A friction plate group separating device

Abstract

A separation device for a friction plate group relates to the field of friction plate groups of clutches. The present invention aims to solve the problems of low axial positioning accuracy of friction elements in existing wet friction clutches, which leads to large clutch drag torque, and poor clutch maintainability and low power density due to the use of cylindrical coil springs and guide rod separation in dry friction clutches. In the separation device for a friction plate group described in the present invention, an end plug is sealed at the head end of the involute gear ring of the clutch, a retaining ring is located between the end plate of the clutch and the flange, and is in close contact with the flange, an outer ring of the retaining ring is interference-fitted with an inner ring of the involute gear ring, a first wave spring is provided between the end plug and the first friction plate of the clutch, and the end plug and the first wave spring are fixedly connected, a second wave spring is provided between two adjacent friction plates of the clutch, and between the rear friction plate of the clutch and the retaining ring, and a third wave spring is provided between two adjacent plates of the clutch.

Description

Technical Field

[0001] The invention belongs to the field of friction plate groups of clutches. Background Art

[0002] A significant disadvantage of existing wet friction clutches compared to tooth clutches is the high drag torque after clutch disengagement, which reduces the clutch's no-load transmission efficiency and easily causes the clutch's discharged lubricant to heat up, increasing the burden on the clutch's lubrication and cooling system. This disadvantage arises from the fact that after a wet friction clutch disengages, one set of friction elements is stationary while the other set rotates. The friction elements are separated and axially positioned by the flow of lubricating oil, resulting in a large drag torque generated by the shear flow of lubricating oil between the friction elements. Furthermore, since all friction elements are separated solely by the flow of lubricating oil, reliable axial positioning is not achieved. This results in random, mutually influencing rubbing between the friction elements even when the clutch is disengaged. This manifests as an intermittent increase in drag torque, further increasing power loss after clutch disengagement.

[0003] The existing dry friction clutch uses an elastic mechanism consisting of cylindrical coil springs and guide rods to separate the friction plate group elements. The guide rods are used to provide support and guidance for the springs. Its significant disadvantage is that depending on the number of friction elements, the friction plate group needs to be installed with dozens of cylindrical coil springs and guide rods, which greatly increases the workload of assembling, repairing and replacing the friction elements. The cylindrical coil springs and guide rods occupy a large radial space of the clutch, further reducing the power density of the clutch. Summary of the Invention

[0004] The present invention aims to solve the problems of low axial positioning accuracy of friction elements in existing wet friction clutches, which leads to large clutch drag torque, and poor clutch maintainability and low power density due to the use of cylindrical coil springs and guide rod separation in dry friction clutches. A friction plate separation device is now provided.

[0005] A friction plate group separating device, comprising: a retaining ring and an end blocking plate,

[0006] The end blocking plate is sealed at the head end of the involute gear ring of the clutch, the retaining ring is located between the end light plate of the clutch and the flange, and the retaining ring and the flange are in close contact, and the outer ring of the retaining ring is interference fit with the inner ring of the involute gear ring.

[0007] A first wave spring is provided between the end blocking plate and the first end friction plate of the clutch, and the end blocking plate and the first wave spring are fixedly connected.

[0008] A second wave spring is provided between two adjacent friction plates of the clutch, and between the rear friction plate and the retaining ring of the clutch.

[0009] A third wave spring is provided between two adjacent light plates of the clutch.

[0010] Furthermore, the friction plate comprises a core plate and two friction layers stacked and coaxially arranged, the two friction layers are fixed on both sides of the core plate respectively, and the friction layer surface is provided with an oil groove.

[0011] An outer widening ring is provided between the outer circumference of the friction plate and the outer teeth, and the second wave spring is located between two adjacent outer widening rings.

[0012] Furthermore, an inner widening ring is provided between the inner ring of the optical sheet and the inner teeth, and the third wave spring is located between two adjacent inner widening rings.

[0013] Furthermore, the second wave spring and the third wave spring are both provided with a plurality of mounting holes uniformly opened along their circumferences.

[0014] A first protrusion is embedded in each mounting hole of the second wave spring and the third wave spring. The first protrusion protrudes in the axial direction, and the protruding directions of two adjacent first protrusions are opposite.

[0015] Furthermore, the first protrusion comprises a protrusion head and a protrusion tail which are coaxially connected in a straight line, and the protrusion tail is connected to the mounting hole by flanging and riveting.

[0016] Furthermore, the first wave spring has a plurality of mounting holes uniformly opened along its circumference.

[0017] Half of the mounting holes are embedded with first protruding posts, and the remaining half of the mounting holes are embedded with second protruding posts. The first protruding posts and the second protruding posts are arranged alternately.

[0018] The second protrusion protrudes toward the end blocking plate, and the protrusion directions of the first protrusion and the second protrusion are opposite.

[0019] Furthermore, the end blocking plate is provided with a plurality of connection holes, and the plurality of connection holes are the same in number as the plurality of second protruding posts and are directly opposite to each other.

[0020] The second protrusion includes a connecting handle, a protrusion head and a protrusion tail which are coaxially connected in a straight line. The connecting handle and the corresponding connecting hole are plugged into each other, and the protrusion tail is connected to the mounting hole of the first wave spring by flanging and riveting.

[0021] The beneficial effects of the present invention are:

[0022] The present invention provides an elastic plate-splitting device capable of axially separating and positioning friction plate elements when a friction clutch is disengaged. This allows for rapid axial separation and precise positioning of the friction elements after clutch disengagement, reducing friction between friction elements in wet friction clutches, lowering drag torque and lubricant oil heating. It also simplifies the assembly difficulty of bulk plate-splitting springs in dry friction clutches, enhances dry friction clutch maintainability, and improves power density. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a longitudinal cross-sectional view of an existing wet friction clutch;

[0024] Figure 2 It is a transverse cross-sectional view of an existing wet friction clutch;

[0025] Figure 3 It is a longitudinal cross-sectional view of an existing dry friction clutch;

[0026] Figure 4 and Figure 5 All of them are longitudinal cross-sectional views of a friction plate group separation device according to the present invention, wherein Figure 4 Indicates the disconnected state. Figure 5 Indicates the engaged state;

[0027] Figure 6 is a schematic diagram of the friction plate;

[0028] Figure 7 is a schematic diagram of the light sheet;

[0029] Figure 8 for Figure 4 Enlarged view of point A in the middle;

[0030] Figure 9 for Figure 4 Enlarged view of point B in the middle;

[0031] Figure 10 for Figure 5 Enlarged view of point C in the middle;

[0032] Figure 11 for Figure 5 Enlarged view of point D in the middle;

[0033] Figure 12 is a front view of the second wave spring and the third wave spring;

[0034] Figure 13 for Figure 12 Middle II sectional view;

[0035] Figure 14 for Figure 12 Middle JJ cross-sectional view;

[0036] Figure 15 for Figure 12 Middle KK section view;

[0037] Figure 16 for Figure 12 Middle LL section view;

[0038] Figure 17 is a height comparison diagram of three elastic states of the second wave spring;

[0039] Figure 18 This is the main view of the end blocking plate;

[0040] Figure 19 and Figure 20 They are cross-sectional views of the connection between the lower end blocking plate and the second wave spring at two angles;

[0041] Figure 21 It is the cross-sectional view of the positive (negative) protrusion column;

[0042] Figure 22 This is a cross-sectional view of the second protruding column.

[0043] In the figure, 10 flange, 20 involute ring gear, 22 ring gear teeth, 24 ring gear oil outlet hole, 30 external tooth friction plate, 32 friction plate teeth, 34 oil groove, 40 internal tooth light plate, 42 light plate teeth, 50 piston, 60 oil cylinder, 70 shaft, 72 shaft working oil hole, 74 shaft lubricating oil hole, 80 light plate seat, 82 light plate seat teeth, 90 end plate, 100 pressure plate, 110 spring, 200 retaining ring, 300 friction plate, 310 external widening ring, 320 external gear, 400 light plate, 410 internal widening ring, 420 internal teeth, 500 second wave spring, 502 first wave spring, 510 third wave spring, 520 reverse protrusion, 522 protrusion head, 524 protrusion tail, 526 tail hole, 528 tail flange, 530 positive protrusion, 532 second protrusion, 534 connecting handle, 536 connecting handle hole, 538 connecting handle flange, 540 large elastic ring, 542 large elastic ring mounting hole, 550 small elastic ring, 552 small elastic ring mounting hole, 600 end plugging plate, 610 connecting hole. DETAILED DESCRIPTION

[0044] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention. It should be noted that the embodiments of the present invention and the features in the embodiments can be combined with each other in the absence of conflict.

[0045] exist Figure 1 and Figure 2In a conventional wet friction clutch, the internally toothed linings 40 and externally toothed friction linings 30 are arranged alternately to form multiple friction pairs. Each externally toothed friction lining 30 forms a sliding sleeve connection with the involute ring gear 20. The externally toothed friction lining 30 can move axially on the involute ring gear 20 while transmitting torque. The ring gear teeth 22 and the friction lining teeth 32 form a sliding fit with side clearance positioning.

[0046] Each inner-toothed optical disc 40 forms a sliding sleeve tooth connection with the optical disc seat 80. The inner-toothed optical disc 40 can move axially on the optical disc seat 80 while transmitting torque. The optical disc teeth 42 and the optical disc seat teeth 82 also form a sliding fit with tooth side clearance positioning.

[0047] 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 connected by an involute spline, and the end plate 90 and the shaft 70 are connected by a positioning spigot.

[0048] 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.

[0049] After the clutch is disengaged, the lubricating oil flowing through the friction pair forms an oil film of a certain thickness, which separates the inner gear light plate 40 and the outer gear friction plate 30 from each other. Since the inner gear light plate 40 and the outer gear friction plate 30 are in a relatively loose state after the clutch is disengaged, their movement state is easily disturbed by external conditions. The oil film thickness between each friction pair is not the same, and friction is very likely to occur, resulting in an increase in the clutch drag torque, heating of the lubricating oil, and lower transmission efficiency.

[0050] exist Figure 3In existing dry friction clutches, a cylindrical coil spring with a larger diameter is installed between at least one set of friction elements to maintain longitudinal stability and to separate the friction elements after the clutch is disengaged. The cylindrical coil springs are evenly distributed around the circumference of the friction element, leaving the circumferential space between adjacent cylindrical coil springs unutilized. This results in a larger dry friction clutch and lower power density. Furthermore, the installation of multiple discrete springs complicates clutch assembly and hinders the repair and replacement of worn friction elements.

[0051] Therefore, the present invention provides the following embodiments to solve the above problems of the friction clutch.

[0052] Specific implementation method 1: refer to Figures 4 to 22 The present embodiment will be described in detail. In the present embodiment, a friction plate group separation device is described. The disc-shaped friction plates 300 and the optical plates 400 are spaced apart from each other to form a plurality of friction pairs.

[0053] The slicing device includes: a retaining ring 200 and an end blocking plate 600.

[0054] The end blocking plate 600 blocks the head end of the involute gear ring 20 of the clutch.

[0055] The retaining ring 200 is located between the clutch end plate 400 and the flange 10, and is in close contact with the flange 10. The outer diameter of the annular retaining ring 200 forms an interference fit with the teeth of the ring gear 22. Once installed, it cannot move axially. One end face of the retaining ring 200 is in close contact with the flange 10 and is axially positioned.

[0056] A first wave spring 502 is provided between the end blocking plate 600 and the first end friction plate 300 of the clutch, and the end blocking plate 600 and the first wave spring 502 are fixedly connected.

[0057] A second wave spring 500 is provided between two adjacent friction plates 300 of the clutch, and between the rear friction plate 300 and the retaining ring 200 of the clutch.

[0058] A third wave spring 510 is provided between two adjacent optical plates 400 of the clutch.

[0059] Furthermore, the friction plate 300 comprises a core plate and two friction layers stacked and coaxially arranged. The two friction layers are fixed to either side of the core plate, and the friction layers have oil grooves 34 formed on their surfaces. An outer widening ring 310 is provided between the outer circumference of the friction plate 300 and the outer teeth 320, and the second wave spring 500 is located between two adjacent outer widening rings 310.

[0060] Furthermore, an inner widening ring 410 is provided between the inner ring of the optical sheet 400 and the inner teeth 420 , and the third wave spring 510 is located between two adjacent inner widening rings 410 .

[0061] Furthermore, the second wave spring 500 and the third wave spring 510 each have a plurality of mounting holes uniformly formed along their circumferences. A first protrusion is embedded in each mounting hole of the second wave spring 500 and the third wave spring 510. The first protrusion protrudes axially, with adjacent first protrusions protruding in opposite directions.

[0062] Furthermore, the first protrusion includes a protrusion head 522 and a protrusion tail 524 that are coaxially connected in a straight line, and the protrusion tail 524 is connected to the mounting hole by flanging and riveting.

[0063] Furthermore, the first wave spring 502 has multiple mounting holes uniformly formed along its circumference. Half of the mounting holes are embedded with first protrusions, and the remaining half are embedded with second protrusions 532. The first protrusions 532 are alternately arranged. The second protrusions 532 protrude toward the end blocking plate 600, and the first and second protrusions 532 protrude in opposite directions.

[0064] Furthermore, the end blocking plate 600 is provided with a plurality of connection holes 610. These connection holes 610 are identical in number to the plurality of second protrusions 532 and are aligned one by one. The second protrusions 532 include a connecting handle 534, a protrusion head 522, and a protrusion tail 524, which are coaxially connected in a straight line. The connecting handle 534 is plugged into the corresponding connection hole 610, and the protrusion tail 524 is connected to the mounting hole of the first wave spring 502 by flanging and riveting.

[0065] In this embodiment, the end face of the protrusion head 522 of the anti-protrusion 520 of the second wave spring 500 located between the friction plate 300 at the tail end and the retaining ring 200 is pressed against the other end face of the retaining ring 200, and the axial length of the retaining ring 200 supplements the gap distance between the last second wave spring 500 and the original flange 10 of the clutch.

[0066] When the clutch is engaged, the piston 50 pushes the friction plate 300 and the optical plate 400 against the end plate 90. The first wave spring 502 mounted on the end plug 600 is at a free height, while all other second and third wave springs 500, 510, are in a compressed state. During the clutch disengagement process, the height of the second and third wave springs 500, 510 is the preload height H1. Both the second and third wave springs 500, 510 are in a deformed and compressed state, leaving ample room for further deformation. This provides a certain degree of elastic restoring force and compensates for the additional compression caused by the reduced distance between adjacent friction elements due to wear of the friction elements. When the clutch is in the disengaged state, the piston 50 retreats to the initial position under the action of the elastic force of the spring 110, and the second wave spring 500 and the third wave spring 510 recover from the compressed height to the preload height. The preload force of the second wave spring 500 and the third wave spring 510 separates all the widened friction plates 300 and the light plates 400 from each other, and finally accurately positions all the widened friction plates 300 and the light plates 400 axially.

[0067] like Figures 6 to 11 As shown, the friction plate 300 comprises a metal core plate in the middle, with sintered or bonded friction layers on both sides. These friction layers are provided with oil grooves 34. When the clutch is disengaged, one end remains stationary while the other continues to rotate at high speed. The viscous forces caused by the speed difference between the two friction pairs generate a certain drag torque. The friction plate 300 is an externally toothed friction plate 30, created by increasing the inner and outer diameters of the core plate. The pitch diameter of the external teeth 320 of the friction plate 300 is also increased by the same amount. The outer widening ring 310 accommodates the radial mounting space for the second wave spring 500, with the stud heads 522 of the second wave spring 500 pressing against the outer widening ring 310.

[0068] The optical blade 400 is an internally toothed optical blade 40 obtained by increasing its outer diameter. The pitch diameter of the internal teeth 420 of the optical blade 400 remains unchanged. The inner widening ring 410 is used to accommodate the radial installation space of the third wave spring 510. The protruding head 522 of the third wave spring 510 is pressed tightly against the inner widening ring 410.

[0069] like Figures 12 to 16 As shown, the second wave spring 500 is composed of an inverted protrusion 520, a positive protrusion 530 and a large elastic ring 540. The third wave spring 510 is composed of an inverted protrusion 520, a positive protrusion 530 and a small elastic ring 550.

[0070] The inverted protrusion 520 and the positive protrusion 530 are fixedly connected by riveting the protrusion tail 524 to the large elastic ring mounting hole 542 of the large elastic ring 540. The inverted protrusion 520 and the positive protrusion 530 are fixedly connected by riveting the protrusion tail 524 to the small elastic ring mounting hole 552 of the small elastic ring 550.

[0071] The protruding post tails 524 of the positive protruding post 530 and the negative protruding post 520 are inserted into the large elastic ring mounting holes 542 at intervals, and the tail holes 526 are riveted to form tail flanges 528. Tail flanges 528 secure the positive protruding post 530 and the negative protruding post 520 to the large elastic ring 540. The protruding post tails 524 of the positive protruding post 530 and the negative protruding post 520 are inserted into the small elastic ring mounting holes 552 at intervals, and the tail holes 526 are riveted to form tail flanges 528. Tail flanges 528 secure the positive protruding post 530 and the negative protruding post 520 to the small elastic ring 550.

[0072] The large elastic ring 540 and the small elastic ring 550 are both elastic plates or cylindrical forgings manufactured through precision machining. The outer diameter of the large elastic ring 540 and the inner diameter of the small elastic ring 550 are turned to obtain high dimensional accuracy, so that the large elastic ring 540 forms a sliding clearance fit with the tooth top circle of the ring gear tooth 22, and the small elastic ring 550 forms a sliding clearance fit with the tooth top circle of the optical plate seat tooth 82. In this way, the second wave spring 500 and the third wave spring 510 can obtain higher radial positioning to avoid causing dynamic imbalance.

[0073] like Figure 17 The figure shows a comparison of the axial deformation of the second wave spring 500 at its free height H0, preload height H1, and working height H2. When the clutch is engaged, the heights of the second and third wave springs 500, 510 are at the working height H2. When the clutch is disengaged, the heights of the second and third wave springs 500, 510 are at the preload height H1. Both the second and third wave springs 500, 510 are in a deformed and compressed state, leaving ample room for further deformation. This provides a certain degree of elastic restoring force and also compensates for the additional compression caused by the reduced distance between adjacent friction elements due to wear of the friction elements.

[0074] like Figure 10 As shown, after the device is engaged, the piston moves to the right to compress the friction plate group. The distance between the end blocking plate 600 and the first widened friction plate 30 is greater than the free height H0 of the second wave spring 500. Therefore, the first wave spring 502 on the end blocking plate 600 must be fixedly connected to prevent arbitrary axial movement.

[0075] like Figures 18 to 20 As shown, corresponding to the position of the outer widening ring 310 of the friction plate 300, a plurality of connecting holes 610 are opened on the end blocking plate 600. The connecting holes 610 are distributed in the same position as the large elastic ring mounting holes 542. The connecting handle 534 of the second protruding column 532 is inserted into the connecting hole 610, and the connecting handle hole 536 is riveted to form a connecting handle flange 538. The connecting handle flange 538 fixes the second protruding column 532 to the end blocking plate 600.

[0076] The tail portion 524 of the second protruding post 532 is inserted into the large elastic ring mounting hole 542 at intervals, and the tail hole 526 is riveted to form a tail flange 528 , which fixes the large elastic ring 540 on the second protruding post 532 .

[0077] The protruding post tail 524 of the anti-protruding post 520 is inserted into the large elastic ring mounting hole 542 at intervals, and the tail hole 526 is riveted to form a tail flange 528, which fixes the anti-protruding post 520 on the large elastic ring 540.

[0078] The difference between the first wave spring 502 and the second wave spring 500 is that the positive protrusion 530 is replaced by a second protrusion 532 , and the number and position of the negative protrusions 520 are exactly the same as those of the second wave spring 500 .

[0079] exist Figure 21 In the figure, the stepped shaft-shaped reverse protrusion 520 or the positive protrusion 530 is composed of a protrusion head 522, a protrusion tail 524, and a tail hole 526. The diameter of the protrusion head 522 is larger than the diameter of the protrusion tail 524. The tail hole 526 is located on one side of the protrusion tail 524. A special riveting tool is used to enlarge the diameter of the tail hole 526 to form a tail flange 528. The diameter of the tail flange 528 is larger than the diameter of the protrusion tail 524. During the formation of the tail flange 528, the tail flange 528 is mechanically deformed to produce a clamping effect and riveted connection with the protrusion head 522, so that the reverse protrusion 520 or the positive protrusion 530 can be fixed in the large elastic ring mounting hole 542 or the small elastic ring mounting hole 552.

[0080] like Figure 22 As shown, the stepped shaft-shaped second stud 532 comprises a connecting shank 534, a connecting shank hole 536, a stud head 522, a stud tail 524, and a tail hole 526. The stud head 522 is located between the connecting shank 534 and the stud tail 524, and its diameter is larger than the connecting shank 534 and the stud tail 524. The connecting shank hole 536 is located on one side of the connecting shank 534. A special riveting tool is used to enlarge the diameter of the connecting shank hole 536 to form a connecting shank flange 538. The diameter of the connecting shank flange 538 is larger than that of the connecting shank 534. During the formation of the connecting shank flange 538, the connecting shank flange 538 is mechanically deformed to produce a clamping effect with the stud head 522, thereby riveting the second stud 532 to secure it within the connecting hole 610. A special riveting tool is used to enlarge the diameter of the tail hole 526 on the second protrusion 532 to form a tail flange 528. The diameter of the tail flange 528 is larger than the diameter of the protrusion tail 524. During the formation of the tail flange 528, the tail flange 528 is mechanically deformed to produce a clamping effect and riveted connection with the protrusion head 522, so that the second protrusion 532 can be fixed in the large elastic ring mounting hole 542.

[0081] In summary, this embodiment relies on the elastic forces of the first, second, and third wave springs 502, 500, and 510 to position and separate the friction elements. Compared to conventional wave springs manufactured by stamping and heat treating elastic sheet material, the positioning diameters d4 and d1 of the large and small elastic rings 540 and 550 are obtained by machining the raw material after heat treatment, eliminating the heat-treatment deformation factor and thus achieving higher positioning diameter accuracy. The free height H0 of the first, second, and third wave springs 502, 500, and 510 can be flexibly adjusted by varying the height of the stud head 522, eliminating the need to manufacture entirely new elastomer blanks and stamping dies. The stiffness of the first wave spring 502, the second wave spring 500, and the third wave spring 510 can also be flexibly adjusted by changing the distribution position and quantity of the installed negative protrusions 520 and positive protrusions 530 and the thickness dimensions of the large elastic ring 540 and the small elastic ring 550. Therefore, this embodiment has high process convenience and does not require a special spring manufacturer and stamping mold for manufacturing. It is more convenient for a friction clutch manufacturer with general mechanical processing equipment to complete the processing and assembly of all clutch parts.

[0082] Although the present invention is described herein with reference to specific embodiments, it should be understood that these embodiments are merely illustrative of the principles and applications of the invention. It should be understood that many modifications may be made to the illustrative embodiments, and that other arrangements may be devised, without departing from the spirit and scope of the invention as defined by the appended claims. It should be understood that the various dependent claims and features described herein may be combined in ways other than those described in the original claims. It should also be understood that features described in conjunction with individual embodiments may be used in conjunction with other described embodiments.

Claims

1. A friction plate group separation device, characterized in that: include: retaining ring (200) and end plugging plate (600), The end blocking plate (600) is sealed at the head end of the involute gear ring (20) of the clutch, the retaining ring (200) is located between the end optical plate (400) of the clutch and the flange (10), and the retaining ring (200) and the flange (10) are in close contact, and the outer ring of the retaining ring (200) and the inner ring of the involute gear ring (20) are interference fit. A first wave spring (502) is provided between the end blocking plate (600) and the first end friction plate (300) of the clutch, and the end blocking plate (600) and the first wave spring (502) are fixedly connected. A second wave spring (500) is provided between two adjacent friction plates (300) of the clutch, and between the rear friction plate (300) and the retaining ring (200) of the clutch. A third wave spring (510) is provided between two adjacent optical plates (400) of the clutch; The second wave spring (500) and the third wave spring (510) are both provided with a plurality of mounting holes uniformly opened along their circumferences. A first protrusion is embedded in each mounting hole of the second wave spring (500) and the third wave spring (510), the first protrusion protrudes in the axial direction, and the protruding directions of two adjacent first protrusions are opposite.

2. A friction plate separation device according to claim 1, characterized in that: The friction plate (300) comprises a core plate and two friction layers stacked and coaxially arranged, wherein the two friction layers are respectively fixed on both sides of the core plate, and an oil groove (34) is formed on the surface of the friction layer. An outer widening ring (310) is provided between the outer circumference of the friction plate (300) and the outer teeth (320), and the second wave spring (500) is located between two adjacent outer widening rings (310).

3. The friction plate separation device according to claim 1, characterized in that: An inner widening ring (410) is provided between the inner ring of the optical sheet (400) and the inner teeth (420), and the third wave spring (510) is located between two adjacent inner widening rings (410).

4. The friction plate separation device according to claim 1, characterized in that: The first protruding column comprises a protruding column head (522) and a protruding column tail (524) which are coaxially connected in a straight line, and the protruding column tail (524) is connected to the mounting hole by means of flanging riveting.

5. The friction plate separation device according to claim 1, characterized in that: The first wave spring (502) has a plurality of mounting holes uniformly formed along its circumference. Half of the mounting holes are embedded with first protruding posts, and the remaining half of the mounting holes are embedded with second protruding posts (532). The first protruding posts and the second protruding posts (532) are arranged alternately. The second protruding column (532) protrudes toward the end blocking plate (600), and the protruding directions of the first protruding column and the second protruding column (532) are opposite.

6. The friction plate separation device according to claim 5, characterized in that: The end blocking plate (600) is provided with a plurality of connection holes (610), and the plurality of connection holes (610) are the same in number as the plurality of second protruding columns (532) and are directly opposite to each other. The second protrusion (532) includes a connecting handle (534), a protrusion head (522) and a protrusion tail (524) which are coaxially connected in a straight line. The connecting handle (534) and the corresponding connecting hole (610) are plugged into each other, and the protrusion tail (524) is connected to the mounting hole of the first wave spring (502) by flanging and riveting.

Images