A positioning device for high-speed wet friction elements

Abstract

The present invention aims to provide a positioning device for a high-speed wet friction element, comprising a shaft, a cylinder, a piston, a plate holder, an end plate, a blocking plate, and a ribbed gear ring. The cylinder, piston, plate holder, and end plate are all mounted on the exterior of the shaft, the blocking plate is fixedly connected to the ribbed gear ring, and an inner-toothed butterfly plate and an outer-lug friction plate are mounted in the space enclosed by the piston, plate holder, end plate, blocking plate, and ribbed gear ring. The inner-toothed butterfly plate and the outer-lug friction plate are spaced apart to form a series of friction pairs. An annular segmented spring is mounted between the outer-lug friction plates, between the blocking plate and the first outer-lug friction plate, and between the ribbed gear ring and the last outer-lug friction plate. The present invention achieves simultaneous precise radial and axial positioning of the friction element without increasing the volume or weight of the wet friction clutch, thereby reducing dynamic imbalance and drag torque of the friction element and enabling the wet friction clutch to adapt to higher operating speeds.

Description

Technical Field

[0001] The present invention relates to a wet friction clutch, in particular to a positioning device of the wet friction clutch. Background Art

[0002] Currently, compared to gear clutches, known wet friction clutches suffer from low power density, low operating speeds, and high drag torque after clutch disengagement. This is because wet friction clutches utilize disc-shaped wet friction elements, which transmit torque through frictional forces between cylinder pistons. Compared to the tooth-to-tooth contact torque transmission of gear clutches, frictional torque transmission significantly reduces torque transmission capacity. Furthermore, the wet friction element is significantly larger than a sleeve gear structure capable of transmitting the same torque, resulting in a larger overall wet friction clutch and lower power density.

[0003] Because there is obvious sliding friction and heating between the friction elements when the wet friction clutch is engaged, a radial clearance is reserved in the design for the radial thermal expansion of the friction elements. After the clutch is disengaged, this radial clearance will cause a certain radial displacement of the friction elements, resulting in a certain dynamic imbalance. When the operating speed is high, the dynamic imbalance will produce greater vibration, so the operating speed of the wet friction clutch cannot be too high.

[0004] After a wet friction clutch is disengaged, the friction elements rely on the flow of lubricating oil to separate and achieve axial positioning. However, as the speed of the wet friction clutch increases, the lubricating oil between the friction elements will generate a large drag torque, increasing the power loss after the clutch is disengaged. At the same time, all friction elements rely solely on the flow of lubricating oil to separate from each other, without achieving reliable axial positioning. As a result, although the clutch is disengaged, random friction will occur between the friction elements, further increasing the power loss after the clutch is disengaged, manifesting as a large drag torque. Summary of the Invention

[0005] The purpose of the present invention is to provide a high-speed wet friction element positioning device that can achieve simultaneous precise radial and axial positioning of the friction element without increasing the volume and weight of the wet friction clutch, so that the wet friction clutch can adapt to higher operating speeds.

[0006] The object of the present invention is achieved like this:

[0007] The present invention provides a positioning device for a high-speed wet friction element, which is characterized by comprising a shaft, an oil cylinder, a piston, a light plate seat, an end plate, a blocking plate, and a rib gear ring. The oil cylinder, the piston, the light plate seat, and the end plate are all installed on the outside of the shaft, and the blocking plate is fixedly connected to the rib gear ring. Inner-toothed butterfly-shaped light plates and outer lug friction plates are installed in the space surrounded by the piston, the light plate seat, the end plate, the blocking plate, and the rib gear ring. The inner-toothed butterfly-shaped light plates and the outer lug friction plates are arranged at intervals from each other to form a series of friction pairs. Circular segmented springs are installed between the outer lug friction plates, a circular segmented spring is installed between the blocking plate and the first outer lug friction plate, and a circular segmented spring is installed between the rib gear ring and the last outer lug friction plate.

[0008] The present invention may also include:

[0009] 1. The outer ring of the optical piece seat is provided with optical piece seat teeth, the inner diameter of the outer lug friction plate is made with a friction plate bearing ring, the inner ring of the inner tooth butterfly optical piece is provided with butterfly optical piece teeth, the friction plate bearing ring and the butterfly optical piece teeth are respectively matched with the optical piece seat teeth.

[0010] 2. The annular segmented spring includes an annular spring body, and a first protrusion and a second protrusion are fixed on both sides of the spring body along its circumference.

[0011] 3. The circular segmented spring is sleeved on the rib gear ring, and the inner diameter of the spring body and the outer diameter of the rib gear ring form a sliding fit.

[0012] 4. An inner groove and an outer groove are provided on the spring body between the adjacent first protrusion and the second protrusion.

[0013] 5. The rib gear ring is provided with a rib rack and a rib tooth groove. The rib rack is formed by the fusion of the gear ring teeth with an involute tooth shape, and the rib tooth groove is formed by the elimination of the gear ring teeth with an involute tooth shape. The rib rack and the rib tooth groove are arranged at intervals; the outer ring of the external lug friction plate is provided with an external lug, and the external lug is in contact with the rib gear rack to transmit torque; the first lug and the second lug extend into the rib tooth groove and press against the external lug, so that the adjacent external lug friction plates are axially separated from each other, or the external lug friction plate, the blocking plate and the rib gear ring are axially separated from each other.

[0014] 6. A shaft lubricating oil hole is opened inside the shaft, and a light piece seat groove oil spray hole and a light piece seat tooth oil spray hole are opened in the light piece seat. The shaft lubricating oil hole is connected to the light piece seat groove oil spray hole and the light piece seat tooth oil spray hole respectively. The outer diameter of the concave disk surface of the inner tooth butterfly light piece is provided with an outer oil wedge groove, and the inner diameter of the convex disk surface of the inner tooth butterfly light piece is provided with an inner oil wedge groove. The lubricating oil flowing out of the light piece seat groove oil spray hole flows to the outer oil wedge groove and the inner oil wedge groove, and the light piece seat tooth oil spray hole supplies oil to the friction plate bearing ring.

[0015] 7. The structure of the outer oil wedge groove and the inner oil wedge groove is a double-turn wedge-shaped oil groove with a deep middle part and shallow sides.

[0016] 8. The cross section of the double-turn wedge-shaped oil tank is straight or arc-shaped.

[0017] 9. The middle part of the outer lug friction plate is a core plate made of metal material, and the two sides of the core plate are fixed friction layers, and the friction layer is provided with a friction plate oil groove; the annular spring body is made of spring steel, and the first and second lugs are made of aluminum or magnesium alloy.

[0018] The advantages of the present invention are that it can achieve simultaneous precise radial and axial positioning of the friction element without increasing the volume and weight of the wet friction clutch, reducing the dynamic imbalance and drag torque of the friction element, and enabling the wet friction clutch to adapt to higher operating speeds. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a longitudinal cross-sectional view of a prior art wet friction clutch;

[0020] Figure 2 is a transverse cross-sectional view of a prior art wet friction clutch;

[0021] Figure 3 The present invention Figure 5 Sectional view of section AA;

[0022] Figure 4 The present invention Figure 5 Cross-sectional view of the middle BB section;

[0023] Figure 5 The present invention Figure 3 Cross-sectional view of the CC section;

[0024] Figure 6 This is the front view of the outer lug friction plate;

[0025] Figure 7 yes Figure 6 Cross-sectional view of the middle DD section;

[0026] Figure 8 This is the main view of the inner tooth butterfly light sheet;

[0027] Figure 9 yes Figure 8 Cross-sectional view of the FF section;

[0028] Figure 10 yes Figure 8 A cross-sectional view of the first embodiment of the GG section;

[0029] Figure 11 yes Figure 8 A cross-sectional view of the first embodiment taken along section HH;

[0030] Figure 12 yes Figure 8 A cross-sectional view of a second embodiment of the invention taken along section GG;

[0031] Figure 13 yes Figure 8 A cross-sectional view of a second embodiment taken along section HH;

[0032] Figure 14 This is a schematic diagram of the lubricating oil flow between the outer lug friction plate and the inner tooth butterfly light plate, in which the butterfly light plate profile is exaggerated;

[0033] Figure 15 is a cross-sectional view of the optical sheet holder;

[0034] Figure 16 is a cross-sectional view of the rib ring;

[0035] Figure 17 This is the main view of the circular ring segment spring;

[0036] Figure 18 yes Figure 17 Cross-sectional view of section II;

[0037] Figure 19 yes Figure 17 Cross-sectional view of section JJ. DETAILED DESCRIPTION

[0038] The present invention will be described in more detail below with reference to the accompanying drawings:

[0039] Combine Figure 1-19 ,exist Figure 1 、 Figure 2 In a known wet friction clutch, internal toothed plates 40 and external toothed friction plates 30 are alternately arranged to form multiple friction pairs. Each external toothed friction plate 30 forms a sliding sleeve connection with the involute ring gear 20. The external toothed friction plates 30 can move axially on the involute ring gear 20 while transmitting torque. The ring gear teeth 22 and friction plate teeth 32 are designed to have a side clearance fit, typically 0.35 mm, to accommodate tooth machining errors and radial thermal expansion of the friction plates caused by clutch engagement friction.

[0040] Each inner-toothed light piece 40 forms a sliding sleeve tooth connection with the light piece seat 80. The inner-toothed light piece 40 can move axially on the light piece seat 80 while transmitting torque. The light piece teeth 42 and the light piece seat teeth 82 are designed to fit the tooth side clearance, with a typical value of 0.15mm, to accommodate the processing error of the teeth.

[0041] The oil cylinder 60 is rigidly connected to the shaft 70, and the piston 50 can slide axially on the oil cylinder 60 and the shaft 70. The end plate 90 is rigidly connected to the optical disc holder 80 via fasteners. The pressure plate 100 presses the end plate 90 and optical disc holder 80 combination onto the shaft 70 via fasteners. The optical disc holder 80 and the shaft 70 are splined, and the end plate 90 and the shaft 70 are connected by a positioning spigot.

[0042] Multiple springs 110 are positioned between the optical disc holder 80 and the piston 50. Pressurized working oil enters the oil cylinder 60 through the shaft working oil hole 72, pushing the piston 50 to move and compress the friction pair, engaging the clutch and enabling bidirectional power transmission between the flange 10 and the shaft 70. When the working oil pressure is released, the springs 110 push the piston 50 back, relaxing the friction pair and disengaging the clutch. The power transmission between the flange 10 and the shaft 70 is disconnected, and the shaft system containing the flange 10 and the shaft 70 can rotate freely or remain stationary. Lubricating oil enters the optical disc holder 80 through the shaft lubricating oil hole 74 and supplies oil to each friction pair through the oil injection holes of the optical disc holder 80. The lubricating oil flowing through the friction pair flows out of the clutch through the ring gear oil outlet hole 24.

[0043] After the clutch is disengaged, the lubricating oil flowing through the friction pairs forms an oil film of a certain thickness, separating the inner toothed plate 40 from the outer toothed friction plate 30. The thickness of the oil film is closely related to the lubricating oil supply, the position and diameter deviation of the oil injection holes, the absolute speed of the shaft 70, and the relative speed between the inner toothed plate 40 and the outer toothed friction plate 30. The oil film thickness varies between the friction pairs, which can easily cause rubbing, resulting in increased drag torque and heating of the lubricating oil.

[0044] Due to the existence of tooth side clearance, after the clutch is disengaged, the external tooth friction plate 30 moves radially relative to the involute gear ring 20 under the action of gravity, causing the shaft system where the involute gear ring 20 is located to be dynamically unbalanced, resulting in the clutch being unable to adapt to high speed requirements.

[0045] Under the existing technology, the optical blade teeth 42 are processed by stamping or gear shaping, which has a large processing error. The tooth side clearance between the optical blade teeth 42 and the optical blade seat teeth 82 will also cause dynamic imbalance of the shaft system where the rear shaft 70 is located after the clutch is disengaged.

[0046] In short, since the inner gear light plate 40 and the outer gear friction plate 30 are in a loose state without precise positioning after the clutch is disengaged, the lubricating oil heating and dynamic imbalance problems caused by the drag torque will occur, and the known wet friction clutch is difficult to operate in the high speed range.

[0047] exist Figure 3-Figure 5A positioning device for a high-speed wet friction element comprises a blocking plate 600, a rib gear ring 200, an outer lug friction plate 300, an inner butterfly-shaped light plate 400, an annular split spring 500, and a light plate holder 80. The disc-shaped outer lug friction plates 300 and the inner butterfly-shaped light plates 400 are spaced apart to form multiple friction pairs. An annular split spring 500 is positioned between the blocking plate 600 and the first outer lug friction plate, between each of the nine outer lug friction plates 300 (see figure), and between the last outer lug friction plate and the rib gear ring 200. When the clutch is disengaged, the split spring 500 forces the first outer lug friction plate to abut against the blocking plate 600, the last outer lug friction plate to abut against the positioning surface of the rib gear ring 200, and separates all the outer lug friction plates 300, ultimately ensuring precise axial positioning of all outer lug friction plates 300.

[0048] exist Figure 6 、 Figure 7 In the example, the outer lug friction plate 300 comprises a metal core plate 36 in the middle, with sintered or bonded friction layers 38 on either side. Friction layer 38 is provided with friction plate oil grooves 34, typically in a cross-grid configuration. When the clutch is engaged, lubricating oil flows out through the friction plate oil grooves 34. When the clutch is disengaged, the lubricating oil flows through the friction pair through the friction plate oil grooves 34 and the disengagement gap between the friction pairs, increasing the oil film thickness. The friction pair oil film is subject to radial centrifugal force and tangential viscous force. After the clutch is disengaged, one end remains stationary while the other continues to rotate at high speed, subjecting the friction pair's oil film to intense shear. Consequently, the viscous force within the oil film, caused by the speed difference, generates a certain drag torque.

[0049] The friction plate teeth 32 feature a well-known involute profile, characterized by self-alignment of the internal and external tooth profiles during torque transmission, ensuring excellent precision positioning. The outer lug 320 is formed by the fusion of several friction plate teeth 32. The tooth side transmitting torque still has an involute profile with the same parameters, allowing the outer lug 320 and rib teeth 220 to self-align during torque transmission. The inner diameter of the outer lug friction plate 300 is formed with a friction plate bearing ring 310 made of bearing alloy. The inner diameter 312 of the bearing ring is a close sliding fit with the tip diameter of the optical plate holder teeth 82 and the outer diameter of the optical plate holder, typically 0.05 mm. This ensures precise radial positioning of the outer lug friction plate 300 and ensures the dynamic balancing accuracy of the shaft system in which the outer lug friction plate 300 is located.

[0050] Figure 8In the process, the butterfly light blade teeth 410 are processed by the currently known manufacturing method of gear shaping, which is improved to medium-wire or slow-wire electric spark wire cutting processing, so that the accuracy of the butterfly light blade teeth 410 is improved from 8-9 levels of gear shaping to 6-7 levels, and the matching accuracy of the butterfly light blade teeth 410 and the light blade seat teeth 82 is improved, so that the inner tooth butterfly light blade 410 relies on a smaller tooth side clearance, the typical value is 0.05mm, and at the same time meets the positioning and sliding requirements, thereby achieving precise radial positioning of the inner tooth butterfly light blade 410.

[0051] Figure 8 picture- Figure 13 In the embodiment, a plurality of evenly distributed outer oil wedge grooves 420 are made on the outer diameter of the inner concave disk surface of the inner-toothed butterfly-shaped light plate 400, and a plurality of evenly distributed inner oil wedge grooves 430 are made on the inner diameter of the outer convex disk surface of the inner-toothed butterfly-shaped light plate 400. Both the outer oil wedge grooves 420 and the inner oil wedge grooves 430 are double-turn wedge-shaped oil grooves. When the lubricating oil flows through these wedge-shaped oil grooves in an approximately circumferential direction, a mutually balanced and stable axial thrust will be generated on the inner concave disk surface and the outer convex disk surface, thereby realizing the precise axial positioning of the inner-toothed butterfly-shaped light plate 400 relative to each adjacent outer lug friction plate 300.

[0052] Figure 10 picture- Figure 13 The inner oil wedge groove 430 and the outer oil wedge groove 420 are double-direction wedge-shaped oil grooves with a deep middle and shallow sides, which can adapt to different working directions of the clutch. An embodiment of the linear type of the wedge-shaped oil groove is a straight line type such as Figure 10 and Figure 11 As shown, the second embodiment of the linear type of the wedge-shaped oil groove is an arc type as shown in FIG. Figure 12 and Figure 13 As shown in the figure, as the lubricating oil flows from the deeper center of the wedge-shaped oil groove to the shallower edge, the oil flow is compressed and its pressure increases, generating a force perpendicular to the wedge-shaped oil groove, namely, axial thrust. The smaller the gap between the inner-toothed butterfly-shaped light plate 400 and the adjacent outer-lug friction plate 300, the greater the compression tendency of the lubricating oil flow, resulting in greater pressure and axial thrust.

[0053] Figure 14In the figure, the inner oil wedge groove 430 opens at the inner diameter of the convex outer surface of the inner-toothed butterfly-shaped optical disc 400. Lubricating oil flows into the friction pair at this point, generating thrust directed toward the inner-toothed butterfly-shaped optical disc 400. The outer oil wedge groove 420 opens at the outer diameter of the concave inner surface of the inner-toothed butterfly-shaped optical disc 400. Lubricating oil flows out of the friction pair at this point, also generating thrust directed toward the inner-toothed butterfly-shaped optical disc 400. As a result, the lubricating oil flow generates thrust on both sides of the inner-toothed butterfly-shaped optical disc 400. When the thrust is unbalanced, the lubricating oil flow on the side with greater thrust causes the inner-toothed butterfly-shaped optical disc 400 to move toward the side with less thrust. As a result, the lubricating oil flow on the side with greater thrust becomes thicker, reducing thrust, while the lubricating oil flow on the side with less thrust becomes thinner, increasing thrust. Ultimately, a stable thrust balance is achieved, achieving precise positioning of the inner-toothed butterfly-shaped optical disc 400.

[0054] Figure 15 In the embodiment, the optical plate holder 80 and the shaft 70 are connected by an involute spline. Lubricating oil provided by the shaft lubricating oil hole 74 flows through the internal oil groove and oil holes of the optical plate holder 80 and out of the optical plate holder slot oil spray hole 84, thus supplying oil to the friction pair. At the same time, lubricating oil provided by the shaft lubricating oil hole 74 flows through the internal oil groove and oil holes of the optical plate holder 80 and out of the optical plate holder gear oil spray hole 86, thus supplying oil to the friction plate bearing ring 310.

[0055] Figure 16 In the clutch, the rib tooth grooves 210 are semi-open in the radial direction and fully open in the axial direction. The blocking plate 600 is fixed to the radially open side of the rib tooth grooves 210 of the rib gear ring 200 using fasteners. Because the rib teeth 220 are located at the point of maximum clutch diameter, they are subjected to minimal force and possess excess strength. Even with the rib tooth grooves 210 open, they still have sufficient torque transmission strength.

[0056] The rib teeth 220 are formed by fusing together several involute ring gear teeth 22, while the rib tooth grooves 210 are formed by eliminating several involute ring gear teeth 22. The outer lugs 320 of the outer lug friction plate 300 contact the rib tooth grooves 210 of the rib gear ring 200 to transmit torque. Because the outer lugs 320 and the rib tooth grooves 210 have the same involute tooth profile parameters, the outer lug friction plate 300 and the rib gear ring 200 can automatically align during torque transmission.

[0057] Figure 17 picture- Figure 19 In the figure, the circular segmented spring 500 consists of a circular spring body 510 with a precisely machined inner diameter, connected to tabs I 520 and II 530 via rivets 540. The two sets of tabs I 520 and II 530 are evenly distributed on either side of the spring body 510, aligning with the angles of the outer lugs 320. The circular segmented spring 500 fits over the ribbed gear ring 200, creating a sliding fit with a small clearance (typically 0.05 mm) between the inner diameter of the spring body 510 and the outer diameter of the ribbed gear ring 200. This ensures the dynamic balance accuracy of the shaft system in which the circular segmented spring 500 is mounted.

[0058] The connection via rivets 540 facilitates the use of materials with different elastic moduli and densities for the annular spring body 510 and lugs I 520 and II 530. For example, using spring steel for the annular spring body 510 and light metals such as aluminum or magnesium alloy for lugs I 520 and II 530 further reduces weight. The connection via rivets 540 also facilitates heat treatment and precision machining of the annular spring body 510's inner diameter, compared to a one-piece stamped wave spring.

[0059] The spring body 510 is centrally located between the protrusions I 520 and II 530, and has an inner groove 550 and an outer groove 560 to adjust the stiffness of the spring body 510. The inner groove 550 further reduces the contact area between the inner diameter of the spring body 510 and the rib gear ring 200, thereby minimizing dimensional changes caused by deformation of the spring body 510 and reducing the sliding resistance of the circular segmented spring 500.

[0060] The lugs I 520 and II 530 extend into the rib tooth grooves 210 and press against the outer lugs 320 , so that the adjacent outer lug friction plates 300 are axially separated from each other, or the outer lug friction plates 300 are axially separated from the blocking plate 600 and the rib gear ring 200 .

[0061] The dispersedly arranged annular segmented springs 500 occupy a large portion of the outer diameter material of the rib gear ring 200 (the length of the radial semi-open structure of the rib tooth groove 210), which greatly reduces the weight of the rib gear ring 200 and the clutch.

Claims

1. A positioning device for a high-speed wet friction element, characterized by: It includes a shaft, a cylinder, a piston, a light plate seat, an end plate, a blocking plate, and a rib gear ring. The cylinder, the piston, the light plate seat, and the end plate are all installed on the outside of the shaft. The blocking plate and the rib gear ring are fixedly connected. Inner-toothed butterfly-shaped light plates and outer lug friction plates are installed in the space surrounded by the piston, the light plate seat, the end plate, the blocking plate, and the rib gear ring. The inner-toothed butterfly-shaped light plates and the outer lug friction plates are arranged at intervals to form a series of friction pairs. Circular segmented springs are installed between the outer lug friction plates, between the blocking plate and the first outer lug friction plate, and between the rib gear ring and the last outer lug friction plate. The outer ring of the optical plate seat is provided with optical plate seat teeth, the inner diameter of the outer lug friction plate is provided with a friction plate bearing ring, the inner ring of the inner tooth butterfly optical plate is provided with butterfly optical plate teeth, the friction plate bearing ring and the butterfly optical plate teeth are respectively matched with the optical plate seat teeth; The circular segmented spring comprises a circular spring body, with a first protrusion and a second protrusion respectively fixed on both sides of the spring body along its circumference; The rib gear ring is provided with rib racks and rib tooth grooves, the rib racks are formed by the fusion of gear ring teeth with involute tooth profiles, and the rib tooth grooves are formed by the elimination of gear ring teeth with involute tooth profiles, and the rib racks and rib tooth grooves are arranged at intervals; the outer ring of the outer lug friction plate is provided with an outer lug, and the outer lug is in contact with the rib gear rack to transmit torque; the first lug and the second lug extend into the rib tooth grooves and press against the outer lugs, so that the adjacent outer lug friction plates are axially separated from each other, or the outer lug friction plate, the blocking plate and the rib gear ring are axially separated from each other.

2. The positioning device for a high-speed wet friction element according to claim 1, characterized in that: The circular segmented spring is sleeved on the rib gear ring, and the inner diameter of the spring body and the outer diameter of the rib gear ring form a sliding fit.

3. The positioning device for a high-speed wet friction element according to claim 1, characterized in that: An inner groove and an outer groove are formed on the spring body between the adjacent first protruding pieces and the second protruding pieces.

4. The positioning device for a high-speed wet friction element according to claim 1, characterized in that: An oil lubrication hole is provided inside the shaft, and an oil spray hole for the light piece seat groove and an oil spray hole for the light piece seat gear are provided in the light piece seat. The oil lubrication hole is connected to the oil spray hole for the light piece seat groove and the oil spray hole for the light piece seat gear respectively. An outer oil wedge groove is provided on the outer diameter of the inner concave disk surface of the inner-toothed butterfly-shaped light piece, and an inner oil wedge groove is provided on the inner diameter of the outer convex disk surface of the inner-toothed butterfly-shaped light piece. The lubricating oil flowing out of the oil spray hole for the light piece seat groove flows to the outer oil wedge groove and the inner oil wedge groove, and the oil spray hole for the light piece seat gear supplies oil to the friction plate bearing ring.

5. The positioning device for a high-speed wet friction element according to claim 4, characterized in that: The structure of the outer oil wedge groove and the inner oil wedge groove is a double-turn wedge-shaped oil groove with a deep middle portion and shallow two sides.

6. The positioning device for a high-speed wet friction element according to claim 4, characterized in that: The cross section of the double-turn wedge-shaped oil groove is straight or arc-shaped.

7. The positioning device for a high-speed wet friction element according to claim 1, characterized in that: The middle part of the outer lug friction plate is a core plate of metal material, and both sides of the core plate are fixed friction layers with friction plate oil grooves formed on the friction layers; the annular spring body is made of spring steel, and the first and second lugs are made of aluminum or magnesium alloy.

Images