), with a slave cylinder (11), arranged coaxially to the main axis (100), for actuating the clutch device (10), wherein the slave cylinder (11) has an annular housing (14) and an axially movable annular piston (15) which delimit a pressure chamber (16) which wraps around the main axis (100), wherein the annular piston (15) is movement-coupled to the clutch device (10) in order to transmit an actuating force, and wherein the clutch device (10) is arranged with respect to the slave cylinder (11) in an oblique position in relation to the main axis (100), and with a pressure connector (17) for hydraulically connecting a hydraulic activating actuator (19), wherein, in order to reduce pressure pulsations due to the oblique position, the annular housing (14) has at least two pressure connector openings (23), (24) which lie diametrically opposite one another and are each flow-connected via a fluid path (25), (26) to the pressure connector (17).

Description

[0001] Clutch arrangement with at least two pressure connections, drive train with the clutch arrangement and method for compensating pressure pulsations

[0002] The invention relates to a clutch arrangement for a drive train of a vehicle having the features of the preamble of claim 1. Furthermore, the invention relates to a drive train with the clutch arrangement and a method for compensating pressure pulsations of the clutch arrangement.

[0003] Concentric slave cylinders (CSC) are typically used in both hybrid and purely electric vehicle drive systems. These serve, for example, to separate the electric motor from the combustion engine or to change gears. Such slave cylinders essentially consist of an annular housing and an annular piston that can be axially displaced within the annular housing. When a master cylinder is actuated, the annular piston acts on a clutch-side release bearing, thus actuating, in particular engaging, the clutch.

[0004] The document DE 10 2020 109 989 A1 discloses a clutch device for a motor vehicle, with a shaft, wherein the shaft extends axially, with a clutch section, wherein the clutch section is arranged coaxially to the shaft and rotates with the shaft, wherein axial and radial forces act on the shaft and / or on the clutch section during rotation of the shaft, wherein at least the radial forces can cause a radial offset of the clutch section and / or a misalignment of the clutch section and / or the shaft, and with a release bearing, wherein the release bearing is axially movable for transmitting an actuating force to the clutch section, wherein the release bearing is guided through the shaft and / or on the shaft in the radial direction to compensate for the axial offset and / or the misalignment.It is an object of the present invention to propose a clutch arrangement which is characterized by high operational reliability, in particular at high speeds.

[0005] This object is achieved by a clutch arrangement having the features of claim 1, a drive train having the features of claim 9 and a method having the features of claim 10. Preferred or advantageous embodiments of the invention emerge from the subclaims, the following description and the attached figures.

[0006] The invention relates to a clutch assembly designed and / or suitable for a drive train of a vehicle, preferably an electric axle. In particular, the clutch assembly serves to interrupt and / or redirect a torque path of the drive train. Preferably, the clutch assembly serves to engage and disengage an electric motor.

[0007] The clutch assembly has a first and a second shaft, which are arranged coaxially with each other with respect to a main axis. The main axis is preferably defined by a rotational axis of the first and / or second shaft. In particular, one shaft can be designed as a drive shaft of a drive motor, and the other shaft can be designed as a transmission shaft of a transmission or as a further drive shaft of another drive motor.

[0008] The clutch arrangement has a clutch device, wherein the first and second shafts are rotatably connected to one another via the clutch device. Preferably, the clutch device is open in the unactuated state, so that the clutch device is closed upon actuation. Alternatively, however, the clutch device can also be closed in the unactuated state, so that the clutch device is opened upon actuation. Preferably, the two shafts are rotatably connected to one another when the clutch device is closed. For example, the clutch device is designed as a positive-locking or friction-locking clutch. In particular, the clutch device is designed as a multi-plate clutch.

[0009] The clutch assembly has a slave cylinder arranged coaxially to the main axis, which is designed and / or suitable for actuating the clutch device. In particular, the slave cylinder serves to transmit an actuating force to the clutch device in order to open or close the clutch device. Preferably, the slave cylinder is designed as a concentric slave cylinder, also known as a "concentric slave cylinder (CSC)." In particular, the concentric slave cylinder is designed as a central release cylinder.

[0010] For this purpose, the slave cylinder essentially comprises an annular housing and an annular piston that is axially movable within the annular housing. The annular piston and the annular housing are preferably arranged coaxially and / or concentrically with respect to the main axis. The annular housing preferably has a central through-opening, in particular a bore, through which at least one of the shafts can pass when the actuating cylinder is installed. The annular piston is preferably rotationally symmetrical with respect to the main axis.

[0011] The annular housing and the annular piston delimit a pressure chamber surrounding the main axis. For this purpose, the annular housing has an annular chamber surrounding the main axis, wherein the annular piston is accommodated in the annular chamber of the annular housing so as to be movable axially with respect to the main axis. The annular chamber is delimited axially with respect to the main axis by the annular piston, so that the pressure chamber is formed between the annular piston and the annular housing. In particular, the annular chamber is open on one side in the axial direction delimited by the annular piston and closed in an axially opposite direction. Preferably, the pressure chamber is filled and / or can be filled with a hydraulic operating medium. The operating medium can be a hydraulic fluid, in particular a hydraulic oil. The annular piston is motion-coupled to the coupling device for transmitting an actuating force.In particular, the clutch device comprises a first clutch section connected to the first shaft in a rotationally fixed manner and a second clutch section connected to the second shaft in a rotationally fixed manner. The two clutch sections are connected to one another in a rotationally fixed manner when closed. In principle, the annular piston can be connected directly to one of the two clutch sections. However, the annular piston is preferably connected to one of the clutch sections via a transmission device.

[0012] The clutch device is arranged at an angle to the slave cylinder with respect to the main axis. In particular, the angle is formed by an unwanted angle of inclination of the clutch device. The unwanted angle of inclination can be caused by axial and / or radial forces during operation of the drive train. In particular, the unwanted angle of inclination can arise due to geometric deviations and / or manufacturing tolerances of the individual components and / or due to the centrifugal forces acting during operation. Alternatively, however, the angle of inclination can also be formed by a required angle of inclination of the clutch device. For example, the angle of inclination can be more than + / - 0.1 degrees, preferably more than + / - 0.5 degrees, in particular more than + / - 1 degree relative to the main axis.In principle, the coupling device, preferably at least one of the coupling sections, can be mounted with the required misalignment and / or exhibit the unwanted misalignment. Alternatively, however, one of the two shafts can also be mounted with the required misalignment and / or exhibit the unwanted misalignment.

[0013] The clutch arrangement has a pressure connection which is designed and / or suitable for the hydraulic connection of the slave cylinder. In particular, the slave cylinder is connected and / or connectable to a hydraulic actuation actuator via the pressure connection. When the slave cylinder is actuated, an actuation volume flow is generated by the actuation actuator, which flows via the pressure connection into the pressure chamber in order to generate or increase an actuation pressure in the pressure chamber. In particular, an actuation force resulting from the actuation pressure is transmitted to the annular piston, so that the latter is axially disengaged. Particularly preferably, the hydraulic actuation actuator is connected to the pressure connection via a pressure line. In principle, the pressure connection can be arranged on the slave cylinder, in particular the annular housing.Alternatively, the pressure connection can also be arranged on an ambient geometry of the slave cylinder.

[0014] Within the scope of the invention, it is proposed that the annular housing, in order to reduce pressure pulsations caused by the misalignment, have at least two diametrically opposed pressure connection openings which are each fluidically connected to the pressure connection via a fluid path. In particular, “diametrically opposed” means that the two pressure connection openings are arranged offset from one another by 180 degrees in the circumferential direction. The pressure connection openings can each be arranged on a radial outer side of the annular housing and / or open radially into the pressure chamber. For this purpose, the pressure connection openings can be formed by a bore or the like made radially in the annular housing. The fluid paths can be designed as two separate and / or fluidically separated lines, channels or the like.Particularly preferably, a first flow path from the pressure chamber runs via a first pressure connection opening and a first fluid path to the pressure connection and a second flow path from the pressure chamber runs via a second pressure connection opening and a second fluid path to the pressure connection.

[0015] During operation, the misalignment of the coupling device leads to a circulating pressure or volume excitation, whereby a pressure or volume peak and a pressure or volume sink are formed in the pressure chamber. A volume peak is understood to be the excitation point in the pressure chamber at which the annular piston displaces the most fluid volume. Correspondingly, a volume sink is understood to be the excitation point in the pressure chamber at which the annular piston displaces the smallest fluid volume. Accordingly, a pressure peak means a sudden increase in the fluid pressure at the excitation point and a pressure sink means a sudden drop in the fluid pressure at the excitation point. With circulating excitation, each excitation point is arranged at the pressure connection openings once per revolution. In particular, the at least two pressure connection openings are arranged in such a way that a pressure or volume transmitted via the pressure connection openings always results.Volume peak, a corresponding pressure or volume sink is simultaneously transferred from the pressure chamber towards the pressure connection, so that these cancel each other out at the pressure connection.

[0016] The invention is based on the finding that when the clutch device is misaligned, the annular piston performs a wobbling motion, which is transmitted to the fluid column between the pressure chamber and the actuating actuator and can lead to pressure oscillations in the fluid column. This effect is typically speed-dependent and can occur, for example, at speeds above 9000 rpm. The pressure oscillations can damage the components of the clutch assembly, particularly the slave cylinder. Furthermore, diagnostics and / or functions that are intended to react based on pressure can be erroneously triggered by the pressure oscillations.

[0017] The invention is based on the idea of ​​interconnecting the pressure peak and the pressure sink in a hydraulic sense such that the pressure peak and the pressure sink cancel each other out. The at least two opposing pressure connection openings allow the pressure oscillations to be reduced by the pressure peak and the pressure sink meeting at the pressure connection and thus compensating each other. This results in a significant reduction, ideally a complete elimination, of the pressure oscillation observed by the actuator. Simply put, a line routing is proposed that cancels out the pressure excitation. By providing two pressure connection openings, a particularly cost-effective and space-saving concept for reducing pressure pulsations is proposed.

[0018] In a specific embodiment, it is proposed that the pressure connection be arranged centrally in the circumferential direction between the at least two or exactly two pressure connection openings. In particular, the at least two pressure connection openings are thus arranged equidistant from the pressure connection. This ensures that the pressure peak and the pressure drop, or a resulting pressure pulse, meet simultaneously at the pressure connection.

[0019] In a further specific embodiment, the pressure connection is arranged on a top side in a designated installation position of the slave cylinder. Alternatively or optionally, the pressure connection is arranged in a 12 o'clock position in a designated installation position of the slave cylinder, particularly relative to the main axis. The radial connection of the pressure connection on the top side of the annular housing thus ensures that the annular space does not form the highest point of the actuation system, thereby ensuring at least partial or complete filling of the pressure chamber with fluid.

[0020] In one specific implementation, the two pressure connection openings are each offset by 90 degrees to the pressure connection. Alternatively, or optionally in addition, one pressure connection opening is arranged in a 3 o'clock position and the other pressure connection opening is arranged in a 9 o'clock position. In other words, the annular housing has exactly two pressure connection openings, which are offset by 180 degrees on the annular housing, with the pressure connection being arranged centrally between the two pressure connection openings in the circumferential direction. This ensures that the excitation point of the pressure or volume peak and the excitation point of the pressure or volume sink occur simultaneously at the pressure connection openings exactly twice per revolution. In a further development, the pressure connection openings are fluidically connected to one another via an additional connecting section.In particular, the two pressure connection openings are, on the one hand, directly fluidically connected to the pressure connection via the respective fluid path, and, on the other hand, directly fluidically connected to one another via the connecting path. The connecting path can be formed as a separate line, channel, or the like. Alternatively, however, the fluid paths and the connecting path can also be formed by a common channel, in particular an annular channel, into which the two pressure connection openings and the pressure connection open. For example, the annular channel is arranged coaxially and / or concentrically with respect to the main axis to the annular housing or is formed in the annular housing. This enables particularly simple production and a compact design of the annular housing.

[0021] In a further specific embodiment, the clutch arrangement comprises a housing section, wherein the annular housing is received in the housing section. The housing section can be formed by a clutch housing, a transmission housing, or a motor housing. An intermediate pressure chamber extending around the main axis is formed radially between the annular housing and the housing section, wherein the fluid paths and the connecting path are formed by the intermediate pressure chamber. The pressure connection can be arranged on a radial outer side of the housing section and / or open radially into the intermediate pressure chamber. For this purpose, the pressure connection can be formed or co-formed by a bore or the like radially introduced into the housing section. The intermediate pressure chamber is preferably delimited in the radial direction on the one hand by an inner circumference of the housing section and on the other hand by an outer circumference of the annular housing.Preferably, the intermediate pressure chamber is fluidically connected, on the one hand, to the pressure chamber via the pressure connection openings formed in the annular housing, and, on the other hand, to the pressure line or the actuating actuator via the pressure connection formed in the housing section. This enables a particularly simple, in particular one-piece, and cost-effective production of the annular housing, while at the same time eliminating the need for separate lines for connecting the pressure connection openings to the pressure connection.

[0022] In a further development, the annular housing has at least or exactly two further diametrically opposed pressure connection openings, which are each connected to the pressure connection via a further fluid path. In particular, the annular housing thus has exactly four pressure connection openings, which are preferably evenly spaced from one another and / or offset by 90 degrees to one another. In principle, however, the annular housing can have any number of pressure connection openings, which are arranged in pairs diametrically opposite one another on the annular housing. As a result, the excitation point of the pressure or volume peak and the excitation point of the pressure or volume sink can occur simultaneously at the pressure connection openings 2n times per revolution, where n corresponds to the number of pressure connection openings.

[0023] In a concrete implementation, the individual fluid paths between the respective pressure connection opening and the pressure connection are geometrically identical. In particular, “geometrically identical” means that the fluid paths each have the same length and the same cross-sectional area. With more than two pressure connection openings, i.e. with 2n pressure connection openings with n>1, the fluid paths are formed by separate, identical lines which directly connect the respective pressure connection opening to the pressure connection. This ensures that the same volume flow always flows through the fluid paths and / or that a pressure drop is always sent from the pressure chamber towards the pressure connection at the same time as a pressure peak.

[0024] A further subject matter of the invention relates to a drive train for a vehicle with the clutch arrangement as already described above. The drive train can be designed as a hybrid or electric drive train. For this purpose, the drive train has at least or exactly one electric drive motor for generating a drive torque, wherein the clutch arrangement is designed and / or suitable for interrupting the drive torque. It can be provided that the electric drive motor forms the only traction motor for the vehicle. Alternatively, the vehicle has further traction motors, for example further electric drive motors and / or an internal combustion engine for generating the drive torque. The electric drive motor can be assigned to a single driven wheel of the vehicle and / or be designed as a single-wheel drive.Alternatively, the electric drive motor is assigned to two driven wheels, preferably a common axle, and / or is designed as a single electric axle. In other embodiments, the electric drive motor can also be assigned to all driven wheels and / or wheels of the vehicle and / or be designed as an all-wheel drive.

[0025] The clutch device is designed to decouple the drive motor in certain driving situations and / or to disconnect a drive torque path, wherein the slave cylinder is designed and / or suitable for actuating the clutch device. The clutch device is preferably designed as a separating clutch, which is designed to disconnect the drive torque path downstream of the electric drive motor. This allows the electric drive motor to rotate without any drive torque being transmitted to the driven wheels. In particular, the clutch device is designed to interrupt a drive torque between the internal combustion engine and the electric motor in the hybrid drive train or to change gears in the electric drive train.

[0026] Another object of the invention relates to a method for compensating pressure pulsations of the clutch arrangement, as already described above, in which, during operation of the clutch arrangement, a pressure or volume peak and a pressure or volume sink are generated in the pressure chamber due to the misalignment of the coupling device. Thus, a pressure pulse resulting from the pressure peak can be transmitted simultaneously to the pressure connection via one pressure connection opening and a pressure pulse resulting from the pressure sink via the other pressure connection opening and can at least partially or completely cancel each other out at the pressure connection. In other words, at the same time as a pressure or volume peak, a pressure or volume sink is always sent from the pressure chamber towards the pressure connection, which meet at the pressure connection and influence each other, in particular compensate for each other.

[0027] Further features, advantages, and effects of the invention will become apparent from the following description of preferred embodiments of the invention. These show:

[0028] Fig. 1 is a schematic representation of a drive train as an embodiment of the invention;

[0029] Fig. 2 is a schematic sectional view of a clutch arrangement of the drive train from Fig. 1;

[0030] Fig. 3 is an axial view of a ring housing of the clutch arrangement in a schematic representation;

[0031] Fig. 4 shows an alternative embodiment of the ring housing in the same representation as in Fig. 3;

[0032] Fig. 5 shows another alternative embodiment of the ring housing in the same representation as in Fig. 3.

[0033] Figure 1 shows a drive train 1 for a vehicle, wherein the drive train 1 comprises a drive motor 2 and a further drive motor 3, which is drive-coupled and / or can be coupled via a clutch arrangement 4. The drive motor 2 and the further drive motor 3 can each be designed as an electric machine. Alternatively, the drive motor 2 can also be designed as an internal combustion engine.

[0034] The clutch assembly 4 is designed as a separating clutch, also called a KO clutch, for interrupting a drive torque between the two drive motors 2, 3. In a closed state of the clutch assembly 4, a first shaft 5, e.g., a crankshaft, of the drive motor 2 is rotationally coupled to a second shaft 6, e.g., a rotor shaft, of the further drive motor 3, and in an open state, they are rotatable relative to each other.

[0035] The drive train 1 also has a transmission device 7, which is connected on the input side to the drive engine 2 or the further drive engine 3 and on the output side to a differential 8, wherein a torque generated by the drive engine 2 and / or the further drive engine 3 is transmitted or translated via the transmission device 7 to the differential 8 and thus to the driven wheels 9 of the vehicle.

[0036] For example, the transmission device 7 can be designed as a dual-clutch transmission.

[0037] As shown in Figure 2, the clutch assembly 4 comprises a clutch device 10 and a concentric slave cylinder 11, abbreviated to CSC, which are arranged coaxially and / or concentrically with the first and / or second shaft 5, 6. For example, the clutch device 4 can be designed as a multi-plate clutch.

[0038] The clutch device 10 has a first and a second clutch section 12, 13, which are rotationally fixedly engaged with one another when the clutch device 10 is closed and are separated or disengaged from one another when the clutch device 10 is open. The first clutch section 12 is rotationally fixedly connected to the first shaft 5, and the second clutch section 13 is rotationally fixedly connected to the second shaft 6. For example, the two clutch sections 12, 13 are each designed as a disc carrier.

[0039] Here, the coupling device 10 can be arranged with an inclination, as schematically indicated in Figure 2, relative to a main axis 100. The main axis 100 is defined by a rotational axis of the first and / or second shafts 5, 6. The reason for the inclination can be, for example, a tilted shaft 5, 6 on which the coupling device 10 is mounted, or a shaft 5, 6 that bends due to transverse forces from gear stages, electric motors, etc.

[0040] The slave cylinder 11 has an annular housing 14 and an annular piston 15 accommodated in the annular housing 14, which is axially movable relative to the annular housing 14 with respect to the main axis 100 between an engaged and a disengaged end position. The annular housing 14 and the annular piston 15 are arranged coaxially and concentrically with respect to the main axis 100. The slave cylinder 11 serves to actuate the clutch device 10, wherein the annular piston 15 is, for this purpose, at least indirectly coupled in terms of movement to the clutch device 10, in particular to the second clutch section 13.

[0041] The annular piston 15 lies radially sealingly within the annular housing 14, such that a pressure chamber 16 is axially delimited or sealed by the annular piston 15. The slave cylinder 11 is hydraulically actuated, wherein the pressure chamber 15 is or will be filled with a hydraulic operating medium, e.g., hydraulic oil, in an operating state. For this purpose, the pressure chamber 16 is connected to a hydraulic actuating actuator 19, e.g., a pump, via a pressure connection 17 and a pressure line 18. The actuating actuator 18 can generate an actuating volume flow which flows along a flow path 101 via the pressure line 18 and the pressure connection 17 into the pressure chamber 16, whereby a pressure in the pressure chamber 16 is increased and an actuating force is applied to the annular piston 15. The ring housing 2 has an inner and an outer cylinder section 20, 21, which delimit the pressure chamber 16 in the radial direction.The two cylinder sections 20, 21 are arranged parallel to each other in the axial direction and connected to each other via an end section 22, wherein the end section 22 defines the pressure chamber 16 in the axial direction. For example, the two cylinder sections 20, 21 and the end section 22 are made from a common section of material.

[0042] In the closed state of the clutch device 10 and / or during rotation of the second shaft 6, the annular piston 15 executes a wobbling movement per revolution due to the misalignment, which is transmitted as excitation into the fluid column and can excite the fluid column or the actuating pressure to pressure oscillations with a frequency corresponding to the clutch speed.

[0043] As shown in Figures 3 and 4, the outer cylinder section 21 of the ring housing 14 has two pressure connection openings 23, 24, which are arranged diametrically opposite one another. In other words, the two pressure connection openings 23, 24 are arranged offset from one another by exactly 180 degrees. The pressure connection 17 is arranged on an upper side, in particular at a 12 o'clock position in an axial view with respect to the main axis 100, centrally between the two pressure connection openings 23, 24. Thus, the two pressure connection openings 23, 24 are each arranged offset at an angle of 90 degrees to the pressure connection opening 23, 24. In particular, in an axial view with respect to the main axis 100, the first pressure connection opening 23 is arranged at a 3 o'clock position and the second pressure connection opening 24 is arranged at a 9 o'clock position.

[0044] The first pressure connection opening 23 is fluidically connected to the pressure connection 17 via a first fluid path 25, and the second pressure connection opening 24 is fluidically connected to the pressure connection 17 via a second fluid path 26. In simplified form, at least two separate fluid paths 25, 26 are led out of the annular pressure chamber 16 in the direction of the pressure connection 17, which are fluidically connected to one another outside the pressure chamber 16 via the pressure connection 17. The two fluid paths 25, 26 have the same geometry, in particular the same length and the same cross-sectional area, up to the junction point or the pressure connection 17. For example, the two fluid paths 25, 26 can be designed as a separate line, channel, or the like.

[0045] Due to the misalignment of the coupling device 4 and the associated wobbling movement of the annular piston 15, a pressure or volume excitation occurs in the pressure chamber 16, whereby a pressure or volume peak 102 and a pressure or volume sink 103 exist in the pressure chamber 16. A pressure or volume peak 102 is understood to be the excitation point in the pressure chamber 16 at which the annular piston 15 displaces the most fluid volume. A pressure or volume sink 103, on the other hand, is understood to be the excitation point in the pressure chamber 16 at which the annular piston 15 displaces the smallest fluid volume. Due to the rotationally symmetrical design of the annular piston 14, the excitation points are always diametrically opposite one another.

[0046] During a rotating excitation, the excitation points of the pressure or volume peak 102 and the pressure or volume sink 103 each move past the pressure connection openings 23, 24 once per revolution. Due to the opposite arrangement of the pressure connection openings 23, 24, a pressure or volume sink 103 is always transmitted from the pressure chamber 16 via the fluid paths 23 to the pressure connection 17 at the same time as a pressure or volume peak 102. The pressure pulses resulting from the pressure or volume peak 102 and the pressure or volume sink 103 meet at the pressure connection 17 and at least partially cancel each other out. This brings about a significant reduction in the pressure oscillation at the pressure connection 17 and, ideally, a compensation for the pressure oscillation arriving at the actuating actuator 19.

[0047] As shown in Figure 4, the two pressure connection openings 23, 24 can be fluidically connected to one another via a connecting section 27. For this purpose, the annular housing 14 can be accommodated in a housing section 28, only indicated schematically, wherein an intermediate pressure chamber 29 is formed radially between the annular housing 14 and the housing section 28, which intermediate pressure chamber 29 surrounds the main axis 100 and is fluidly connected to the actuating actuator 19 via the pressure connection 17 on the one hand and to the pressure chamber 16 via the two pressure connection openings 23, 24 on the other. The pressure connection 17 is arranged on an upper side of the housing section 28, wherein the two fluid paths 25, 26 and the connecting section 27 are formed by the intermediate pressure chamber 29.For example, the intermediate pressure chamber 29 can be designed as an annular chamber surrounding the main axis 100, into which the two pressure connection openings 23, 24 and the pressure connection 17 open. For example, the housing section 27 is designed as a housing of the drive motor 2, the further drive motor 3, or the transmission 7, as described in Figure 1.

[0048] As shown in Figure 5, the outer cylinder section 21 of the annular housing 14 has two additional pressure connection openings 30, 31, which are arranged diametrically opposite one another. In other words, the two additional pressure connection openings 30, 31 are arranged offset from one another by exactly 180 degrees. The pressure connection openings 23, 24, 30, 31 are each arranged offset from one another at an angle of 90 degrees, with the pressure connection 17 still being arranged on the upper side, in particular at a 12 o'clock position in an axial view relative to the main axis 100.

[0049] The third pressure connection opening 30 is fluidically connected to the pressure connection 17 via a third fluid path 32, and the fourth pressure connection opening 31 is fluidly connected to the pressure connection 17 via a fourth fluid path 33. In simplified form, four separate fluid paths 25, 26, 32, 33 lead from the annular pressure chamber 16 in the direction of the pressure connection 17, which are fluidically connected to one another outside the pressure chamber 16 via the pressure connection 17. The fluid paths 25, 26, 32, 33 have the same geometry up to the junction point or the pressure connection 17, in particular the same length and the same cross-sectional area. For example, the four fluid paths 25, 26, 32, 33 can each be designed as a separate line, channel, or the like. The two additional pressure connection openings 30, 31 can further reduce the pressure oscillations.

[0050] List of reference symbols

[0051] Powertrain

[0052] drive machine additional drive machine

[0053] Clutch arrangement first shaft second shaft

[0054] Gearbox

[0055] differential

[0056] Wheels

[0057] Coupling device

[0058] Slave cylinder first clutch section second clutch section ring housing

[0059] Ring piston

[0060] Print room

[0061] Pressure connection

[0062] pressure line

[0063] Actuator inner cylinder section outer cylinder section end section first pressure connection opening second pressure connection opening first fluid path second fluid path

[0064] Connecting section Housing section Intermediate pressure chamber Third pressure connection opening Fourth pressure connection opening Third fluid section Fourth fluid section Main axis Flow path Pressure peak Pressure sink

Claims

Patent claims 1 . Clutch arrangement (4) for a drive train (1) of a vehicle, - with a first and a second shaft (5, 6) which are arranged coaxially with respect to a main axis (100), - with a coupling device (10), wherein the first and second shafts (5, 6) can be connected to one another in a rotationally fixed manner via the coupling device (10), - with a slave cylinder (11) arranged coaxially to the main axis (100) for actuating the clutch device (10), wherein the slave cylinder (11) has an annular housing (14) and an axially movable annular piston (15) which delimit a pressure chamber (16) surrounding the main axis (100), wherein the annular piston (15) is coupled in motion to the clutch device (10) for transmitting an actuating force, and wherein the clutch device (10) is arranged in an oblique position relative to the slave cylinder (11) with respect to the main axis (100), - with a pressure connection (17) for the hydraulic connection of a hydraulic actuating actuator (19), characterized in that the annular housing (14) has at least two diametrically opposed pressure connection openings (23, 24) for reducing pressure pulsations caused by the tilted position, which are each fluidically connected to the pressure connection (17) via a fluid path (25, 26).

2. Coupling arrangement (4) according to claim 1, characterized in that the pressure connection (17) is arranged centrally in the circumferential direction between the two pressure connection openings (23, 24).

3. Clutch arrangement (4) according to claim 1 or 2, characterized in that the pressure connection (23, 24) is arranged on an upper side and / or in a 12 o'clock position in a proper installation position of the slave cylinder (11).

4. Coupling arrangement (4) according to one of the preceding claims, characterized in that the two pressure connection openings (23, 24) are each offset by 90 degrees to the pressure connection (17) and / or arranged in a 3 o'clock and a 9 o'clock position.

5. Coupling arrangement (4) according to one of the preceding claims, characterized in that the two pressure connection openings (23, 24) are fluidically connected to one another via an additional connecting section (27).

6. Coupling arrangement (4) according to claim 5, characterized in that the annular housing (14) is accommodated in a housing section (28), wherein an intermediate pressure chamber (29) running around the main axis (100) is formed radially between the annular housing (14) and the housing section (28), wherein the fluid paths (25, 26) and the connecting path (27) are formed by the intermediate pressure chamber (29).

7. Coupling arrangement (4) according to one of the preceding claims, characterized in that the annular housing (14) has at least two further diametrically opposed pressure connection openings (30, 31), which are each connected to the pressure connection (17) via a further fluid path (32, 33).

8. Coupling arrangement (4) according to one of the preceding claims, characterized in that the individual fluid paths (25, 26, 30, 31) between the respective pressure connection opening (23, 24, 32, 33) and the pressure connection (17) are geometrically identical.

9. Drive train (1) for a vehicle, with at least one electric drive machine (2, 3) for generating a drive torque and with the clutch arrangement (4) according to one of the preceding claims.

10. Method for compensating pressure pulsations of a clutch arrangement (4) according to one of the preceding claims, in which, during operation of the clutch arrangement (4), a pressure peak (102) and a pressure dip (103) are generated in the pressure chamber (16) due to the misalignment of the clutch device (10), wherein at the same time a pressure pulse resulting from the pressure peak (102) A pressure pulse is transmitted via one pressure connection opening (23, 24) and a pressure pulse resulting from the pressure sink (103) is transmitted via the other pressure connection opening (23, 24) to the pressure connection (17) and is at least partially canceled out at the pressure connection (17).

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