Dual mass flywheel

Abstract

A dual mass flywheel comprising: a first mass flywheel (10); the second mass flywheel (20) is arranged on one side of the first mass flywheel (10) in the axial direction (A), and an accommodating space is formed by the second mass flywheel (20) and the first mass flywheel (10); the damping mechanism (30) is located in the containing space, and the damping mechanism (30) comprises a flange plate (31); the supporting assembly comprises a radial supporting part (80), and the radial supporting part (80) is supported on the radial inner side of the flange plate (31); the radial outer side of the diaphragm spring (40) abuts against the first mass flywheel (10), the middle of the diaphragm spring (40) is clamped between the second mass flywheel (20) and the flange plate (31), and the radial inner side of the diaphragm spring (40) extends to the radial inner side of the radial supporting part (80).

Description

dual-mass flywheel Technical Field

[0001] The present invention relates to the technical field of vehicle shock absorption, and in particular to a dual-mass flywheel. Background Art

[0002] In related technologies, a diaphragm spring is often provided in a dual-mass flywheel. The diaphragm spring is a metal elastic structure that can provide axial force. The diaphragm spring is often provided between the first mass flywheel and the second mass flywheel. The diaphragm spring can play the role of compression, separation and sealing.

[0003] However, there is a possibility that the grease in the flywheel spring will flow from the spring cavity to the middle position of the flange. Since the dual-mass flywheel is used in a high-speed rotation environment and is prone to radial movement under the action of centrifugal force, the lubricating oil may leak along the gap between the diaphragm spring and the second mass flywheel.

[0004] Summary of the Invention

[0005] In order to overcome the problems existing in the related art, the present disclosure provides a dual mass flywheel.

[0006] According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a dual-mass flywheel, comprising: a first mass flywheel; a second mass flywheel, axially arranged on one side of the first mass flywheel, and forming a housing space with the first mass flywheel; a shock absorbing mechanism, located in the housing space, the shock absorbing mechanism comprising a flange; a support assembly, comprising a radial support portion, the radial support portion being supported on the radial inner side of the flange; and a diaphragm spring, the radial outer side of the diaphragm spring abutting the first mass flywheel, the middle part of the diaphragm spring being sandwiched between the second flywheel mass and the flange, wherein the radial inner side of the diaphragm spring extends to the radial inner side of the radial support portion.

[0007] In some embodiments, the second mass flywheel is bent along the axial direction and in a direction away from the first mass flywheel, and then bent radially inward to form a first bent portion;

[0008] A second bending portion is provided on the radial inner side of the diaphragm spring, and the second bending portion is bent along the bending direction of the first bending portion of the second mass flywheel.

[0009] In some embodiments, the diaphragm spring is bent toward the first mass flywheel to form an anti-overflow baffle, and the anti-overflow baffle is located radially inward of the radial support portion.

[0010] In some embodiments, the dual mass flywheel further includes: a first support plate, part or all of which is located between the first mass flywheel and the flange, for axially supporting the flange; a second support plate, located radially inwardly of the first support plate, for radially supporting the first support plate, the second support plate being fixedly connected to the axial inner side of the first mass flywheel; wherein the first support plate or the second support plate extends axially to form the radial support portion.

[0011] In some embodiments, the diaphragm spring further includes a radial portion, the radial portion is connected to an end of the anti-overflow baffle close to the first mass flywheel, and the radial portion extends radially outward to form an anti-overflow groove with the anti-overflow baffle.

[0012] In some embodiments, the first mass flywheel includes a first housing and a cover plate; wherein the first housing and the cover plate are arranged axially, and the radial outer side of the cover plate is torsionally connected to the radial outer side of the first housing, and the radial inner side of the cover plate abuts against the radial outer side of the diaphragm spring.

[0013] In some embodiments, the dual mass flywheel further includes a first friction ring disposed between a radially outer side of the diaphragm spring and a radially inner side of the cover plate.

[0014] In some embodiments, the shock absorbing mechanism further includes an arc-shaped flywheel spring, a spring cavity is formed between the first shell and the cover plate, the flywheel spring is installed in the spring cavity and abuts against the flange.

[0015] The technical solution provided by the embodiments of the present disclosure may include the following beneficial effects: the radial inner side of the diaphragm spring is closer to the rotation center axis of the dual-mass flywheel than the radial inner side of the flange, which can avoid the overflow of lubricating grease in the accommodating space. Furthermore, the anti-overflow baffle formed by the diaphragm spring toward the first mass flywheel can not only collect the lubricating grease, but also return the lubricating grease to the accommodating space under the action of centrifugal force, thereby avoiding the lubricating grease from overflowing from the gap between the diaphragm spring and the second mass flywheel. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0017] FIG1 is a schematic cross-sectional view of a dual-mass flywheel according to a first exemplary embodiment;

[0018] FIG2 is a partial enlarged view of portion A in FIG1 ;

[0019] FIG3 is a perspective structural diagram of a diaphragm spring shown in a first exemplary embodiment;

[0020] FIG4 is a schematic cross-sectional view of a dual mass flywheel shown in a second exemplary embodiment;

[0021] FIG5 is a partial enlarged view of portion B in FIG4 ;

[0022] FIG6 is a perspective structural diagram of a diaphragm spring shown in a second exemplary embodiment;

[0023] 7 to 10 are schematic diagrams showing the positional relationship between the radial support portion formed by the second support plate and the diaphragm spring;

[0024] 11 to 16 are schematic diagrams showing the positional relationship between the radial support portion formed by the first support plate and the diaphragm spring. DETAILED DESCRIPTION

[0025] Exemplary embodiments will be described in detail herein, with examples illustrated in the accompanying drawings. In the following description, when referring to the drawings, identical numerals in different figures represent identical or similar elements, unless otherwise indicated. The embodiments described in the following exemplary embodiments are not intended to represent all possible embodiments consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present disclosure, as detailed in the appended claims.

[0026] In the present invention, unless otherwise specified, the axial direction A, radial direction R and circumferential direction refer to the axial direction A, radial direction R and circumferential direction of the dual mass flywheel respectively; one axial side refers to the left side in Figures 1 and 4 (for example, the side where the power source is located), and the other axial side refers to the right side in Figures 1 and 4 (for example, the side where the transmission is located); the radial outer side refers to the side away from the rotation center axis O in Figure 1 in the radial direction R (the upper side in Figure 1), and the radial inner side refers to the side close to the rotation center axis O in the radial direction R (the lower side in Figure 1).

[0027] Furthermore, a "transmission connection" refers to the ability to transmit driving force / torque between two components. This can be achieved by direct connection or through various transmission mechanisms or connection structures. A "torsion-resistant connection" refers to the ability to transmit torque between two components. Torque-resistant connection methods can include interference fits and bolted connections.

[0028] In order to solve the above technical problems, the present disclosure provides a dual-mass flywheel, as shown in Figures 1 to 6, the dual-mass flywheel includes a first mass flywheel 10 (also known as the main flywheel mass), a second mass flywheel 20 (also known as the secondary flywheel mass), a shock absorbing mechanism 30 and a diaphragm spring 40.

[0029] The engine crankshaft is connected to a drive system (e.g., a transmission) via a dual-mass flywheel. The first-mass flywheel 10 of the dual-mass flywheel is connected to the engine crankshaft, while the second-mass flywheel 20 is connected to the transmission system. A damping mechanism 30 is installed between the transmission paths of the first-mass flywheel 10 and the second-mass flywheel 20. The first-mass flywheel 10 is in transmission connection with the second-mass flywheel 20 via the damping mechanism 30. When the engine is running, the first-mass flywheel 10 rotates. The damping mechanism 30 transmits the rotation of the first-mass flywheel 10 to the second-mass flywheel 20, which then transmits the rotation to the transmission.

[0030] The second mass flywheel 20 is arranged along the axial direction A on the other axial side of the first mass flywheel 10 (the right side as shown in Figure 1) and forms an annular accommodating space with the first mass flywheel 10; the shock absorbing mechanism 30 is located in the accommodating space to achieve the effect of attenuating the torsional vibration between the engine crankshaft and the input shaft of the transmission.

[0031] Specifically, the first mass flywheel 10 includes a first shell 11 and a cover plate 12; wherein, the first shell 11 and the cover plate 12 are arranged along the axial direction A, the first shell 11 is cylindrical, and the cover plate 12 is annular. As shown in Figure 1, the cover plate 12 is located on the right side of the first shell 11, and the radial outer side of the cover plate 12 is torsionally connected to the radial outer side of the first shell 11. The radial R dimension of the cover plate 12 is smaller than the radial R dimension of the first shell 11, so a spring cavity is formed between the cover plate 12 and the first shell 11. The spring cavity is annular and is part of the accommodating space.

[0032] Furthermore, the shock-absorbing mechanism 30 includes a flange 31 and a flywheel spring 32. The flywheel spring 32 is arc-shaped and can be a helical arc spring. Two flywheel springs 32 can be provided (for example only). The two flywheel springs 32 are arranged at equal intervals along the circumference of the dual-mass flywheel within the spring cavity, with adjacent flywheel springs 32 separated by a circumferential gap. In other embodiments, the flywheel springs 32 can be provided in three or four configurations, which are not specifically limited herein.

[0033] The flange 31 may include a base circular portion 311 and flange wings (also known as flange lugs) extending radially outward from the base circular portion 311. The base circular portion 311 is located within the accommodating space, and the flange wings extend into the spring cavity and into the circumferential gap between the two flywheel springs 32. Therefore, within the spring cavity, the circumferential ends of the flywheel springs 32 abut against the flange wings of the flange 31. When the first mass flywheel 10 rotates, the first mass flywheel 10 and the flange 31 rotate at different times, squeezing the flywheel spring 32. The flywheel spring 32 drives the flange 31 and the second mass flywheel 20 to rotate via the flange wings of the flange 31, thereby transmitting torque and attenuating torsional vibration.

[0034] Furthermore, the dual mass flywheel further includes a support assembly, which includes a radial support portion 80 . The radial support portion 80 is located radially inward of the flange 31 and is used to radially R support the base circle portion 311 of the flange 31 .

[0035] Furthermore, the radial outer side of the diaphragm spring 40 abuts against the radial inner side of the cover plate 12 of the first mass flywheel 10, and the middle part of the diaphragm spring 40 is clamped between the second flywheel mass and the base circle 311 of the flange 31. The base circle 311 of the flange 31, the middle part of the diaphragm spring 40 and the second mass flywheel 20 are fixedly connected in the axial direction A by bolts, thereby achieving the closure of the accommodating space by the diaphragm spring 40 to prevent external impurities such as water, dust, sand and gravel from entering the accommodating space.

[0036] The radial inner side of the diaphragm spring 40 extends to the radial inner side of the flange 31 (as shown in FIG. 1 to FIG. 3 ). Furthermore, the radial inner side of the diaphragm spring 40 extends to the radial inner side of the radial support portion 80 .

[0037] Specifically, the radial inner side of the diaphragm spring 40 is closer to the rotational axis O of the dual mass flywheel than the radial inner side of the base circle 311 of the flange 31 and the radial inner side of the radial support portion 80. That is, the inner diameter of the diaphragm spring 40 is smaller than the inner diameters of the base circle 311 and even the radial inner side of the radial support portion 80. When grease in the spring cavity overflows into the accommodating space and bypasses the radial inner side of the flange 31 to reach the diaphragm spring 40, the radial inner side of the diaphragm spring 40, being closer to the rotational axis O, prevents the grease from bypassing the radial inner side of the diaphragm spring 40 and reaching the axial outer side of the diaphragm spring 40. This prevents the grease from overflowing from the gap between the diaphragm spring 40 and the second mass flywheel 20, thus preventing wear between the damping mechanism 30 and the first mass flywheel 10 or the flange wing of the flange 31 due to insufficient grease, and thus preventing insufficient damping.

[0038] Furthermore, the radial inner side of the diaphragm spring 40 continues to bend toward the first mass flywheel 10 to form an anti-overflow baffle 41, and the anti-overflow baffle 41 is further located on the radial inner side of the flange 31 and the radial support portion 80. In addition, along the axial direction A, the anti-overflow baffle 41 can extend axially and extend over the side of the flange 31 close to the first mass flywheel 10, so that the width of the anti-overflow baffle 41 can be greater than the width of the base circle 311 of the flange 31.

[0039] The width of the anti-overflow baffle 41 is greater than the width of the base circle 311 of the flange 31, so that the anti-overflow baffle 41 can receive as much lubricating grease as possible in the axial direction and increase the path distance of the lubricating grease to the diaphragm spring 40.

[0040] In addition, the overflow baffle 41 can be parallel to the rotation center axis O, or it can be set at an angle to the rotation center axis O. When the overflow baffle 41 is set at an angle, the inner diameter of the end of the overflow baffle 41 close to the first mass flywheel 10 is larger than the inner diameter of the end of the overflow baffle 41 close to the second mass flywheel 20.

[0041] In this way, when the lubricating grease that bypasses the radial inner side of the base circle 311 of the flange 31 continues to flow along the axial inner side of the diaphragm spring 40 toward the rotation center axis O, the anti-overflow baffle 41 can prevent the lubricating grease from continuing to flow toward the rotation center axis O, and when the dual-mass flywheel rotates at high speed, under the action of centrifugal force, the lubricating grease gathered at the anti-overflow baffle 41 is thrown back to the accommodating space or spring cavity along the axial inner side of the diaphragm spring 40, thereby avoiding leakage of the lubricating grease and realizing the recycling of the lubricating grease.

[0042] As can be seen from the above, the radial inner side of the diaphragm spring 40 extends to the radial inner side of the flange 31, which can prevent the lubricating grease in the accommodating space from overflowing. Furthermore, the anti-overflow baffle 41 formed by the diaphragm spring 40 toward the first mass flywheel 10 can not only collect the lubricating grease, but also return the lubricating grease to the accommodating space or spring cavity under the action of centrifugal force, thereby preventing the lubricating grease from overflowing from the gap between the diaphragm spring 40 and the second mass flywheel 20.

[0043] In some embodiments, as shown in FIG. 1 and FIG. 4 , the second mass flywheel 20 is bent along the axial direction A and in a direction away from the first mass flywheel 10 , and then bent radially inward to form a first bent portion 21 .

[0044] In some embodiments, the radial inner side of the diaphragm spring 40 may directly extend along the radial direction R. The diaphragm spring 40 of this structure has a simple structure and manufacturing process.

[0045] In other embodiments, a second bend 42 is provided on the radially inner side of the diaphragm spring 40. The second bend 42 bends along the bend direction of the first bend 21 of the second mass flywheel 20. That is, the diaphragm spring 40 extends along the inner wall of the second mass flywheel 20. Therefore, the diaphragm spring 40 also bends correspondingly at the first bend 21 of the second mass flywheel 20 to form the second bend 42. The radially inner dimension of the second bend 42 is also smaller than the radially inner dimension of the radial support portion 80.

[0046] In this way, the close fit between the diaphragm spring 40 and the second mass flywheel 20 increases the length of the diaphragm spring 40, preventing grease that overflows into the accommodation space and bypasses the radially inner side of the flange 31 from being thrown out of the gap between the diaphragm spring 40 and the second mass flywheel 20 by centrifugal force. As a result, the grease can only flow back along the inner wall of the diaphragm spring 40. In addition, when some grease overflows between the diaphragm spring 40 and the second mass flywheel 20, the diaphragm spring 40 bends and fits the second mass flywheel 20, increasing the length of the gap between the diaphragm spring 40 and the second mass flywheel 20. This is equivalent to increasing the length of the grease overflow path. The bent diaphragm spring 40 also increases the resistance of the grease, further preventing the grease from overflowing.

[0047] It should be noted that regardless of whether the diaphragm spring 40 forms the second bent portion 42, the diaphragm spring 40 can be further bent along the axial direction A to form the anti-overflow baffle 41. That is, after the radial inner side of the diaphragm spring 40 extends past the radial support portion 80, it can be directly bent along the axial direction A to form the anti-overflow baffle 41 (as shown in Figures 4, 5, 9, 10, 15, and 16). Alternatively, after the radial inner side of the diaphragm spring 40 is bent to form the second bent portion 42, it can be further bent along the axial direction A to form the anti-overflow baffle 41 (as shown in Figures 2 and 12).

[0048] Furthermore, the support assembly includes a first support plate 70 and a second support plate 50. The radial support portion 80 can be formed by the first support plate 70 (as shown in Figures 11 to 16) or by the second support plate 50 (as shown in Figures 1 to 10). Part or all of the first support plate 70 is located between the first mass flywheel 10 and the flange 31. The first support plate 70 and the second flange 20 work together to axially support the flange 31 and prevent it from moving in the axial direction A.

[0049] The second support plate 50 is located radially inward of the first support plate 70, providing radial support for the first support plate 70. The second support plate 50 is fixedly connected axially inwardly to the first mass flywheel 10, reinforcing the axial strength of the first mass flywheel. Therefore, the first support plate 70 is typically made of nylon, while the second support plate 50 is typically made of metal.

[0050] The present invention will be described in detail below with reference to the specific structures of the first support plate 70 and the second support plate 50 in the first embodiment. In the exemplary embodiment of the present disclosure, the second support plate 50 forms a radial support portion 80 .

[0051] Specifically, as shown in Figures 2, 4, and 5, the second support plate 50 includes a first axial plate 51, a first radial plate 52, and a second radial plate 53. In some embodiments, the second support plate 50 is an integrally formed structure. The second support plate 50 can be made of a metal material and integrally formed through a process such as stamping or casting. The integrally formed second support plate 50 saves material, reduces processing steps, and improves the overall strength of the second support plate 50.

[0052] Furthermore, the first axial plate 51 serves as a radial support portion 80 for radially supporting the radially inner side of the flange 31. The first axial plate 51 is located between the radially inner side of the flange 31 and the anti-overflow baffle 41 of the diaphragm spring 40. In the disclosed embodiment, the first axial plate 51 is arranged parallel to the rotational axis O and perpendicular to the first radial plate 52 and the second radial plate 53. In other embodiments, the first axial plate 51 may be arranged at an angle or in a wavy shape, which are not specifically limited here.

[0053] Furthermore, the first radial plate 52 extending radially outward and the first axial plate 51 form a bend that can accommodate lubricating grease. When the lubricating grease bypasses the radial inner side of the flange 31, it is first stored in the bend of the first radial plate 52 and the first axial plate 51, forming a first barrier to prevent the grease from overflowing. Only when the lubricating grease bypasses the radial outer side of the first radial plate 52 can it enter the anti-overflow baffle 41 of the diaphragm spring 40.

[0054] Furthermore, when the second radial plate 53 is provided, the second radial plate 53 may extend radially outward or radially inward. In this embodiment, the second radial plate 53 extends radially inward and is torsionally connected to the first housing 11 of the first mass flywheel 10 via fasteners.

[0055] In this way, the second support plate 50 is torsionally connected to the first mass flywheel 10 through the second radial plate 53. The structural arrangement of the first axial plate 51 and the first radial plate 52 of the second support plate 50 can further prevent the lubricating grease from bypassing the radial inner side of the flange 31 and flowing to the diaphragm spring 40, and can store the lubricating grease.

[0056] In addition, the anti-overflow baffle 41 can be in contact with the first axial plate 51 of the support plate (as shown in FIG. 1 and FIG. 2 ), or can be spaced apart by a certain distance in the radial direction, which is not specifically limited here.

[0057] In other embodiments, the diaphragm spring 40 further includes a radial portion (not shown in the figure), which is connected to one end of the anti-overflow baffle 41 close to the first mass flywheel 10, and the radial portion extends radially outward to form an anti-overflow groove with the anti-overflow baffle 41.

[0058] Specifically, the radial portion orients the opening of the anti-overflow groove toward the first axial plate 51 of the support plate 50. This further prevents grease from flowing toward the rotational axis O of the dual-mass flywheel, thereby preventing grease from overflowing from the gap between the diaphragm spring 40 and the second-mass flywheel 20. Furthermore, the anti-overflow groove formed by the radial plate and the anti-overflow baffle 41 can better store grease. Under the centrifugal force of high-speed rotation, the grease stored in the anti-overflow groove is flung back into the spring cavity.

[0059] In some embodiments, the dual mass flywheel further includes a first friction ring 60 , which is disposed between the radially outer side of the diaphragm spring 40 and the radially inner side of the cover plate 12 .

[0060] Among them, it can be seen from the above content that the diaphragm spring 40 is torsionally connected to the second mass flywheel 20. When the first mass flywheel 10 drives the second mass flywheel 20 to rotate, there is relative rotation between the first mass flywheel 10 and the second mass flywheel 20, and the radial outer side of the diaphragm spring 40 and the radial inner side of the cover plate 12 will also produce relative rotation. The first friction ring 60 can be made of plastic material. In this way, the first friction ring 60 can not only avoid friction between the diaphragm spring 40 and the cover plate 12, but also adjust the axial gap between the radial outer side of the diaphragm spring 40 and the radial inner side of the cover plate 12, thereby preventing external water, dust, gravel, etc. from entering the accommodation space, making the accommodation space more sealed.

[0061] It is understood that in this disclosure, "plurality" refers to two or more than two, and other quantifiers are similar. "And / or" describes the association relationship of related objects, indicating that three relationships may exist. For example, A and / or B can mean: A exists alone, A and B exist at the same time, and B exists alone. The character " / " generally indicates that the related objects before and after are in an "or" relationship. The singular forms "a", "the" and "the" are also intended to include the plural forms, unless the context clearly indicates otherwise.

[0062] It will be further understood that the terms "first," "second," and the like are used to describe various structures, but these structures should not be limited to these terms. These terms are merely used to distinguish structures of the same type from one another and do not indicate a particular order or degree of importance. In fact, the expressions "first," "second," and the like are fully interchangeable. For example, a first structure could also be referred to as a second structure, and similarly, a second structure could also be referred to as a first structure without departing from the scope of this disclosure.

[0063] It can be further understood that the terms "center", "longitudinal", "lateral", "front", "back", "up", "down", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this embodiment and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation.

[0064] It is further understood that, unless otherwise specified, “connection” includes a direct connection where there are no other components between the two elements, and also includes an indirect connection where there are other elements between the two elements.

[0065] It is further understood that although operations are described in a particular order in the drawings in the embodiments of the present disclosure, this should not be construed as requiring that the operations be performed in the particular order shown or in a serial order, or that all of the operations shown be performed to obtain the desired results. In certain circumstances, multitasking and parallel processing may be advantageous.

[0066] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of the present disclosure that follow the general principles of the present disclosure and include common knowledge or customary techniques in the art not disclosed herein. The description and examples are to be considered merely as exemplary, and the true scope and spirit of the present disclosure are indicated by the following claims.

[0067] It should be understood that the present disclosure is not limited to the exact structures described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A dual mass flywheel, characterized in that: include: a first mass flywheel (10); a second mass flywheel (20) arranged on one side of the first mass flywheel (10) in the axial direction (A) and forming an accommodation space with the first mass flywheel (10); A shock absorbing mechanism (30) is located in the accommodation space, and the shock absorbing mechanism (30) includes a flange (31); A support assembly includes a radial support portion (80), wherein the radial support portion (80) is supported on the radial inner side of the flange (31); and a diaphragm spring (40), wherein the radial outer side of the diaphragm spring (40) abuts against the first mass flywheel (10), and the middle part of the diaphragm spring (40) is sandwiched between the second flywheel mass and the flange (31), The radial inner side of the diaphragm spring (40) extends to the radial inner side of the radial support portion (80).

2. The dual mass flywheel according to claim 1, characterized in that The second mass flywheel (20) is bent along the axial direction (A) and in a direction away from the first mass flywheel (10), and then bent radially inward to form a first bent portion (21); A second bending portion (42) is provided on the radial inner side of the diaphragm spring (40), and the second bending portion (42) is bent along the bending direction of the first bending portion (21) of the second mass flywheel (20).

3. The dual mass flywheel according to claim 1 or 2, characterized in that The diaphragm spring (40) is bent toward the first mass flywheel (10) to form an anti-overflow baffle (41), and the anti-overflow baffle is located radially inside the radial support portion.

4. The dual mass flywheel according to claim 1, characterized in that The support assembly further comprises: a first support plate (70), wherein a portion or the entirety of the first support plate (70) is located between the first mass flywheel (10) and the flange (31), and is used to axially support the flange (31); a second support plate (50) located radially inward of the first support plate (70) and used for radially supporting the first support plate (70), the second support plate (50) being fixedly connected to the axial inner side of the first mass flywheel (10); Wherein, the first support plate (70) or the second support plate (50) extends along the axial direction (A) to form the radial support portion.

5. The dual mass flywheel according to claim 1, characterized in that The diaphragm spring (40) further comprises a radial portion, the radial portion being connected to one end of the anti-overflow baffle (41) close to the first mass flywheel (10), and the radial portion extending radially outward to form an anti-overflow groove with the anti-overflow baffle (41).

6. The dual mass flywheel according to claim 1, characterized in that The first mass flywheel (10) comprises a first housing (11) and a cover plate (12); The first shell (11) and the cover plate (12) are arranged along the axial direction (A), and the radial outer side of the cover plate (12) is torsionally connected to the radial outer side of the first shell (11), and the radial inner side of the cover plate (12) abuts against the radial outer side of the diaphragm spring (40).

7. The dual mass flywheel according to claim 6, characterized in that The dual mass flywheel further comprises a first friction ring (60), which is arranged between the radial outer side of the diaphragm spring (40) and the radial inner side of the cover plate (12).

8. The dual mass flywheel according to claim 1, characterized in that The shock absorbing mechanism (30) further comprises an arc-shaped flywheel spring (32); a spring cavity is formed between the first housing (11) and the cover plate (12); the flywheel spring (32) is installed in the spring cavity and abuts against the flange (31).

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