Wave form dual steel sheet clutch quick self-separation device

Abstract

The present application relates to the technical field of clutch, and specifically provides a wave-shaped dual steel sheet clutch quick self-separation device, which comprises a transmission shaft and a shaft sleeve, the shaft sleeve is coaxial and fixedly arranged on the transmission shaft, a plurality of friction sheets, a gear ring and dual steel sheets are arranged in the shaft sleeve, the dual steel sheets are alternately arranged with the gear ring, the friction sheets are located between the dual steel sheets and the gear ring, the outer periphery of the dual steel sheets is uniformly distributed with first wave-shaped elastic sheets and second wave-shaped elastic sheets, the suspension ends of the first wave-shaped elastic sheets and the second wave-shaped elastic sheets are opposite, and the first wave-shaped elastic sheets and the second wave-shaped elastic sheets of adjacent dual steel sheets abut each other, so that the piston cylinder is pushed away from the adjacent dual steel sheets after elastic reset driven by pressure relief, a separation gap is forced to be formed, the sticking and seizure of the friction sheets caused by high-temperature sintering, oil film failure and impurity adhesion are avoided, and quick and reliable self-separation is realized.

Description

Technical Field

[0001] This invention relates to the field of clutch technology, and in particular to a rapid self-disengagement device for a wave-coupled steel plate clutch. Background Technology

[0002] Steel plate clutches, as core components in mechanical transmission systems that realize power switching, speed switching, and torque transmission, are widely used in engineering machinery, vehicle transmission, and industrial equipment. Existing steel plate clutches mostly employ a structure of alternating stacked gear rings, friction plates, and partitions, relying on axial compression and release to complete engagement and disengagement. Under long-term continuous or frequent clutch operation, the friction plates, partitions, and gear rings are prone to adhesion and seizing due to factors such as high-temperature sintering, lubricating oil film failure, and impurity adhesion.

[0003] This adhesion problem directly leads to incomplete clutch disengagement, delayed power cut-off, and increased shift shock. In severe cases, it can cause overload of the transmission system, abnormal wear of components, and even failure, reducing the reliability and service life of the clutch and increasing equipment maintenance costs. Currently, conventional steel plate clutches mostly rely on hydraulic thrust to achieve separation, lacking active anti-adhesion structures and elastic self-separation capabilities. After the partition and friction plate are attached, there is no reliable pre-separation elastic force, making it difficult to structurally suppress adhesion and failing to meet the requirements for high reliability, long service life, and rapid response. Summary of the Invention

[0004] Therefore, it is necessary to provide a rapid self-separation device for wave-coupled steel plate clutches to address the problem that friction plates, partitions, and gear rings are prone to sticking and seizing under long-term continuous or frequent clutch operation due to factors such as high-temperature sintering, lubricating oil film failure, and impurity adhesion.

[0005] The above objectives are achieved through the following technical solutions: A wave-coupled steel plate clutch quick self-disengagement device includes: A drive shaft and a bushing, wherein the bushing is coaxial and fixedly mounted on the drive shaft, and a plurality of friction plates, a gear ring and a mating steel plate are provided inside the bushing, wherein the mating steel plate and the gear ring are alternately arranged, and the friction plates are located between the mating steel plate and the gear ring; A piston cylinder is disposed within the bushing, and the telescopic end of the piston cylinder abuts against the end of the mating steel plate away from the friction plate. An elastic element is also provided on the telescopic end of the piston cylinder. The outer periphery of the dual steel sheet is uniformly provided with a plurality of first wave springs and second wave springs. The suspended end of the first wave spring and the suspended end of the second wave spring face opposite directions. The first wave spring and the second wave spring are alternately arranged, and the first wave spring and the second wave spring of adjacent dual steel sheets abut against each other.

[0006] Furthermore, the contact force between the first and second wave springs of adjacent paired steel plates is positively correlated with the locking force of the clutch.

[0007] Furthermore, both the first and second wave springs are provided with multiple dividing grooves, which divide the suspended ends of the first and second wave springs into multiple independent parts. The contact force between the first and second wave springs is positively correlated with the number of independent parts on the first and second wave springs that contact each other.

[0008] Furthermore, the contact force between the first and second wave spring sheets of the adjacent paired steel sheets is positively correlated with the elastic coefficients of the first and second wave spring sheets.

[0009] Furthermore, a hydraulic flow channel is provided on the drive shaft, and the hydraulic flow channel is connected to the hydraulic chamber of the piston cylinder.

[0010] Furthermore, the drive shaft is provided with a lubricating oil flow channel, and the lubricating oil flow channel is provided with a plurality of lubricating oil nozzles, the lubricating oil nozzles facing the inside of the bushing.

[0011] Furthermore, an abutment plate is fixedly provided inside the bushing. The abutment plate is located at the outer end of the outermost mating steel sheet. An abutment piece is provided on the outer periphery of the abutment plate corresponding to the position of the first wave spring and the second wave spring. The abutment piece abuts against the first wave spring and the second wave spring.

[0012] Furthermore, the bushing has a plurality of snap-fit ​​grooves evenly distributed around its outer circumference. The number of snap-fit ​​grooves is the same as the sum of the number of first and second wave spring pieces on a single paired steel sheet. The first and second wave spring pieces of the paired steel sheet are located in the corresponding snap-fit ​​grooves.

[0013] Furthermore, the elastic element is a disc spring, one end of which is fixed to the drive shaft by a clamp, and the other end abuts against the extension and retraction end of the piston cylinder.

[0014] Furthermore, the first and second wave spring sheets are integrally stamped with the paired steel sheet.

[0015] The beneficial effects of this invention are: This invention utilizes a first wave spring and a second wave spring evenly distributed circumferentially on the outer periphery of the mating steel plates. The suspended ends of the first wave spring and the second wave spring face opposite directions, and the first wave spring and the second wave spring of adjacent mating steel plates abut against each other. This allows the piston cylinder to actively and elastically reset and push the adjacent mating steel plates apart after depressurization, forcibly forming a separation gap. This avoids the friction plates from sticking and seizing due to high-temperature sintering, oil film failure, and impurity adhesion, thus achieving rapid and reliable self-separation.

[0016] This invention creates a partition groove on the first and second wave springs, forming multiple independent parts that do not affect each other. The contact force between the first and second wave springs can be adjusted by changing the number of contacts of these independent parts, thus adapting to different types of clutches and exhibiting strong versatility.

[0017] The present invention provides an abutment plate at the outer end of the outermost paired steel sheet, and an abutment piece on the abutment plate. The abutment piece abuts against the first or second wave spring on the paired steel sheet, so that the first and second wave springs on the outermost paired steel sheet are subjected to almost the same force as the first and second wave springs on other paired steel sheets, thus ensuring that the multiple paired steel sheets are subjected to uniform force.

[0018] This invention integrates the first wave spring, the second wave spring, and the dual steel sheet into a single stamping process, without adding independent elastic parts. This results in simple assembly, good consistency, and reduced processing and assembly costs. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the structure of a waveform-coupled steel plate clutch quick self-separation device provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of the internal structure of a waveform-coupled steel plate clutch quick self-separation device provided in an embodiment of the present invention; Figure 3 This is a schematic diagram of the transmission shaft structure of a waveform-coupled steel plate clutch quick self-separation device according to an embodiment of the present invention; Figure 4 for Figure 1 Left view of the drive shaft of the waveform-coupled steel plate clutch quick self-disengagement device provided in one embodiment; Figure 5 for Figure 4 A cross-sectional view along AA of a waveform-coupled steel plate clutch quick self-disengagement device provided in one embodiment; Figure 6 for Figure 4 A cross-sectional view along BB of a waveform-coupled steel plate clutch quick self-disengagement device provided in one embodiment; Figure 7 for Figure 4 A cross-sectional view along CC of a waveform-coupled steel plate clutch quick self-disengagement device provided in one embodiment; Figure 8 This is an exploded view of a waveform-coupled steel plate clutch quick self-disengagement device provided in an embodiment of the present invention; Figure 9This is a schematic diagram of the dual steel plate structure of a waveform dual steel plate clutch quick self-separation device provided in an embodiment of the present invention; Figure 10 This is a schematic diagram of the structure of a waveform-coupled steel plate clutch quick self-separation device provided in an embodiment of the present invention, showing adjacent coupled steel plates abutting together; Figure 11 for Figure 10 A partial enlarged view of part X of the waveform-coupled steel plate clutch quick self-disengagement device provided in one embodiment.

[0020] in: 100. Drive shaft; 110. First hydraulic flow channel; 111. First oil inlet; 112. First oil outlet; 120. Second hydraulic flow channel; 121. Second oil inlet; 122. Second oil outlet; 130. Lubricating oil flow channel; 131. Lubricating oil nozzle; 140. Telescopic end; 150. Hydraulic chamber; 160. Elastic element; 170. Clamp; 200, bushing; 210, snap-fit ​​groove; 220, abutment plate; 230, abutment piece; 300, Dual steel sheet; 310, First wave spring; 320, Second wave spring; 330, Separating groove; 400. Friction plate; 500. Gear ring. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0022] The component designations used in this document, such as "first" and "second," are merely for distinguishing the described objects and do not have any sequential or technical meaning. The terms "connection" and "linkage" used in this invention, unless otherwise specified, include both direct and indirect connections (linkages). It should be understood that the terms "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are used only for the convenience of describing the invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the invention.

[0023] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0024] The following reference Figures 1-11 This invention describes the waveform-coupled steel plate clutch quick self-separation device provided by the present invention.

[0025] A wave-shaped, dual-plate clutch quick-release device includes a drive shaft 100 and a bushing 200. The bushing 200 is coaxially and fixedly mounted on the drive shaft 100. The bushing 200 has an internal space and houses multiple friction plates 400, a gear ring 500, and dual-plates 300. All the dual-plates 300, gear ring 500, and friction plates 400 are coaxially arranged, and their axes coincide with the axes of the drive shaft 100 and the bushing 200. The multiple dual-plates 300 can move along the axis of the bushing 200. The cylinder slides but cannot rotate circumferentially. Multiple mating steel plates 300 and gear ring 500 are alternately distributed, and multiple friction plates 400 are located between gear ring 500 and mating steel plates 300. A piston cylinder is also provided inside the bushing 200. The fixed end of the piston cylinder is fixed inside the bushing 200, and the telescopic end 140 of the piston cylinder abuts against one end of the mating steel plate 300. An elastic element 160 is also provided on the telescopic end 140 of the piston cylinder. The elastic element 160 is used to reset the telescopic end 140 of the piston cylinder. When the extension end 140 of the piston cylinder pushes the mating steel plate 300, the mating steel plate 300 squeezes the friction plate 400 and the gear ring 500, so that the two ends of the friction plate 400 are tightly attached to the gear ring 500 and the mating steel plate 300. The roughness of the two end faces of the friction plate 400, combined with the pushing force of the piston cylinder, prevents the gear ring 500 and the mating steel plate 300 from rotating relative to each other. This also prevents the gear ring 500 from rotating relative to the drive shaft 100 and the bushing 200. The teeth inside the gear ring 500 are engaged with other transmission components. (Not shown in the figure) When the drive shaft 100 rotates, it drives other transmission components to rotate through the gear ring 500. When the extension end 140 of the piston cylinder is reset by the elastic element 160, the multiple mating steel plates 300, friction plates 400 and gear ring 500 lose their abutting force, so that the gear ring 500 can rotate relative to the mating steel plates 300, and thus the gear ring 500 can rotate relative to the drive shaft 100 and the bushing 200. At this time, when the drive shaft 100 rotates, it cannot drive the transmission components to rotate through the gear ring 500.

[0026] Under long-term continuous or frequent clutch operation, the friction plate 400 and the mating steel plate 300 and gear ring 500 are prone to adhesion and seizing due to factors such as high-temperature sintering, lubricating oil film failure, and impurity adhesion. Therefore, this invention uniformly arranges multiple first wave springs 310 and second wave springs 320 on the outer circumference of the mating steel plate 300. All the first wave springs 310 and second wave springs 320 are in a bent state, but in different directions. The suspended ends of the first wave springs 310 and the second wave springs 320 face opposite directions, and the first wave springs 310 and second wave springs 320 are alternately arranged. The first wave springs 310 and second wave springs 320 of adjacent mating steel plates 300 abut against each other. When the piston... When the extension end 140 of the cylinder pushes against the mating steel plate 300, multiple first wave springs 310 and second wave springs 320 are squeezed and deformed. Adjacent mating steel plates 300 approach each other to squeeze the friction plate 400 and the gear ring 500. The mating steel plate 300, the friction plate 400 and the gear ring 500 abut together. When the extension end 140 of the piston cylinder is pushed back to its original position by the elastic element 160, the first wave springs 310 and second wave springs 320 on the multiple mating steel plates 300 are reset, thereby causing the adjacent mating steel plates 300 to move away from each other. This allows the friction plate 400 and the gear ring 500 between the adjacent mating steel plates 300 to have space to separate from each other, thus preventing the friction plate 400 from sticking and seizing due to factors such as high-temperature sintering, lubricating oil film failure and impurity adhesion.

[0027] It should be noted that, in this embodiment, the first wave spring 310 and the second wave spring 320 provided on the mating steel sheet 300 can be integrally stamped and formed with the mating steel sheet 300, and the produced mating steel sheets 300 are of the same size. During the installation process, the mating steel sheet 300 can be rotated so that the first wave spring 310 and the second wave spring 320 on multiple mating steel sheets 300 abut together, without the need to produce additional elastic components so that adjacent mating steel sheets 300 can move away from each other.

[0028] Specifically, in this embodiment, the orientation of the suspended ends of the first wave spring 310 and the second wave spring 320 on the mating steel sheet 300 is as follows: Figure 9 As shown, the orientation of the suspended end of the first wave spring 310 is as indicated by arrow a, and the orientation of the suspended end of the second wave spring 320 is as indicated by arrow b.

[0029] In a further embodiment, to enable the mating steel plate 300 of the present invention to adapt to different types of clutches (i.e., clutches with different locking forces, where locking force refers to the magnitude of the locking force between the friction plate 400, the mating steel plate 300, and the gear ring 500), the contact force between the first wave spring 310 and the second wave spring 320 on the mating steel plate 300 is adjustable in this embodiment, thereby adapting to clutches with different locking forces. When the locking force of the clutch is large, the contact force between the first wave spring 310 and the second wave spring 320 needs to be appropriately increased to avoid weakening the separation effect between the first wave spring 310 and the second wave spring 320, ensuring that the first wave spring 310 and the second wave spring 320 can be reset. When the locking force of the clutch is small, the contact force between the first wave spring 310 and the second wave spring 320 can be appropriately reduced to avoid excessive energy consumption of the piston cylinder hydraulic push due to a large contact force between the first wave spring 310 and the second wave spring 320.

[0030] It should be noted that, in order to make the abutment force between the first wave spring 310 and the second wave spring 320 adjustable, while keeping the elastic coefficient of the first wave spring 310 and the second wave spring 320 constant, the size of the first wave spring 310 and the second wave spring 320 is changed to change the abutment force between them. When the size of the first wave spring 310 and the second wave spring 320 is larger, the abutment force between them is greater; when the size of the first wave spring 310 and the second wave spring 320 is smaller, the abutment force between them is smaller.

[0031] In one embodiment of the present invention, multiple dividing grooves 330 can be formed on both the first wave spring 310 and the second wave spring 320. These multiple dividing grooves 330 divide the suspended ends of the first wave spring 310 and the second wave spring 320 into multiple independent parts. These independent parts do not affect each other. When it is necessary to adjust the contact force between the first wave spring 310 and the second wave spring 320, it is only necessary to change the number of independent parts contacting each other on the first wave spring 310 and the second wave spring 320. The contact force between the first wave spring 310 and the second wave spring 320 is positively correlated with the number of independent parts of the first wave spring 310 and the second wave spring 320 that come into contact. That is, the more independent parts of the first wave spring 310 and the second wave spring 320 come into contact, the greater the contact force between the first wave spring 310 and the second wave spring 320. Conversely, the fewer independent parts of the first wave spring 310 and the second wave spring 320 come into contact, the smaller the contact force between the first wave spring 310 and the second wave spring 320.

[0032] It is understood that in this embodiment, the same specification of the mating steel sheet 300 can be adapted to clutches with different locking forces, thereby increasing the adaptability range of the mating steel sheet 300.

[0033] It should be noted that during the testing phase, the clutch quick-release device of this embodiment requires frequent adjustment of the contact force between the first wave spring 310 and the second wave spring 320 on the mating steel plate 300, that is, adjusting the number of independent contact parts of the first wave spring 310 and the second wave spring 320 on the mating steel plate 300, so as to adapt to clutches with different locking forces. After the adjustment is completed for clutches with different locking forces and after assembly and production, the number of independent contact parts of the first wave spring 310 and the second wave spring 320 on the mating steel plate 300 is no longer adjusted.

[0034] Specifically, in this embodiment, when the clutch is not working, the piston cylinder applies a certain preload to the mating steel plate 300, thereby causing the independent parts of the first wave spring 310 and the second wave spring 320 on the adjacent mating steel plates 300 to abut together, preventing the adjacent mating steel plates 300 from rotating relative to each other and causing a change in the number of independent parts of the first wave spring 310 and the second wave spring 320 in contact.

[0035] In another embodiment of the present invention, when the first wave spring 310 and the second wave spring 320 are the same size, the abutting force between the first wave spring 310 and the second wave spring 320 can also be determined by the elastic coefficient of the first wave spring 310 and the second wave spring 320. That is, when producing the mating steel sheet 300, a material with a larger or smaller elastic coefficient is used. When a material with a larger elastic coefficient is used, the elastic coefficients of the first wave spring 310 and the second wave spring 320 are larger, and the abutting force between the first wave spring 310 and the second wave spring 320 is larger; when a material with a smaller elastic coefficient is used, the elastic coefficients of the first wave spring 310 and the second wave spring 320 are smaller, and the abutting force between the first wave spring 310 and the second wave spring 320 is smaller.

[0036] Specifically, in order for the extension end 140 of the piston cylinder to push the mating steel plate 300, a hydraulic flow channel is provided on the transmission shaft 100 in this embodiment. The oil inlet of the hydraulic flow channel is close to the end of the transmission shaft 100, and the oil outlet of the hydraulic flow channel is connected to the hydraulic chamber 150 of the piston cylinder. When hydraulic oil enters the hydraulic chamber 150 of the piston cylinder through the hydraulic flow channel, the hydraulic oil pushes the extension end 140 of the piston cylinder to extend, thereby pushing the mating steel plate 300.

[0037] It should be noted that in this embodiment, there are two piston cylinders, and each of the multiple mating steel plates 300, friction plates 400, and gear rings 500 has two sets. The two sets of mating steel plates 300, friction plates 400, and gear rings 500 are symmetrically arranged within the bushing 200, as detailed below. Figure 2 and Figure 8 As shown, the two piston cylinders are also symmetrically arranged, and the telescopic ends 140 of the two piston cylinders push against the two sets of paired steel plates 300 respectively.

[0038] It should also be noted that the drive shaft 100 in this embodiment is also provided with another hydraulic flow channel. This hydraulic flow channel is used to supply hydraulic oil to the hydraulic chamber 150 of another piston cylinder. For ease of description, the two hydraulic flow channels are named the first hydraulic flow channel 110 and the second hydraulic flow channel 120, respectively. The oil inlet and oil outlet on the first hydraulic flow channel 110 are named the first oil inlet 111 and the first oil outlet 112, respectively, and the oil inlet and oil outlet on the second hydraulic flow channel 120 are named the second oil inlet 121 and the second oil outlet 122, respectively. Specifically, as shown below... Figure 2 , Figure 3 , Figure 5 and Figure 6 As shown, the first oil outlet 112 of the first hydraulic flow channel 110 is connected to the hydraulic chamber 150 of one of the piston cylinders, and the second oil outlet 122 of the second hydraulic flow channel 120 is connected to the hydraulic chamber 150 of the other piston cylinder.

[0039] In a further embodiment, the drive shaft 100 in this embodiment is also provided with a lubricating oil flow channel 130, such as... Figure 7 As shown, the lubricating oil flow channel 130 is provided with multiple lubricating oil nozzles 131, which face the inside of the bushing 200. Lubricating oil is continuously introduced into the lubricating oil flow channel 130 and sprayed into the inside of the bushing 200 through the lubricating oil nozzles 131, thereby lubricating the friction plate 400 and the gear ring 500, and the friction plate 400 and the mating steel plate 300. This reduces the friction between the friction plate 400 and the gear ring 500, and between the friction plate 400 and the mating steel plate 300 when the two mating steel plates 300 move away from each other, thereby reducing the wear between the mating steel plate 300 and the friction plate 400, and between the friction plate 400 and the gear ring 500.

[0040] In a further embodiment, the outermost mating steel plate 300 of the present invention is provided with an abutment plate 220 at its outer end. That is, the outer end of the mating steel plate 300 furthest from the piston cylinder telescopic end 140 is provided with an abutment plate 220. The abutment plate 220 is an annular disc and is fixedly disposed inside the bushing 200. One end of the abutment plate 220 is fixedly disposed inside the bushing 200, and the other end of the abutment plate 220 abuts against the mating steel plate 300. In order to make the first wave spring 310 or the second wave spring 320 on the mating steel plate 300 uniformly stressed, the outer periphery of the abutment plate 220 in this embodiment is uniformly stressed. Abutment pieces 230 are evenly provided, and the abutment pieces 230 correspond to the first wave spring piece 310 or the second wave spring piece 320. The abutment pieces 230 can abut against the first wave spring piece 310 or the second wave spring piece 320. The abutment pieces 230 have a certain thickness, so that the deformation of the multiple first wave spring pieces 310 or second wave spring pieces 320 on the outermost paired steel plate 300 is as similar as possible to the deformation of the first wave spring pieces 310 or second wave spring pieces 320 on the other paired steel plates 300, thereby making the multiple first wave spring pieces 310 and second wave spring pieces 320 on the multiple paired steel plates 300 uniformly stressed.

[0041] Specifically, in order to enable the multiple mating steel plates 300 to rotate synchronously with the bushing 200 and the drive shaft 100, the bushing 200 in this embodiment has multiple snap-fit ​​grooves 210 on its outer periphery, as shown in the figure below. Figure 1 and Figure 8As shown, the snap-fit ​​grooves 210 are evenly distributed circumferentially on the bushing 200. The number of snap-fit ​​grooves 210 is the same as the sum of the number of first wave spring pieces 310 and second wave spring pieces 320 on a single paired steel plate 300. The first wave spring pieces 310 and second wave spring pieces 320 on multiple paired steel plates 300 are all located in the corresponding snap-fit ​​grooves 210. The number of abutment pieces 230 on the abutment plate 220 is the same as the number of snap-fit ​​grooves 210. The abutment pieces 230 are also located in the snap-fit ​​grooves 210. When the drive shaft 100 drives the bushing 200 to rotate, the first wave spring pieces 310 and second wave spring pieces 320 on the paired steel plates 300 abut against the side wall of the snap-fit ​​grooves 210. The bushing 200 drives the paired steel plates 300 to rotate synchronously through the snap-fit ​​grooves 210, the first wave spring pieces 310 and the second wave spring pieces 320.

[0042] More specifically, in this embodiment, the elastic element 160 is a disc spring. One end of the disc spring is fixedly connected to the transmission shaft 100 by a clamp 170, and the other end of the disc spring abuts against the extension end 140 of the piston cylinder. When the extension end 140 of the piston cylinder extends and pushes the mating steel plate 300, it can push the disc spring at the same time. The disc spring is compressed and stores energy. When the first hydraulic channel 110 or the second hydraulic channel 120 stops supplying oil, the piston cylinder depressurizes, the disc spring is released, and thus pushes the extension end 140 of the piston cylinder to reset. At the same time, the first wave spring 310 and the second wave spring 320 on the multiple mating steel plates 300 also reset, thereby pushing the adjacent mating steel plates 300 away from each other.

[0043] The specific working process of the waveform-coupled steel plate clutch quick self-disengagement device provided by the present invention will be described in conjunction with the above embodiments: When assembling the mating steel plates 300, adjust the number of independent parts abutting on the first wave spring 310 and the second wave spring 320 on adjacent mating steel plates 300 according to the locking force of the clutch, so that the abutting force between the first wave spring 310 and the second wave spring 320 is adapted to the locking force of the clutch. If the pushing force of the piston cylinder is large, the number of independent parts abutting on the first wave spring 310 and the second wave spring 320 can be increased; if the pushing force of the piston cylinder is small, the number of independent parts abutting on the first wave spring 310 and the second wave spring 320 can be reduced.

[0044] The transmission component (not shown in the figure) rotates synchronously with the transmission shaft 100: Hydraulic oil in the first hydraulic channel 110 and the second hydraulic channel 120 enters the hydraulic chamber 150 of the piston cylinder, thereby pushing the extension end 140 of the piston cylinder to extend. The extension end 140 of the piston cylinder pushes the elastic element 160 to compress it while simultaneously pushing the mating steel plate 300, increasing the deformation of the first wave spring 310 and the second wave spring 320 on the adjacent mating steel plates 300, reducing the distance between the adjacent mating steel plates 300, and simultaneously increasing the distance between the mating steel plates 300, the friction plate 400, and the gear ring 500. Lubricating oil is squeezed out, and the mating steel plate 300, friction plate 400 and gear ring 500 abut against each other. The thrust of the piston cylinder and the rough end faces of the friction plate 400 prevent the mating steel plate 300 and gear ring 500 from rotating relative to each other. When the transmission shaft 100 drives the bushing 200 to rotate, the first wave spring 310 and the second wave spring 320 on the mating steel plate 300 abut against the side wall of the snap groove 210, driving the gear ring 500 to rotate synchronously, thereby causing the gear ring 500 to drive the transmission components to rotate synchronously.

[0045] The transmission component does not rotate synchronously with the transmission shaft 100: The hydraulic oil supply in the first hydraulic flow channel 110 and the second hydraulic flow channel 120 stops, the piston cylinder is depressurized, the elastic element 160 resets and pushes the extension end 140 of the piston cylinder to shorten. At the same time, the first wave spring 310 and the second wave spring 320 on the mating steel plate 300 also reset, thereby pushing the adjacent mating steel plates 300 away from each other, increasing the space between the adjacent mating steel plates 300, so that the friction plate 400 and the gear ring 500 have space to disengage from each other, and the lubricating oil can lubricate the friction plate 400, the gear ring 500 and the mating steel plate 300, thereby reducing the wear between the friction plate 400, the gear ring 500 and the mating steel plate 300. After the friction plate 400, the gear ring 500 and the mating steel plate 300 disengage, the transmission shaft 100 cannot drive the transmission component to rotate through the mating steel plate 300.

[0046] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0047] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A rapid self-disengagement device for a wave-shaped dual steel plate clutch, characterized in that, include: A drive shaft and a bushing, wherein the bushing is coaxial and fixedly mounted on the drive shaft, and a plurality of friction plates, a gear ring and a mating steel plate are provided inside the bushing, wherein the mating steel plate and the gear ring are alternately arranged, and the friction plates are located between the mating steel plate and the gear ring; A piston cylinder is disposed within the bushing, and the telescopic end of the piston cylinder abuts against the end of the mating steel plate away from the friction plate. An elastic element is also provided on the telescopic end of the piston cylinder. Multiple first wave springs and second wave springs are uniformly arranged on the outer periphery of the dual steel sheet. The suspended end of the first wave spring and the suspended end of the second wave spring face opposite directions. The first wave spring and the second wave spring are arranged alternately, and the first wave spring and the second wave spring of adjacent dual steel sheets abut against each other. The contact force between the first and second wave springs of adjacent paired steel plates is positively correlated with the locking force of the clutch; The first and second wave springs are each provided with multiple dividing grooves. The multiple dividing grooves divide the suspended end of the first and second wave springs into multiple independent parts. The contact force between the first and second wave springs is positively correlated with the number of independent parts of the first and second wave springs that contact each other. When the clutch is not engaged, the piston cylinder applies a certain preload to the mating steel plates, thereby causing the independent parts of the first and second wave springs on the adjacent mating steel plates to abut together, preventing the relative rotation of the adjacent mating steel plates from causing a change in the number of contacting independent parts of the first and second wave springs.

2. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The contact force between the first and second wave springs of the adjacent paired steel sheets is positively correlated with the elastic coefficients of the first and second wave springs.

3. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The drive shaft has a hydraulic flow channel, which is connected to the hydraulic chamber of the piston cylinder.

4. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The drive shaft has a lubricating oil channel, and the lubricating oil channel has multiple lubricating oil nozzles, which face inwards towards the bushing.

5. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, An abutment plate is fixedly provided inside the bushing. The abutment plate is located at the outer end of the outermost mating steel plate. An abutment piece is provided on the outer periphery of the abutment plate corresponding to the position of the first wave spring and the second wave spring. The abutment piece abuts against the first wave spring and the second wave spring.

6. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The bushing has multiple snap-fit ​​grooves evenly distributed around its outer circumference. The number of snap-fit ​​grooves is the same as the total number of first and second wave spring pieces on a single paired steel sheet. The first and second wave spring pieces of the paired steel sheet are located in the corresponding snap-fit ​​grooves.

7. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The elastic element is a disc spring, one end of which is fixed to the drive shaft by a clamp, and the other end abuts against the extension and retraction end of the piston cylinder.

8. The waveform-coupled steel plate clutch quick self-disengagement device according to claim 1, characterized in that, The first and second wave spring sheets are integrally stamped with the paired steel sheet.

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