A friction clutch with radially partitioned output pistons

Abstract

The application discloses a friction clutch with a radial partition output piston and belongs to the technical field of power transmission.The application solves the technical problem of complex structure of the existing wet multi-plate friction clutch in the occasion of only needing to transmit stepped torque.Through a convex ring and a partition concave ring, a cavity between the piston and the oil cylinder is divided into three annular cavities, the first annular cavity is arranged on the upper side of the convex ring, the second annular cavity is arranged on the lower side of the convex ring, the third annular cavity is arranged on the left side of the convex ring, a first oil inlet oil passage in communication with the first annular cavity is arranged in the oil cylinder, a second oil inlet oil passage in communication with the second annular cavity is arranged in the oil cylinder, an oil inlet damping screw plug is arranged in the second oil inlet oil passage, and an installation gap arranged between the convex ring and the partition concave ring generates liquid resistance to working oil flowing in the installation gap; an oil conveying oil passage is arranged in an input shaft, a two-position three-way electromagnetic valve is arranged on the oil conveying oil passage, and the oil conveying oil passage is in communication with the first oil inlet oil passage and the second oil inlet oil passage.The application is used for clutch design and has the advantages of simple structure.

Description

Technical Field

[0001] This invention relates to a friction clutch with a radially partitioned output piston, belonging to the field of power transmission technology. Background Technology

[0002] A wet multi-plate friction clutch uses a hydraulic piston to press the friction plates together, and transmits the host power (torque, speed) through the friction torque of the friction plates. The torque T that a wet multi-plate friction clutch can transmit can be expressed by the following formula:

[0003] T=Z*F*f* Rv(1)

[0004] T - Transmitted torque, Z - Number of friction pairs in the friction plate group, f - Friction coefficient of the friction pair, Rv - Equivalent friction radius of the friction pair, F - Piston clamping force; F=P*S, P - Piston pressure, S - Piston area

[0005] The torque T can be further simplified and expressed by the following formula:

[0006] T = k * P * S (2), k = Z * f * Rv

[0007] According to formula (2), when k is approximately constant, the torque T transmitted by the wet multi-plate friction clutch is positively correlated with the piston pressure P and the piston area S.

[0008] In a traditional wet multi-plate friction clutch, the piston area S remains constant. By changing the piston pressure P through an external pressure control valve group, the torque T transmitted by the wet multi-plate friction clutch is changed, thereby enabling the wet multi-plate friction clutch to transmit rated host power at low torque and high torque.

[0009] In simple applications where only a wet multi-plate friction clutch is needed to transmit stepped torque, external pressure control valves increase the complexity of the clutch control system.

[0010] In summary, existing wet multi-plate friction clutches present technical challenges due to their complex structure in applications where only stepped torque transmission is required. Summary of the Invention

[0011] The present invention aims to solve the technical problem of the complex structure of existing wet multi-plate friction clutches in situations where only stepped torque needs to be transmitted. Therefore, a friction clutch with a radially partitioned output piston is proposed, which includes an input shaft, a hydraulic cylinder, a piston, a convex ring, a partitioned concave ring, an oil inlet damping screw plug, and a two-position three-way solenoid valve.

[0012] A convex ring is disposed on the side wall of the piston, and a partitioned concave ring is disposed on the side wall of the cylinder. The shapes of the convex ring and the partitioned concave ring are matched, and the cavity between the piston and the cylinder is divided into three annular cavities by the convex ring and the partitioned concave ring, namely the first annular cavity, the second annular cavity and the third annular cavity. The first annular cavity is disposed on the upper side of the convex ring, the second annular cavity is disposed on the lower side of the convex ring, and the third annular cavity is disposed on the left side of the convex ring. A first oil inlet passage communicating with the first annular cavity is disposed in the cylinder, and a second oil inlet passage communicating with the second annular cavity is disposed in the cylinder. An oil inlet damping screw plug is installed in the second oil inlet passage. An installation gap is provided between the convex ring and the partitioned concave ring, and the installation gap generates hydraulic resistance to the working oil flowing inside.

[0013] The input shaft is equipped with an oil supply circuit, and a two-position three-way solenoid valve is installed on the oil supply circuit. The oil supply circuit is connected to the first oil inlet circuit and the second oil inlet circuit respectively.

[0014] As another improvement of the present invention, it also includes a friction plate assembly, an output toothed ring, an end plate, a friction plate seat, a stop ring, and a return spring;

[0015] The friction plate assembly is installed on the right side of the convex ring, the output toothed ring is installed on the upper side of the friction plate assembly, the end plate is installed on the right side of the friction plate assembly, the friction plate seat is set between the input shaft and the end plate, the stop ring is installed on the lower side of the friction plate assembly, and the return spring is embedded in the stop ring.

[0016] The return spring is used to push the piston back to the disengaged position when the cylinder pressure drops.

[0017] As another improvement of the present invention, the oil supply circuit includes an axial oil hole and a radial oil hole, and a total oil inlet is provided in the oil cylinder. The axial oil hole, the radial oil hole and the total oil inlet are connected in sequence, and the total oil inlet is connected to the first oil inlet circuit and the second oil inlet circuit respectively.

[0018] As another improvement of the present invention, the two-position three-way solenoid valve has a P port, an A port and a T port;

[0019] Port P connects to the external oil supply system, port A connects to the oil delivery circuit, and port T is the return port.

[0020] As another improvement of the present invention, when the two-position three-way solenoid valve is energized, external pressure oil quickly enters the first annular cavity through the oil supply line and the first oil inlet line.

[0021] The second and third annular cavities are filled with oil for a delayed period due to the hydraulic resistance of the oil inlet damping plug and the installation gap.

[0022] As another improvement of the present invention, when the two-position three-way solenoid valve is de-energized, the oil in the cylinder is discharged through the oil supply line.

[0023] The piston is pushed back to the disengaged position by the return spring, and the friction plate assembly is released.

[0024] As another improvement of the present invention, the diameter of the damping hole of the oil inlet damping screw plug is adjustable, which is used to control the oil filling time of the second annular cavity.

[0025] As another improvement of the present invention, the ratio of the area of ​​the first annular cavity to the total hydraulic area of ​​the piston is adjustable, which is used to set the torque magnitude of the flexible connection stage.

[0026] As another improvement of the present invention, during the oil filling process, the pressures of the first annular cavity, the second annular cavity and the third annular cavity reach the system oil supply pressure in sequence, forming a time difference in pressure establishment.

[0027] As another improvement of the present invention, during the clutch engagement process, the clamping force on the piston increases in a stepwise manner, corresponding to a stepwise change in the clutch output torque.

[0028] The beneficial effects of this invention are:

[0029] 1. The present invention provides a friction clutch with a radially partitioned output piston. By radially partitioning the piston and setting an internal flow channel, the structure is compact and reasonable, enabling the clutch to automatically form a stepped clamping force at different stages. Externally, only a two-position three-way solenoid valve is needed to control the oil circuit, and no pressure regulation function is required.

[0030] 2. This invention discloses a friction clutch with a radially partitioned output piston. Utilizing the characteristics of rapid oil filling in the first annular cavity and delayed oil filling in the second and third annular cavities, the piston clamping force increases in a stepped manner, correspondingly resulting in a stepped change in the clutch's transmitted torque. "During the clutch's low-torque output phase, the host machine can accelerate the load under low load, i.e., a soft-contact clutch. During the clutch's high-torque output phase, the host machine can continuously operate the load under high load for extended periods." This effect is entirely achieved through the piston partitioning and damping structure, requiring no external pressure changes.

[0031] 3. By changing the diameter of the damping hole of the oil inlet damping screw, the oil filling delay time of the second and third annular chambers can be adjusted, thereby controlling the duration of the low torque stage.

[0032] By adjusting the proportion of the area of ​​the first annular cavity in the total effective hydraulic area of ​​the piston, the ratio of the clamping force to the full clamping force in the low torque stage can be changed, thereby matching the torque required by the soft contact plate of the host machine.

[0033] The two adjustment methods described above can be used to flexibly adjust the torque of different flexible connectors. Attached Figure Description

[0034] Figure 1 This is a schematic diagram of the disengaged state of a friction clutch with a radially partitioned output piston according to the present invention.

[0035] Figure 2 This is a schematic diagram showing the first annular cavity being filled with oil during the initial stage of the discharge process.

[0036] Figure 3 This is a schematic diagram showing the filling of the first, second, and third annular cavities with oil after the discharge process is completed.

[0037] Figure 4 This is a schematic diagram of the oil draining process in the first, second, and third annular cavities.

[0038] Figure 5 These are the pressure variation curves of the first annular cavity, the second annular cavity, and the third annular cavity over time.

[0039] Figure 6 It is a curve showing the change in the force of the piston pressing against the friction plate assembly over time. Detailed Implementation

[0040] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention. In the description of the present invention, it should be noted that the positional relationships indicated by terms such as "upper," "lower," "first," and "second" are only based on the positional relationships shown in the accompanying drawings and are only for the convenience of describing the present invention, and are not intended to indicate or imply that the referred components have a specific orientation, or are constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention.

[0041] Specific implementation method one: Combining Figures 1 to 4 This embodiment describes a friction clutch with a radially partitioned output piston, which includes an input shaft 100, a cylinder 300, a piston 400, a convex ring 420, a partitioned concave ring 310, an oil inlet damping screw plug 350, and a two-position three-way solenoid valve 900.

[0042] A convex ring 420 is disposed on the side wall of the piston 400, and a partitioned concave ring 310 is disposed on the side wall of the cylinder 300. The shapes of the convex ring 420 and the partitioned concave ring 310 are matched, and the cavity between the piston 400 and the cylinder 300 is divided into three annular cavities by the convex ring 420 and the partitioned concave ring 310, namely the first annular cavity B1, the second annular cavity B2 and the third annular cavity B3. The first annular cavity B1 is disposed on the upper side of the convex ring 420, the second annular cavity B2 is disposed on the lower side of the convex ring 420, and the third annular cavity B3 is disposed on the left side of the convex ring 420. A first oil inlet passage 340 communicating with the first annular cavity B1 is provided in the cylinder 300, and a second oil inlet passage 330 communicating with the second annular cavity B2 is provided in the cylinder 300. An oil inlet damping screw plug 350 is installed in the second oil inlet passage 330. An installation gap is provided between the convex ring 420 and the partitioned concave ring 310, and the installation gap generates hydraulic resistance to the working oil flowing inside.

[0043] An oil supply circuit is provided inside the input shaft 100. A two-position three-way solenoid valve 900 is installed on the oil supply circuit. The oil supply circuit is connected to the first oil inlet circuit 340 and the second oil inlet circuit 330 respectively.

[0044] The cylinder partition concave ring 310 and piston convex ring 420 form two sets of sliding clearance fits, which will generate hydraulic resistance to the flowing working oil. The diameter of the oil inlet hole 340 of the first annular cavity B1 is much larger than the damping hole diameter of the oil inlet damping screw plug 350 of the second annular cavity B2. The oil inlet damping screw plug 350 of the second annular cavity B2 is installed inside the oil inlet hole 330 of the second annular cavity B2. The cylinder radial main oil inlet hole 320 connects the oil inlet hole 330 of the second annular cavity B2 and the oil inlet hole 340 of the first annular cavity B1.

[0045] The input shaft 100 has an axial oil hole 120 and a radial oil hole 140, which are interconnected with the cylinder radial main oil inlet 320. The A port of the two-position three-way solenoid valve 900 is connected to the axial oil hole 120. The P port of the two-position three-way solenoid valve 900 receives pressurized oil from an external oil supply system, typically at 2.0 MPa. When the two-position three-way solenoid valve 900 is de-energized, the A port connects to the T port, and the pressure in the cylinder 300 matches the pressure at the T port. The piston 400 is pushed back to the fully disengaged position by the return spring 60, and the friction plate assembly 10 is completely released.

[0046] When the two-position three-way solenoid valve 900 is energized, port P and port A are connected. External pressure oil rapidly fills the first annular cavity B1 of the piston 400 along the axial oil hole 120, radial oil hole 140, radial main oil inlet 320, and first annular cavity B1 oil inlet 340. Since the first annular cavity B1 is located on the outermost radial side of the piston 400, under the action of centrifugal force, the lubricating oil entering the first annular cavity B1 tends to flow towards the outer diameter of the piston 400.

[0047] The gap between the cylinder partition concave ring 310 and the piston partition convex ring 420 creates hydraulic resistance to the flowing working oil, preventing the third annular cavity B3 from filling with working oil synchronously with the first annular cavity B1. The damping orifice diameter of the oil inlet damping plug 350 in the second annular cavity B2 is much smaller than the diameter of the oil inlet orifice 340 in the first annular cavity B1.

[0048] The second annular cavity B2 also cannot be filled with working oil synchronously with the first annular cavity B1. Therefore, the clamping force on the piston is F1 = the pressure oil provided by the external oil supply system * the area of ​​the first annular cavity B1 = 2SB1.

[0049] Figure 3 In Figure 2 Based on this, after a period of time, the pressurized oil supplied by the external oil supply system fills the second annular cavity B2 through the oil inlet 330 and the oil inlet damping screw plug 350. Simultaneously, the oil in the second annular cavity B2 fills the third annular cavity B3 through the gap between the cylinder partition concave ring 310 and the piston partition convex ring 420. The clamping force F on the piston is:

[0050] F = F1 + F2 + F3 = 2 * (SB1 + SB2 + SB3).

[0051] Figure 4 When the two-position three-way solenoid valve 900 is de-energized, port P is cut off, and ports A and T are connected. The oil stored in cylinder 300 is discharged through the radial main oil inlet 320, radial oil hole 140, axial oil hole 120, and port T of the two-position three-way solenoid valve 900. The pressure in cylinder 300 is the same as the pressure at port T, dropping to 0. Piston 400 is pushed back to the fully disengaged position by return spring 60, friction plate assembly 10 is completely relaxed, the clamping force on friction plate assembly 10 is 0, and the transmittable torque also drops to close to 0.

[0052] Specific Implementation Method Two: Combining Figures 1 to 4 This embodiment differs from specific embodiment one in that it also includes a friction plate assembly 10, an output gear ring 20, an end plate 30, a friction plate seat 40, a stop ring 50, and a return spring 60. The friction plate assembly 10 is mounted on the right side of the convex ring 420, the output gear ring 20 is mounted on the upper side of the friction plate assembly 10, the end plate 30 is mounted on the right side of the friction plate assembly 10, the friction plate seat 40 is positioned between the input shaft 100 and the end plate 30, the stop ring 50 is mounted on the lower side of the friction plate assembly 10, and the return spring 60 is embedded within the stop ring 50. The return spring 60 is used to push the piston 400 back to the disengaged position when the pressure in the cylinder 300 decreases. A retaining ring 220 is installed at the lower end of the cylinder side. The positions and connections of the friction plate assembly 10, the output gear ring 20, the end plate 30, the friction plate seat 40, the stop ring 50, and the return spring 60 satisfy the technical principles of existing friction clutch technology. Other components and connections are the same as in specific embodiment one.

[0053] Specific implementation method three: Combining Figures 1 to 6 This embodiment differs from specific embodiment one in that the oil supply circuit includes an axial oil hole 120 and a radial oil hole 140, and the cylinder 300 is provided with a main oil inlet 320. The axial oil hole 120, the radial oil hole 140, and the main oil inlet 320 are sequentially connected, and the main oil inlet 320 is connected to the first oil inlet circuit 340 and the second oil inlet circuit 330, respectively. Other components and connection methods are the same as in specific embodiment one or two.

[0054] Specific implementation method four: Combination Figures 1 to 6 This embodiment differs from specific embodiment one in that the two-position three-way solenoid valve 900 has a P port, an A port, and a T port; the P port is connected to the external oil supply system, the A port is connected to the oil delivery circuit, and the T port is the return port. Other components and connections are the same as in any one of specific embodiments one to three.

[0055] Specific Implementation Method Five: Combining Figures 1 to 6 This embodiment differs from specific embodiment one in that when the two-position three-way solenoid valve 900 is energized, external pressure oil quickly enters the first annular cavity B1 through the oil supply line and the first oil inlet line 340.

[0056] The second annular cavity B2 and the third annular cavity B3 are filled with oil for a delayed time due to the hydraulic resistance of the oil inlet damping plug 350 and the installation gap.

[0057] By utilizing the rapid oil filling of the first annular cavity and the delayed oil filling of the second and third annular cavities, the piston clamping force increases in a stepwise manner, correspondingly causing the clutch transmission torque to change in a stepwise manner as well. "During the low-torque phase of the clutch output, the main unit can drive the load to accelerate under low load, i.e., a soft-contact clutch. During the high-torque phase of the clutch output, the main unit can drive the load to operate continuously for a long time under high load." This effect is achieved entirely through piston partitioning and damping structures, without requiring external pressure changes. Other components and connection methods are the same as any one of specific implementation methods one through four.

[0058] Specific Implementation Method Six: Combination Figures 1 to 6 This embodiment differs from Specific Embodiment 1 in that when the two-position three-way solenoid valve 900 is de-energized, the oil in the oil cylinder 300 is discharged through the oil supply circuit.

[0059] The piston 400 is pushed back to the disengaged position by the return spring 60, and the friction plate assembly 10 is released. Other components and connections are the same as in any one of embodiments one through five.

[0060] Specific implementation method seven: Combination Figures 1 to 6This embodiment differs from specific embodiment one in that the diameter of the damping orifice of the oil inlet damping plug 350 is adjustable, used to control the oil filling time of the second annular cavity B2. The diameter of the damping orifice is determined by the diameter of the oil inlet damping plug 350, the gap between the cylinder partition concave ring 310 and the piston partition convex ring 420, the pressure provided by the external oil supply system, and the flow characteristics of the working oil. It can be adjusted by changing the diameter of the damping orifice of the oil damping plug 350. Other components and connection methods are the same as in any one of specific embodiments one through six.

[0061] Specific implementation method eight: Combination Figures 1 to 6 This embodiment differs from Specific Embodiment 1 in that the area of ​​the first annular cavity B1 is adjustable in proportion to the total hydraulic area of ​​the piston 400, which is used to set the torque magnitude during the flexible connection stage. Figure 2 In this state, the clamping force on the piston is F1 = 2SB1

[0062] Figure 3 In this state, the clamping force on the piston is F = F1 + F2 + F3 = 2*(SB1 + SB2 + SB3) = 2*S.

[0063] S = SB1 + SB2 + SB3 is the total effective hydraulic area of ​​piston 400.

[0064] The ratio of F1 to F is F / F1 = SB1 / S, and the proportion of the area of ​​the first annular cavity B1 in S can be adjusted according to the torque requirements of the host flexible connector. Other components and connection methods are the same as any one of the specific embodiments one to seven.

[0065] Specific Implementation Method Nine: Combining Figures 1 to 6 This embodiment differs from specific embodiment one in that, during the oil filling process, the pressures in the first annular cavity B1, the second annular cavity B2, and the third annular cavity B3 sequentially reach the system oil supply pressure, creating a time difference in pressure build-up. The pressures PB1 in the first annular cavity B1, PB2 in the second annular cavity B2, and PB3 in the third annular cavity B3 reach the pressure P supplied by the external oil supply system, typically 2.0 MPa, with a certain time interval. The clutch automatically forms a stepped clamping force at different stages, requiring only a two-position three-way solenoid valve for external control of the oil circuit, eliminating the need for pressure regulation. Other components and connections are the same as any one of specific embodiments one through eight.

[0066] Specific Implementation Method Ten: Combining Figures 1 to 6This embodiment differs from specific embodiment one in that, during clutch engagement, the clamping force on piston 400 increases in a stepped manner, corresponding to a stepped change in clutch output torque. During clutch engagement, the hydraulic clamping force F on piston 400 is stepped, and the clutch output torque also exhibits a stepped shape. In the low-torque phase, the main unit can drive the load to accelerate under low load, i.e., a soft engagement. In the high-torque phase, the main unit can drive the load to operate continuously for extended periods under high load. Other components and connections are the same as in any one of specific embodiments one through eight.

[0067] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A friction clutch with a radially partitioned output piston, characterized in that... It includes an input shaft (100), a hydraulic cylinder (300), a piston (400), a convex ring (420), a partitioned concave ring (310), an oil inlet damping screw plug (350), and a two-position three-way solenoid valve (900). A convex ring (420) is disposed on the side wall of the piston (400), and a partitioned concave ring (310) is disposed on the side wall of the cylinder (300). The shapes of the convex ring (420) and the partitioned concave ring (310) are matched, and the cavity between the piston (400) and the cylinder (300) is divided into three annular cavities by the convex ring (420) and the partitioned concave ring (310), namely the first annular cavity (B1), the second annular cavity (B2), and the third annular cavity (B3). The first annular cavity (B1) is disposed on the upper side of the convex ring (420), the second annular cavity (B2), the third annular cavity (B3), and the fourth annular cavity (B4) is disposed on the upper side of the convex ring (420). 2) The third annular cavity (B3) is located on the left side of the convex ring (420) and is located on the lower side of the convex ring (420). The cylinder (300) is provided with a first oil inlet passage (340) that communicates with the first annular cavity (B1). The cylinder (300) is provided with a second oil inlet passage (330) that communicates with the second annular cavity (B2). An oil inlet damping screw plug (350) is installed in the second oil inlet passage (330). An installation gap is provided between the convex ring (420) and the partitioned concave ring (310). The installation gap generates liquid resistance to the working oil flowing inside. An oil supply circuit is provided inside the input shaft (100), and a two-position three-way solenoid valve (900) is installed on the oil supply circuit. The oil supply circuit is connected to the first oil inlet circuit (340) and the second oil inlet circuit (330) respectively.

2. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that... It also includes a friction plate assembly (10), an output gear ring (20), an end plate (30), a friction plate seat (40), a stop ring (50), and a return spring (60). The friction plate assembly (10) is installed on the right side of the convex ring (420), the output toothed ring (20) is installed on the upper side of the friction plate assembly (10), the end plate (30) is installed on the right side of the friction plate assembly (10), the friction plate seat (40) is set between the input shaft (100) and the end plate (30), the stop ring (50) is installed on the lower side of the friction plate assembly (10), and the return spring (60) is embedded in the stop ring (50); The return spring (60) is used to push the piston (400) back to the disengaged position when the pressure in the cylinder (300) drops.

3. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, The oil supply circuit includes an axial oil hole (120) and a radial oil hole (140). The cylinder (300) is provided with a total oil inlet (320). The axial oil hole (120), the radial oil hole (140) and the total oil inlet (320) are connected in sequence. The total oil inlet (320) is connected to the first oil inlet circuit (340) and the second oil inlet circuit (330) respectively.

4. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, The two-position three-way solenoid valve (900) has a P port, an A port, and a T port; Port P connects to the external oil supply system, port A connects to the oil delivery circuit, and port T is the return port.

5. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, When the two-position three-way solenoid valve (900) is energized, external pressure oil quickly enters the first annular cavity (B1) through the oil supply line and the first oil inlet line (340). The second annular cavity (B2) and the third annular cavity (B3) are filled with oil for a delayed time due to the hydraulic resistance of the oil inlet damping plug (350) and the installation gap.

6. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, When the two-position three-way solenoid valve (900) is de-energized, the oil in the cylinder (300) is discharged through the oil supply line; The piston (400) is pushed back to the disengaged position by the return spring (60), and the friction plate assembly (10) is released.

7. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, The damping orifice diameter of the inlet damping plug (350) is adjustable to control the filling time of the second annular cavity (B2).

8. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, The area of ​​the first annular cavity (B1) is adjustable as a proportion of the total hydraulic area of ​​the piston (400) to set the torque magnitude of the flexible connection stage.

9. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, During the oil filling process, the pressures of the first annular cavity (B1), the second annular cavity (B2), and the third annular cavity (B3) sequentially reach the system oil supply pressure, creating a time difference in pressure build-up.

10. A friction clutch with a radially partitioned output piston according to claim 1, characterized in that, During clutch engagement, the clamping force on the piston (400) increases in a stepwise manner, corresponding to a stepwise change in the clutch output torque.

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