Wet dual clutch assembly

Abstract

The application discloses a wet double clutch assembly. The wet double clutch assembly comprises a piston housing, a low-gear piston, a high-gear piston, a low-gear bearing, a high-gear bearing, a low-gear clutch assembly and a high-gear clutch assembly; the piston housing is arranged between the low-gear clutch assembly and the high-gear clutch assembly; the low-gear piston and the high-gear piston are arranged in the piston housing respectively; the low-gear clutch assembly comprises a low-gear clutch outer hub, a low-gear clutch inner hub, a low-gear friction plate, a low-gear steel sheet and a low-gear separation spring; and the high-gear clutch assembly comprises a high-gear clutch outer hub, a high-gear clutch inner hub, a high-gear friction plate, a high-gear steel sheet and a high-gear separation spring. The wet double clutch assembly can optimize the structure.

Description

Technical Field

[0001] This application relates to the automotive field, and more specifically, to a wet dual-clutch assembly. Background Technology

[0002] There exists a wet clutch assembly comprising a hydraulic actuator, a piston, an outer clutch hub, an inner clutch hub, friction plates, steel plates, and a cooling and lubrication structure. This type of wet clutch assembly supplies oil to the piston's oil chamber via hydraulic control lines, pushing the piston to move axially, causing the friction plates and steel plates to press together or separate, thereby achieving the engagement and disengagement of power.

[0003] In a wet multi-plate clutch structure, the friction plates and steel plates are typically in a lubricating oil or cooling oil environment. When the clutch is engaged, torque is transmitted between the friction plates and steel plates through friction; when the clutch is disengaged, the friction plates and steel plates are released from their clamping state. Summary of the Invention

[0004] According to one aspect of this application, a wet dual-clutch assembly includes: a piston housing, a low-gear piston, a high-gear piston, a low-gear bearing, a high-gear bearing, a low-gear clutch assembly, and a high-gear clutch assembly. The piston housing is disposed between the low-gear clutch assembly and the high-gear clutch assembly; The low-gear piston and the high-gear piston are respectively disposed in the piston housing. The low-gear piston applies an axial clamping force to the low-gear clutch assembly through the low-gear bearing, and the high-gear piston applies an axial clamping force to the high-gear clutch assembly through the high-gear bearing. The low-gear clutch assembly includes a low-gear clutch outer hub, a low-gear clutch inner hub, a low-gear friction plate, a low-gear steel plate, and a low-gear release spring. The low-gear friction plate is kinetically connected to the low-gear clutch outer hub, and the low-gear steel plate is kinetically connected to the low-gear clutch inner hub. The low-gear release spring is disposed in the low-gear clutch assembly and is used to separate the low-gear friction plate from the low-gear steel plate when the low-gear clutch assembly is disengaged. The high-gear clutch assembly includes a high-gear clutch outer hub, a high-gear clutch inner hub, a high-gear friction plate, a high-gear steel plate, and a high-gear release spring. The high-gear friction plate is tractively connected to the high-gear clutch outer hub, and the high-gear steel plate is tractively connected to the high-gear clutch inner hub. The high-gear release spring is disposed in the high-gear clutch assembly and is used to separate the high-gear friction plate from the high-gear steel plate when the high-gear clutch assembly is disengaged.

[0005] With the above technical solution, the piston housing is positioned between the low-gear clutch assembly and the high-gear clutch assembly. The low-gear piston and the high-gear piston apply axial clamping force to their respective clutch assemblies through corresponding bearings, thereby enabling separate driving of the two clutches. The low-gear release spring and the high-gear release spring are used to separate the friction plates from the steel plates when the corresponding clutch assemblies are disengaged, which helps to reduce the drag torque of the wet dual-clutch assembly in the disengaged state. Thus, the wet dual-clutch assembly has an optimized structure. Attached Figure Description

[0006] The disclosure of this application is illustrated with reference to the accompanying drawings. It should be understood that the drawings are for illustrative purposes only and are not intended to limit the scope of protection of this application. Wherein: Figure 1 The schematic illustration shows a wet dual-clutch assembly according to one embodiment of this application; Figure 2 A partial exploded view of the wet dual-clutch assembly is shown schematically. Figure 3a The diagram schematically shows the inner ring of a split needle roller thrust bearing in a wet dual-clutch assembly. Figure 3b The schematic diagram shows the outer ring of the split needle roller thrust bearing in the wet dual-clutch assembly; Figure 4a The schematic diagram shows the outer hub of the high-gear clutch in a wet dual-clutch assembly; Figure 4b The schematic diagram shows the low-gear clutch outer hub in a wet dual-clutch assembly; Figure 5a The release spring in the wet dual-clutch assembly is shown schematically in a front view; Figure 5b The release spring in the wet dual-clutch assembly is schematically shown in a side view; Figure 6 The schematic diagram illustrates the assembly configuration of the release spring in a wet dual-clutch assembly. Detailed Implementation

[0007] The embodiments of this application will now be described in detail with reference to the accompanying drawings. Those skilled in the art will appreciate that these descriptions are merely descriptive and exemplary and should not be construed as limiting the scope of protection of this application.

[0008] refer to Figures 1 to 2As shown, a wet dual-clutch assembly according to a specific embodiment of this application includes a piston housing 6, a low-gear piston 18, a high-gear piston 15, a low-gear bearing, a high-gear bearing, a low-gear clutch assembly, and a high-gear clutch assembly. The low-gear bearing can be a low-gear thrust bearing 19, and the high-gear bearing can be a high-gear thrust bearing 14. The piston housing 6 is disposed between the low-gear clutch assembly and the high-gear clutch assembly. The low-gear piston and the high-gear piston are respectively disposed within the piston housing 6.

[0009] The piston housing 6 can serve as the mounting base for a centrally symmetrical actuator system. The low-gear clutch assembly and the high-gear clutch assembly are located on opposite axial sides of the piston housing 6, with the low-gear piston and high-gear piston respectively outputting axial thrust towards their respective clutch assemblies. The low-gear piston applies axial clamping force to the low-gear clutch assembly via the low-gear bearing, and the high-gear piston applies axial clamping force to the high-gear clutch assembly via the high-gear bearing.

[0010] The low-gear clutch assembly includes a low-gear clutch outer hub 1, a low-gear clutch inner hub 10, a low-gear friction plate, a low-gear steel plate, and a low-gear release spring. The low-gear friction plate can be formed from friction plate 20, the low-gear steel plate can be formed from steel plate 3, and the low-gear release spring can be formed from release spring 4. The low-gear friction plate is driven to the low-gear clutch outer hub 1, and the low-gear steel plate is driven to the low-gear clutch inner hub 10. For example, the internal splines of the low-gear clutch outer hub 1 mate with the external splines of the low-gear friction plate, and the internal splines of the low-gear steel plate mate with the external splines of the low-gear clutch inner hub 10.

[0011] The high-gear clutch assembly includes a high-gear clutch outer hub 8, a high-gear clutch inner hub 12, a high-gear friction plate, a high-gear steel plate, and a high-gear release spring. (Reference) Figure 2 The high-gear friction plate can be formed from friction plate 20, the high-gear steel plate can be formed from steel plate 3, and the high-gear release spring can be formed from release spring 4. The high-gear friction plate is driven by the outer hub 8 of the high-gear clutch, and the high-gear steel plate is driven by the inner hub 12 of the high-gear clutch. For example, the internal splines of the outer hub 8 of the high-gear clutch mate with the external splines of the high-gear friction plate, and the internal splines of the high-gear steel plate mate with the external splines of the inner hub 12 of the high-gear clutch.

[0012] The low-gear release spring is located in the low-gear clutch assembly and is used to separate the low-gear friction plate from the low-gear steel plate when the low-gear clutch assembly is disengaged. The high-gear release spring is located in the high-gear clutch assembly and is used to separate the high-gear friction plate from the high-gear steel plate when the high-gear clutch assembly is disengaged.

[0013] The low-gear clutch assembly and the high-gear clutch assembly may also include a retaining ring 5. The retaining ring 5 is fixedly installed in a retaining ring in the corresponding clutch outer hub and is used to axially limit the installation of the friction plate 20, the steel plate 3, and the release spring 4. The friction plate 20, the steel plate 3, the release spring 4, and the friction plate 20 can be arranged sequentially inside the outer hub and axially limited by the retaining ring 5.

[0014] The piston housing 6 is positioned between the two clutch assemblies, forming a centrally located actuator arrangement that can control the engagement and disengagement of the low-gear clutch assembly and the high-gear clutch assembly respectively. The release spring 4 separates the friction plate 20 from the steel plate 3 when the clutch is disengaged, which helps to reduce the drag torque generated by the oil film shear between the plates.

[0015] The low-gear piston and high-gear piston can be configured to be arranged opposite each other along the axial direction of the wet dual-clutch assembly, and their movement directions are opposite. The low-gear piston moves toward the low-gear clutch assembly under hydraulic pressure, and the high-gear piston moves toward the high-gear clutch assembly under hydraulic pressure.

[0016] The low-gear piston and the high-gear piston are integrated and installed within the same piston housing 6. The piston housing 6 is located in the middle of the wet dual-clutch assembly, and the low-gear piston and the high-gear piston output axial clamping force to opposite sides of the piston housing 6, respectively. The low-gear piston and the high-gear piston can be arranged axially symmetrically or approximately symmetrically to form a centrally symmetrical actuation system.

[0017] The two pistons are arranged opposite each other and move in opposite directions. They can drive two sets of clutches respectively through a centrally located hydraulic actuator, which helps to improve the structural integration and reduce the axial repetition of the actuators.

[0018] According to one embodiment, a low-gear piston oil chamber and a high-gear piston oil chamber are formed within the piston housing 6. The low-gear piston is disposed within the low-gear piston oil chamber, and the high-gear piston is disposed within the high-gear piston oil chamber. The low-gear piston oil chamber and the high-gear piston oil chamber are independent of each other, that is, they are isolated from each other and each is independently sealed.

[0019] The piston housing 6 is provided with a low-gear oil inlet passage and a high-gear oil inlet passage. The low-gear oil inlet passage communicates with the low-gear piston oil chamber, and the high-gear oil inlet passage communicates with the high-gear piston oil chamber. According to one embodiment, an oil inlet pipe 7 is installed on the piston housing 6 and connected to the clutch hydraulic control line. The hydraulic control line can generate oil pressure through a solenoid valve and input the oil pressure into the corresponding piston oil chamber to drive the low-gear piston or the high-gear piston to move axially.

[0020] The low-gear piston oil chamber and the high-gear piston oil chamber are independent of each other, as are the low-gear oil inlet circuit and the high-gear oil inlet circuit. Pressure changes in the low-gear piston oil chamber control the movement of the low-gear piston, and pressure changes in the high-gear piston oil chamber control the movement of the high-gear piston. Therefore, the low-gear clutch assembly and the high-gear clutch assembly can be controlled independently.

[0021] The two piston oil chambers and the two oil inlet circuits are independent of each other, which can meet the needs of independent control of the low-gear piston and the high-gear piston, and facilitate the power switching between low gear and high gear.

[0022] According to one embodiment, a sealing ring is provided on the outer diameter side and the inner diameter side of the low-gear piston, and a sealing ring is provided on the outer diameter side and the inner diameter side of the high-gear piston. Specifically, an outer diameter sealing ring 16 can be provided on the outer diameter side of the piston, and an inner diameter sealing ring 17 can be provided on the inner diameter side of the piston. The outer diameter sealing ring and the inner diameter sealing ring can be installed in the annular groove of the piston housing 6, or they can cooperate with the outer circumferential surface and the inner circumferential surface of the piston to form a seal.

[0023] The outer diameter side seal of the low-gear piston mates with the outer diameter side sealing surface of the piston housing 6, and the inner diameter side seal of the low-gear piston mates with the inner diameter side sealing surface of the piston housing 6, thereby defining the low-gear piston oil chamber. The outer diameter side seal and inner diameter side seal of the high-gear piston define the high-gear piston oil chamber in a corresponding manner.

[0024] Sealing rings are installed on both the outer and inner diameter sides of the piston, which can improve the sealing performance of the corresponding piston oil chamber, so that the hydraulic pressure acts stably on the piston, thereby enabling the piston to reliably output axial clamping force.

[0025] According to one embodiment, the low-gear bearing and the high-gear bearing are thrust bearings. The low-gear bearing can be a low-gear thrust bearing, and the high-gear bearing can be a high-gear thrust bearing. The low-gear thrust bearing is disposed between the low-gear piston and the low-gear clutch assembly, and the high-gear thrust bearing is disposed between the high-gear piston and the high-gear clutch assembly. The thrust bearing is used to withstand and transmit the axial clamping force generated by the piston, while allowing relative rotation between the piston and the rotary clutch components.

[0026] For example, a low-gear bearing includes an outer ring and an inner ring. The outer ring is installed in the annular groove of the low-gear piston, and the inner ring contacts the outermost low-gear steel plate among a plurality of low-gear steel plates. A high-gear bearing includes an outer ring and an inner ring. The outer ring is installed in the annular groove of the high-gear piston, and the inner ring contacts the outermost high-gear steel plate among a plurality of high-gear steel plates.

[0027] Both the low-gear and high-gear thrust bearings can be split-type needle roller thrust bearings. (See reference...) Figure 3a and Figure 3b As shown. The outer ring of the split needle roller thrust bearing is installed in the annular groove of the corresponding piston, and the inner ring is preloaded and fitted onto the outermost steel plate 3 of the corresponding clutch assembly. The split needle roller thrust bearing can transmit axial force through the fit between the outer ring, inner ring, and rolling elements.

[0028] During operation, the axial thrust of the low-gear piston is transmitted to the outer ring of the low-gear bearing, and then to the inner ring of the low-gear bearing. The inner ring of the low-gear bearing applies axial clamping force to the outermost low-gear steel plate among the multiple low-gear steel plates, thereby pressing the low-gear friction plate and the low-gear steel plate together. The force transmission method of the high-gear bearing corresponds to that of the low-gear bearing.

[0029] After assembly, split needle roller thrust bearings can adapt to a certain range of assembly deviations through the relative fit between the outer ring, inner ring, and rolling elements, thereby reducing the impact of assembly eccentricity on the stability of axial clamping force transmission.

[0030] Thrust bearings can transmit the axial clamping force output by the piston and reduce the friction between the piston and the rotary clutch components; the split needle roller thrust bearing has a smaller axial dimension, which is beneficial to reduce the axial arrangement space of the wet dual clutch assembly and reduce the energy loss caused by bearing friction.

[0031] According to one embodiment, low-gear friction plates and low-gear steel plates are arranged alternately along the axial direction, and high-gear friction plates and high-gear steel plates are arranged alternately along the axial direction. Friction plates 20 can serve as both low-gear and high-gear friction plates, and steel plates 3 can serve as both low-gear and high-gear steel plates. Multiple low-gear friction plates and multiple low-gear steel plates together form a low-gear clutch plate group, and multiple high-gear friction plates and multiple high-gear steel plates together form a high-gear clutch plate group.

[0032] The low-gear release spring is positioned between adjacent low-gear friction plates, and the high-gear release spring is positioned between adjacent high-gear friction plates. Release spring 4 can function as both a low-gear and high-gear release spring. When the clutch is engaged, the low-gear piston or high-gear piston applies axial clamping force through the corresponding bearing, compressing the release spring 4 and gradually pressing the friction plates 20 against the steel plate 3. When the clutch disengages, the axial clamping force applied by the piston decreases or is released, and the release spring 4 uses its rebound force to separate the friction plates 20 from the steel plate 3.

[0033] The release spring 4 can be arranged between adjacent friction plates 20, and by means of corresponding wave crests, the friction plates 20 and steel plates 3 are separated by a certain axial distance when the clutch is in the disengaged state, and the gap between the plates is relatively uniform.

[0034] The retaining ring 5 is fixedly installed in the retaining ring of the outer hub of the clutch to axially limit the friction plate 20, the steel plate 3, and the release spring 4. The retaining plate 2 can also be set inside the outer hub of the clutch, forming a plate assembly structure together with the steel plate 3, the release spring 4, and the friction plate 20.

[0035] The friction plates 20 and steel plates 3 are arranged alternately along the axial direction, which can form multiple friction pairs in a limited axial space; the separation spring 4 is set between adjacent friction plates 20, which can cause the friction plates 20 and steel plates 3 to actively separate when the clutch is not engaged, thereby reducing the drag torque.

[0036] refer to Figure 5a , Figure 5b and Figure 6 As shown, the low-gear release spring and the high-gear release spring are annular wave-shaped springs with multiple crests 26 and troughs 27 along the circumferential direction. Both the low-gear release spring and the high-gear release spring can be formed by the release spring 4. The crests and troughs form a height difference along the axial direction, enabling the release spring 4 to generate an elastic separation force within a small axial space.

[0037] refer to Figure 5b As shown, the low-gear release spring and the high-gear release spring are each provided with a positioning groove 25. (Reference) Figure 4b As shown, the inner spline of the low-gear clutch outer hub 1 is provided with positioning teeth 24 that mate with the positioning groove of the low-gear release spring; Reference Figure 4a As shown, the inner spline of the high-gear clutch outer hub 8 is provided with positioning teeth 23 that cooperate with the positioning groove of the high-gear release spring.

[0038] For example, the release spring 4 has several slots. (See reference) Figure 6 As shown, when assembling the release spring 4, the positioning groove of the release spring 4 engages with the positioning teeth in the spline inside the clutch outer hub to ensure the radial and circumferential positioning of the release spring 4 within the clutch outer hub. The positioning teeth can be formed by special teeth in the spline inside the clutch outer hub. Through the engagement of the positioning groove and the positioning teeth, the release spring 4 is less prone to circumferential movement during clutch operation.

[0039] According to one embodiment, an annular wave spring is arranged between adjacent friction plates 20, with multiple wave crests forming an elastic support relationship with adjacent structures in the axial direction. When the clutch is disengaged, the annular wave spring creates a gap between the friction plate 20 and the steel plate 3 through its own elastic restoring force; when the clutch is engaged, the axial clamping force applied by the piston overcomes the elastic force of the annular wave spring, pressing the friction plate 20 and the steel plate 3 together.

[0040] The annular wave spring can provide separation force within a limited axial space; the positioning groove and positioning teeth can keep the installation position of the separation spring 4 stable, so that the friction plate 20 and the steel plate 3 maintain a relatively uniform inter-plate distance in the separated state.

[0041] According to one embodiment, the low-gear clutch outer hub 1 is fixedly connected to the low-gear transmission gear 9, and the high-gear clutch outer hub 8 is fixedly connected to the high-gear transmission gear 13. Specifically, the low-gear clutch outer hub 1 can be welded to the low-gear transmission gear 9, and the high-gear clutch outer hub 8 can be welded to the high-gear transmission gear 13.

[0042] The low-gear clutch outer hub 1 and the high-gear clutch outer hub 8 can be manufactured using a spinning process. A number of circular holes can be machined on the splined outer wall of the clutch outer hub to guide cooling oil recovery during clutch operation. A number of fan-shaped areas can be machined on the bottom of the clutch outer hub to reduce its weight.

[0043] The low-gear clutch outer hub 1 is provided with an oil drain hole 22, and the high-gear clutch outer hub 8 is provided with an oil drain groove 21. According to one embodiment, the oil drain hole of the low-gear clutch outer hub 1 can be a round hole, and the oil drain groove of the high-gear clutch outer hub 8 can be a U-shaped groove. During gear shifting, when the high-gear clutch plate assembly undertakes more slippage, the oil drain groove of the high-gear clutch outer hub 8 can reduce the oil flow resistance, allowing more cooling oil to flow through the high-gear clutch plate assembly to carry away the heat generated during slippage.

[0044] The low-gear clutch outer hub 1 and the high-gear clutch outer hub 8 are fixedly connected to the corresponding transmission gears, respectively, forming a low-gear power input path and a high-gear power input path. After flowing through the friction plates 20 and the steel plates 3, the cooling oil can be discharged through the oil drain hole or oil drain groove to maintain the cooling and lubrication of the clutch plate assembly.

[0045] After the outer hub is fixedly connected to the corresponding transmission gear, it can realize the transmission of power paths in low gear and high gear. The outer hub 1 of the low gear clutch is provided with an oil drain hole and the outer hub 8 of the high gear clutch is provided with an oil drain groove, which can improve the discharge and distribution of cooling oil and is beneficial to cooling the clutch plate assembly.

[0046] When the clutch system shifts from neutral to a low or high gear, power is transmitted from the low-gear transmission gear 9 or the high-gear transmission gear 13 to the corresponding low-gear clutch outer hub 1 or high-gear clutch outer hub 8, and then transmitted to the corresponding friction plate 20 through the splines of the corresponding clutch outer hub. At this time, the hydraulic control system generates oil pressure and pushes the corresponding low-gear piston or high-gear piston to move axially, which in turn pushes the corresponding low-gear thrust bearing or high-gear thrust bearing to move axially. The corresponding thrust bearing contacts the steel plate 3 and successively compresses the release spring 4, so that the speed difference between the friction plate 20 and the steel plate 3 gradually decreases until the friction plate 20 and the steel plate 3 engage. Subsequently, power is transmitted from the internal splines of the steel plate 3 to the corresponding low-gear clutch inner hub 10 or high-gear clutch inner hub 12, thereby realizing the transmission of power torque.

[0047] When the clutch system shifts from a low gear to a high gear, the hydraulic control system reduces the oil pressure in the low gear piston circuit, decreasing the piston thrust. The rebound force of the release spring 4 causes the friction plate 20 to quickly separate from the steel plate 3, interrupting the low gear power. Simultaneously, the hydraulic control system increases the oil pressure in the high gear piston circuit, pushing the high gear piston and the high gear thrust bearing axially. The high gear thrust bearing contacts the steel plate 3 and subsequently compresses the release spring 4, gradually reducing the speed difference between the friction plate 20 and the steel plate 3 until they engage. Power is then transmitted from the internal spline of the steel plate 3 to the high gear clutch inner hub 12, achieving gear shifting.

[0048] When the clutch system shifts from a low gear or a high gear to neutral, the hydraulic control system reduces the oil pressure in the corresponding piston circuit, thereby reducing the thrust of the corresponding low-gear or high-gear piston. The release springs 4 between the friction plates 20 use their rebound force to quickly separate the friction plates 20 from the steel plates 3, and push the corresponding pistons back to their original positions, thus interrupting power.

[0049] The low-gear clutch assembly and the high-gear clutch assembly can be controlled by corresponding pistons and thrust bearings respectively; the release spring 4 can cause the friction plate 20 and the steel plate 3 to separate quickly when the corresponding clutch is disengaged; the thrust bearing can reduce relative rotational friction while transmitting axial force, which helps to reduce drag torque and reduce axial arrangement space.

Claims

1. A wet dual-clutch assembly, characterized in that, The wet dual-clutch assembly includes: a piston housing, a low-gear piston, a high-gear piston, a low-gear bearing, a high-gear bearing, a low-gear clutch assembly, and a high-gear clutch assembly; The piston housing is disposed between the low-gear clutch assembly and the high-gear clutch assembly; The low-gear piston and the high-gear piston are respectively disposed in the piston housing. The low-gear piston applies an axial clamping force to the low-gear clutch assembly through the low-gear bearing, and the high-gear piston applies an axial clamping force to the high-gear clutch assembly through the high-gear bearing. The low-gear clutch assembly includes a low-gear clutch outer hub, a low-gear clutch inner hub, a low-gear friction plate, a low-gear steel plate, and a low-gear release spring. The low-gear friction plate is throttle-connected to the low-gear clutch outer hub, the low-gear steel plate is throttle-connected to the low-gear clutch inner hub, and the low-gear release spring is disposed in the low-gear clutch assembly for separating the low-gear friction plate from the low-gear steel plate when the low-gear clutch assembly is disengaged. The high-gear clutch assembly includes a high-gear clutch outer hub, a high-gear clutch inner hub, a high-gear friction plate, a high-gear steel plate, and a high-gear release spring. The high-gear friction plate is tractively connected to the high-gear clutch outer hub, and the high-gear steel plate is tractively connected to the high-gear clutch inner hub. The high-gear release spring is disposed in the high-gear clutch assembly and is used to separate the high-gear friction plate from the high-gear steel plate when the high-gear clutch assembly is disengaged.

2. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear piston and the high-gear piston are arranged opposite to each other along the axial direction of the wet dual-clutch assembly, and the low-gear piston and the high-gear piston move in opposite directions.

3. The wet dual-clutch assembly according to claim 1, characterized in that, The piston housing forms a low-gear piston oil chamber and a high-gear piston oil chamber. The low-gear piston is disposed in the low-gear piston oil chamber, and the high-gear piston is disposed in the high-gear piston oil chamber. The low-gear piston oil chamber and the high-gear piston oil chamber are independent of each other.

4. The wet dual-clutch assembly according to claim 3, characterized in that, The piston housing is provided with a low-gear oil inlet passage and a high-gear oil inlet passage. The low-gear oil inlet passage is connected to the low-gear piston oil chamber, and the high-gear oil inlet passage is connected to the high-gear piston oil chamber.

5. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear piston has sealing rings on its outer diameter side and inner diameter side, and the high-gear piston has sealing rings on its outer diameter side and inner diameter side.

6. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear bearing and the high-gear bearing are thrust bearings.

7. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear bearing includes a low-gear bearing outer ring and a low-gear bearing inner ring. The low-gear bearing outer ring is installed in the annular groove of the low-gear piston, and the low-gear bearing inner ring is in contact with the outermost low-gear steel sheet among the plurality of low-gear steel sheets. The high-gear bearing includes a high-gear bearing outer ring and a high-gear bearing inner ring. The high-gear bearing outer ring is installed in the annular groove of the high-gear piston, and the high-gear bearing inner ring is in contact with the outermost high-gear steel sheet among the plurality of high-gear steel sheets.

8. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear friction plate and the low-gear steel plate are arranged alternately along the axial direction, and the high-gear friction plate and the high-gear steel plate are arranged alternately along the axial direction. The low-gear separation spring is disposed between adjacent low-gear friction plates, and the high-gear separation spring is disposed between adjacent high-gear friction plates.

9. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear release spring and the high-gear release spring are annular wave-shaped springs with multiple peaks and troughs along the circumference. The low-gear release spring and the high-gear release spring are respectively provided with positioning grooves. The inner spline of the low-gear clutch outer hub is provided with positioning teeth that cooperate with the positioning groove of the low-gear release spring. The inner spline of the high-gear clutch outer hub is provided with positioning teeth that cooperate with the positioning groove of the high-gear release spring.

10. The wet dual-clutch assembly according to claim 1, characterized in that, The low-gear clutch outer hub is fixedly connected to the low-gear transmission gear, and the high-gear clutch outer hub is fixedly connected to the high-gear transmission gear. The low-gear clutch outer hub is provided with an oil drain hole, and the high-gear clutch outer hub is provided with an oil drain groove.

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