dual-mass flywheel

Abstract

The present invention relates to a dual-mass flywheel, comprising: a first mass flywheel; a second mass flywheel which is arranged in the axial direction on one side of the first mass flywheel and forms a receiving space with the first mass flywheel; a damping device which is located in the receiving space, wherein the damping device comprises a flange; a support arrangement which comprises a radial support section, wherein the radial support section is supported on the radially inner side of the flange; and a diaphragm spring, wherein the radially outer side of the diaphragm spring bears against the first mass flywheel, wherein the central part of the diaphragm spring is arranged between the second mass flywheel and the flange, and wherein the radially inner side of the diaphragm spring extends to the radially inner side of the radial support section.The radially extended diaphragm spring can block and collect grease and cause the grease to be returned to the receiving space under the action of centrifugal force, thereby preventing grease leakage through the gap between the diaphragm spring and the second mass flywheel.

Description

Technical area

[0001] The present invention relates to the field of vehicle damping technology, in particular it relates to a dual-mass flywheel. Background of the invention

[0002] In the relevant technology, diaphragm springs are often used in dual-mass flywheels. Diaphragm springs are metallic elastic structures that can provide axial force. Diaphragm springs are often arranged between the first and second mass flywheels and can perform pressure, separating, and sealing functions.

[0003] However, there is a possibility that the grease in the flywheel spring could flow from the spring chamber into the center of the flange. Because dual-mass flywheels are used in high-speed environments, the grease moves slightly radially under the influence of centrifugal force, potentially leaking along the gap between the diaphragm spring and the second mass flywheel. Subject of the invention

[0004] To overcome the problems existing in the prior art, the present disclosure provides a dual mass flywheel.

[0005] According to a first aspect of embodiments of the present disclosure, a dual-mass flywheel is provided, comprising: a first mass flywheel; a second mass flywheel arranged in the axial direction on one side of the first mass flywheel and forming a receiving space with the first mass flywheel; a damping device located in the receiving space, wherein the damping device comprises a flange; a support assembly comprising a radial support portion, wherein the radial support portion is supported on the radially inner side of the flange; and a diaphragm spring, wherein the radially outer side of the diaphragm spring abuts the first mass flywheel, wherein the central part of the diaphragm spring is arranged between the second mass flywheel and the flange, wherein the radially inner side of the diaphragm spring extends to the radially inner side of the radial support portion.

[0006] In some embodiments, the second mass flywheel is bent axially and away from the first mass flywheel and then bent radially inward to form a first bent portion; wherein the radially inner side of the diaphragm spring is provided with a second bent portion, the second bent portion being bent in the bending direction of the first bent portion of the second mass flywheel.

[0007] In some embodiments, the diaphragm spring is bent toward the first mass flywheel to form an overflow protection plate, wherein the overflow protection plate is located on the radially inner side of the radial support portion.

[0008] In some embodiments, the dual mass flywheel further comprises: a first support plate, wherein the first support plate is located wholly or partially between the first mass flywheel and the flange to axially support the flange; a second support plate located on the radially inner side of the first support plate to radially support the first support plate, wherein the second support plate is fixedly connected to the axially inner side of the first mass flywheel; wherein the first support plate or the second support plate forms an axially extended portion to form the radial support portion.

[0009] In some embodiments, the diaphragm spring further comprises a radial portion connected to an end of the spill protection plate closer to the first mass flywheel, and wherein the radial portion extends radially outward and forms an spill protection groove with the spill protection plate.

[0010] In some embodiments, the first mass flywheel comprises a first housing and a cover plate; wherein the first housing and the cover plate are arranged in an axial direction, and wherein the radially outer side of the cover plate is non-rotatably connected to the radially outer side of the first housing, and the radially inner side of the cover plate abuts the radially outer side of the diaphragm spring.

[0011] In some embodiments, the dual mass flywheel further comprises a first friction ring provided between the radially outer side of the diaphragm spring and the radially inner side of the cover plate.

[0012] In some embodiments, the damping device further comprises arcuate flywheel springs, wherein a spring chamber is formed between the first housing and the cover plate, wherein the flywheel springs are mounted in the spring chamber and abut against the flange.

[0013] The technical solutions provided in the embodiments of the present disclosure may include the following advantageous effects: The radially inner side of the diaphragm spring is closer to the rotation axis of the dual-mass flywheel than the radially inner side of the flange, thereby preventing grease from overflowing from the receiving space. Furthermore, the overflow prevention plate formed by the diaphragm spring toward the first mass flywheel can not only capture grease but also cause the grease to return to the receiving space under the action of centrifugal force, thereby preventing grease from leaking through the gap between the diaphragm spring and the second mass flywheel. Image description

[0014] The accompanying drawings, which are incorporated in and form a part of the specification, illustrate an embodiment according to the disclosure and, together with the description, serve to explain the principle of the disclosure. Fig. 1 is a schematic sectional view of a dual-mass flywheel according to a first exemplary embodiment; Fig. 2 is a local enlarged view of part A in Fig. 1; Fig. 3 is a perspective structural view of the diaphragm spring according to the first exemplary embodiment; Fig. 4 is a schematic sectional view of a dual-mass flywheel according to a second exemplary embodiment; Fig. 5 is a local enlarged view of part B in Fig. 4; Fig. 6 is a perspective structural view of the diaphragm spring according to the second embodiment; Fig. 7 to 10 are schematic representations of the positional relationship between the second support plate constituting a radial support portion and the diaphragm spring; Fig. 11 to 16 are schematic representations of the positional relationship between the first support plate forming a radial support portion and the diaphragm spring. Detailed embodiments

[0015] Exemplary embodiments are described in detail below, as shown by way of example in the accompanying drawings. When the following description refers to the accompanying drawings, the same numerals refer to the same or similar elements in different drawings unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments in accordance with the disclosure. Rather, they are merely examples of an apparatus and method in accordance with some aspects of the disclosure, as recited in the appended claims.

[0016] In the present invention, unless otherwise stated, axial direction A, radial direction R and circumferential direction respectively refer to the axial direction A, the radial direction R and the circumferential direction of the dual mass flywheel; an axial side refers to the left side in the Fig. 1 and Fig. 4 (e.g. the side where the power source is located), and the other axial side refers to the right side in the Fig. 1 and Fig. 4 (e.g. the side on which the gearbox is located); the radially outer side refers to the side which is in the radial direction R from the axis of rotation O in Fig. 1 is removed (the upper side in Fig. 1), and the radially inner side refers to the side that is close to the rotation axis O in the radial direction R (the lower side in Fig. 1).

[0017] Furthermore, "drive connection" means that a driving force / torque can be transmitted between two components. These two components can be directly connected or connected through various transmission mechanisms or connecting structures to achieve the above-mentioned function. "torsion-resistant connection" means that a torque can be transmitted between two components. The method of achieving a torque-resistant connection can include interference fit, screw connection, etc.

[0018] To solve the above-mentioned technical problems, the present disclosure provides a dual-mass flywheel. As shown in the Fig. 1 to 6, the dual-mass flywheel comprises a first mass flywheel 10 (also referred to as primary mass flywheel), a second mass flywheel 20 (also referred to as secondary mass flywheel), a damping device 30 and a diaphragm spring 40.

[0019] The crankshaft of an engine is connected to a drive system (e.g., a transmission) via the dual-mass flywheel. The first mass flywheel 10 of the dual-mass flywheel is connected to the engine's crankshaft, the second mass flywheel 20 is connected to the drive system, and the damping device 30 is installed in the transmission path between the first mass flywheel 10 and the second mass flywheel 20. The first mass flywheel 10 is drivingly connected to the second mass flywheel 20 via the damping device 30. Engine operation drives the first mass flywheel 10 to rotate. The damping device 30 transmits the rotation of the first mass flywheel 10 to the second mass flywheel 20, which then transmits it to the transmission.

[0020] The second mass flywheel 20 is arranged axially A on the other axial side of the first mass flywheel 10 (the right side, as in Fig. 1) and forms an annular receiving space with the first mass flywheel 10; the damping device 30 is located in the receiving space in order to dampen the torsional vibrations between the crankshaft of the engine and the input shaft of the transmission.

[0021] In particular, the first mass flywheel 10 comprises a first housing 11 and a cover plate 12; wherein the first housing 11 and the cover plate 12 are arranged axially A, the first housing 11 is cylindrical and the cover plate 12 is annular. As in Fig. As shown in Figure 1, the cover plate 12 is located on the right side of the first housing 11, and the radially outer side of the cover plate 12 is non-rotatably connected to the radially outer side of the first housing 11. The radial dimension R of the cover plate 12 is smaller than the radial dimension R of the first housing 11, therefore the cover plate 12 forms a spring chamber with the first housing 11. The spring chamber is annular and is part of the receiving chamber.

[0022] The damping device 30 further comprises a flange 31 and flywheel springs 32, wherein the flywheel springs 32 are arc-shaped and may be spiral-shaped arc springs. The flywheel springs 32 may be two in number (this is only an example), wherein the two flywheel springs 32 are arranged in the spring chamber at equal spacing in the circumferential direction of the dual-mass flywheel, and the circumferential ends of adjacent flywheel springs 32 are spaced apart from each other by a specific circumferential gap. In other exemplary embodiments, the flywheel springs 32 may also consist of three or four, etc., which is not specified in more detail here.

[0023] The flange 31 may include a base circular section 311 and flange wings (also referred to as flange noses) projecting radially outward from the base circular section 311. The base circular section 311 is located in the receiving space, and the flange wings project into the spring space and into the circumferential gap between two flywheel springs 32. Therefore, in the spring space, the circumferential ends of the flywheel springs 32 abut the flange wings of the flange 31. When the first mass flywheel 10 rotates and the first mass flywheel 10 and the flange 31 do not rotate simultaneously, the flywheel springs 32 are compressed. The flywheel springs 32 drive the flange 31 and the second mass flywheel 20 to rotate via the flange wings of the flange 31, thereby transmitting torque and damping torsional vibrations.

[0024] Furthermore, the dual-mass flywheel comprises a support assembly comprising a radial support section 80. The radial support section 80 is located on the radially inner side of the flange 31 and serves to radially support the base circle section 311 of the flange 31.

[0025] Furthermore, the radially outer side of the diaphragm spring 40 rests against the radially inner side of the cover plate 12 of the first mass flywheel 10. The central part of the diaphragm spring 40 is clamped between the second mass flywheel and the base circular section 311 of the flange 31. The base circular section 311 of the flange 31, the central part of the diaphragm spring 40, and the second mass flywheel 20 are firmly connected to one another axially A by screws. In this way, the receiving space is sealed by the diaphragm spring 40, preventing external contaminants such as water, dust, and sand from entering the receiving space.

[0026] The radially inner side of the diaphragm spring 40 extends to the radially inner side of the flange 31 (as in Fig. 1 to 3), and further, the radially inner side of the diaphragm spring 40 extends to the radially inner side of the radial support portion 80.

[0027] In particular, the radially inner side of the diaphragm spring 40 is closer to the rotation axis O of the dual-mass flywheel than the base circle section 311 of the flange 31 and the radially inner side of the radial support section 80, that is, the inner diameter of the diaphragm spring 40 is smaller than the inner diameter of the base circle section 311 or even the radial support section 80. When grease overflows from the spring space into the receiving space and bypasses the radially inner side of the flange 31 and reaches the diaphragm spring 40, the fact that the radially inner side of the diaphragm spring 40 is closer to the rotation axis O prevents the grease from bypassing the radially inner side of the diaphragm spring 40 and reaching the axially outer side of the diaphragm spring 40.This prevents grease from leaking through the gap between the diaphragm spring 40 and the second mass flywheel 20, thereby avoiding wear between the damping device 30 and the first mass flywheel 10 or the flange vanes of the flange 31 due to lack of grease and insufficient damping.

[0028] Furthermore, the radially inner side of the diaphragm spring 40 is further bent toward the first mass flywheel 10 to form an overflow protection plate 41. The overflow protection plate 41 is also located further on the radially inner side of the flange 31 and the radial support portion 80. Furthermore, the overflow protection plate 41 can extend in the axial direction A and extend beyond the side of the flange 31 facing the first mass flywheel 10, so that the width of the overflow protection plate 41 can be greater than the width of the base circular portion 311 of the flange 31.

[0029] The larger width of the overflow protection plate 41 compared to the width of the base circular section 311 of the flange 31 enables the overflow protection plate 41 to axially absorb as much grease as possible and to extend the path of the grease to the diaphragm spring 40.

[0030] Furthermore, the overflow protection plate 41 can be arranged parallel to the rotation axis O or inclined to the rotation axis O. When the overflow protection plate 41 is arranged inclined, the inner diameter of the overflow protection plate 41 at the end closer to the first mass flywheel 10 is larger than the inner diameter of the overflow protection plate 41 at the end closer to the second mass flywheel 20.

[0031] In this way, when the grease that has bypassed the radially inner side of the base circle portion 311 of the flange 31 flows further along the axially inner side of the diaphragm spring 40 toward the rotation axis O, the overflow prevention plate 41 can prevent the grease from flowing further toward the rotation axis O. At a high rotational speed of the dual-mass flywheel, the grease accumulated on the overflow prevention plate 41 is thrown back into the receiving space or the spring space along the axially inner side of the diaphragm spring 40 under the action of centrifugal force, thereby preventing grease leakage and realizing grease reuse.

[0032] From the above, it can be seen that extending the radially inner side of the diaphragm spring 40 to the radially inner side of the flange 31 can prevent the grease from overflowing from the receiving space. Furthermore, the overflow prevention plate 41 formed by the diaphragm spring 40 toward the first mass flywheel 10 can not only capture the grease but also cause the grease to return to the receiving space or the spring space under the action of centrifugal force, thereby preventing grease from leaking through the gap between the diaphragm spring 40 and the second mass flywheel 20.

[0033] In some embodiments, as in Fig. 1 and Fig. 4, the second mass flywheel 20 is bent in the axial direction A and away from the first mass flywheel 10 and then bent radially inward to form a first bent portion 21.

[0034] In some embodiments, the radially inner side of the diaphragm spring 40 may extend directly in the radial direction R. The diaphragm spring 40 of this structure is simple in construction and easy to manufacture.

[0035] In other embodiments, the radially inner side of the diaphragm spring 40 is provided with a second bent portion 42, wherein the second bent portion 42 is bent in the bending direction of the first bent portion 21 of the second mass flywheel 20. That is, the diaphragm spring 40 extends adjacent to the inner wall of the second mass flywheel 20; therefore, the diaphragm spring 40 is also bent correspondingly at the first bent portion 21 of the second mass flywheel 20 to form the second bent portion 42. The dimension of the radially inner side of the second bent portion 42 is also smaller than the dimension of the radially inner side of the radial support portion 80.

[0036] In this way, the abutment of the diaphragm spring 40 against the second mass flywheel 20 increases the length of the diaphragm spring 40 and can prevent grease that has overflowed into the receiving space and bypassed 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, so that the grease can only flow back along the inner wall of the diaphragm spring 40. Furthermore, when some of the grease overflows between the diaphragm spring 40 and the second mass flywheel 20, the curved abutment of the diaphragm spring 40 against the second mass flywheel 20 increases the length of the gap between the diaphragm spring 40 and the second mass flywheel 20, which corresponds to the extension of the overflow path of the grease, and the curved diaphragm spring 40 increases the resistance to the grease, thereby further preventing grease overflow.

[0037] It should be noted that regardless of whether the diaphragm spring 40 forms a second bent portion 42 or not, the diaphragm spring 40 can always be further bent in the axial direction A to form the overflow protection plate 41. That is, after the radially inner side of the diaphragm spring 40 extends beyond the radial support portion 80, it can be directly bent axially A to form the overflow protection plate 41 (as shown in Fig. 4, Fig. 5, Fig. 9, Fig. 10, Fig. 15 and Fig. 16), or after the radially inner side of the diaphragm spring 40 has been bent to form the second bent portion 42, it can then be bent axially A to form the overflow protection plate 41 (as shown in Fig. 2 and Fig. 12 shown).

[0038] Furthermore, the support assembly comprises a first support plate 70 and a second support plate 50. The radial support section 80 can be formed by the first support plate 70 (as in Fig. 11 to 16) or formed by the second support plate 50 (as shown in Fig. 1 to 10). The first support plate 70 is located wholly or partially between the first mass flywheel 10 and the flange 31. The first support plate 70 cooperates with the second flange 20 to axially support the flange 31 and prevent movement of the flange 31 in the axial direction A.

[0039] The second support plate 50 is located on the radially inner side of the first support plate 70 and serves to radially support the first support plate 70. Furthermore, the second support plate 50 is firmly connected to the axially inner side of the first mass flywheel 10 to enhance the axial strength of the first mass flywheel. Therefore, the first support plate 70 is typically made of nylon material, and the second support plate 50 is typically made of metal material.

[0040] The invention will be described in detail below based on the specific structure 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 the radial support portion 80.

[0041] In particular, as in Fig. 2, Fig. 4 and Fig. As shown in Figure 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 integrally formed. The second support plate 50 may be made of metal material and integrally formed by processes such as stamping or casting. An integrally formed second support plate 50 can save material, reduce process steps, and ensure high overall mechanical strength of the second support plate 50.

[0042] Furthermore, the first axial plate 51 forms the radial support portion 80 for radially supporting the radially inner side of the flange 31, and the first axial plate 51 is located between the radially inner side of the flange 31 and the overflow protection plate 41 of the diaphragm spring 40. In the embodiment of the present disclosure, the first axial plate 51 is arranged parallel to the rotation axis O, and the first axial plate 51 is perpendicular to the first radial plate 52 and the second radial plate 53, respectively. In some other embodiments, the first axial plate 51 may also be inclined or wave-shaped, which is not specified here.

[0043] Furthermore, the radially outwardly extending first radial plate 52 forms a bend with the first axial plate 51 that can accommodate grease. When grease bypasses the radially 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, thereby forming a first barrier against grease overflow. Only when the grease bypasses the radially outer side of the first radial plate 52 can it enter the overflow protection plate 41 of the diaphragm spring 40.

[0044] Furthermore, if a 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 non-rotatably connected to the first housing 11 of the first mass flywheel 10 via fastening elements.

[0045] In this way, the second radial plate 53 establishes a rotationally fixed connection between the second support plate 50 and the first mass flywheel 10. 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 flow of grease that has bypassed the radially inner side of the flange 31 to the diaphragm spring 40 and store the grease.

[0046] In addition, the overflow protection plate 41 can abut against the first axial plate 51 of the support plate (as in Fig. 1 and Fig. 2) or have a certain distance in the radial direction, which is not specified here.

[0047] In some other embodiments, the diaphragm spring 40 further includes a radial portion (not shown in the drawing). The radial portion is connected to the end of the overflow protection plate 41 facing the first mass flywheel 10, and the radial portion extends radially outward and forms an overflow protection groove with the overflow protection plate 41.

[0048] In particular, the radial portion causes the opening of the overflow protection groove of the first axial plate 51 to face the support plate 50. The radial portion can further prevent the flow of grease toward the rotational axis O of the dual-mass flywheel and prevent grease from leaking through the gap between the diaphragm spring 40 and the second mass flywheel 20. Furthermore, the overflow protection groove formed by the radial plate and the overflow protection plate 41 can better retain grease and propel the grease stored in the overflow protection groove back into the spring chamber under the action of centrifugal force at high speed.

[0049] In some embodiments, the dual-mass flywheel further includes a first friction ring 60. The first friction ring 60 is disposed between the radially outer side of the diaphragm spring 40 and the radially inner side of the cover plate 12.

[0050] As can be seen from the above, the diaphragm spring 40 is non-rotatably connected to the second mass flywheel 20. When the first mass flywheel 10 drives the second mass flywheel 20, relative rotation occurs between the first mass flywheel 10 and the second mass flywheel 20. The radially outer side of the diaphragm spring 40 and the radially inner side of the cover plate 12 also generate relative rotation. The first friction ring 60 can be made of plastic. In this way, the first friction ring 60 can not only prevent friction between the diaphragm spring 40 and the cover plate 12, but also adjust the axial gap between the radially outer side of the diaphragm spring 40 and the radially inner side of the cover plate 12 to prevent external water, dust, and sand from entering the accommodation space and improve the tightness of the accommodation space.

[0051] It is understood that the term "multiple" and the like in the disclosure refers to two or more. The term "and / or" represents a relationship between associated objects, which can include three relationships; for example, "A and / or B" can mean only A, both A and B, and only B. The symbol " / " generally indicates that the associated objects before and after are in an "or" relationship. The singular forms "a / an," "the," and "this / these" are intended to include the plural forms as well, unless clearly stated in this context.

[0052] It should be further understood that the terms "first," "second," etc., are used to describe various structures, but these structures should not be limited by these terms. These terms are used only to distinguish structures of the same type and do not imply any particular order or importance. Indeed, terms such as "first" and "second" can be used entirely interchangeably. 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 the disclosure.

[0053] It is further understood that the orientations or positional relationships indicated by the terms "central", "longitudinal", "transverse", "front", "rear", "top", "bottom", "left", "right", "vertical", "horizontal", "tip", "bottom", "inside", "outside", etc., are based on the orientations or positional relationships shown in the drawings and are provided only for the convenience and ease of describing the embodiments, rather than stating or implying that the defined devices or elements have a particular orientation or must be constructed and operated in a particular orientation.

[0054] It is further understood that, unless expressly stated otherwise, “connection” includes both a direct connection without other components in between and an indirect connection with other elements in between.

[0055] It should be further understood that, while the drawings describe the operations in a particular order in the embodiments of the disclosure, this should not be understood to imply that the operations are performed in the particular order shown, or in a serial order, or that all of the operations shown must be performed to achieve the desired result. Multitasking and parallel processing may be advantageous under certain circumstances.

[0056] Other embodiments of the present disclosure will be readily apparent to those skilled in the art from consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any modifications, uses, or adaptations of the disclosure, and such modifications, uses, or adaptations follow the general principles of the disclosure and include common knowledge or conventional technical means in the art not disclosed in the disclosure. The specification and embodiments are to be considered as examples only, with a true scope and spirit of the disclosure being indicated by the following claims.

[0057] It should be understood that the disclosure is not limited to the precise constructions described above and shown in the drawings, and that various modifications and changes may be made without departing from its scope. The scope of the disclosure is limited only by the scope of the appended claims.

Claims

[1] Dual-mass flywheel, characterized by that it includes: a first mass flywheel (10); a second mass flywheel (20) which is arranged in the axial direction (A) on one side of the first mass flywheel (10) and forms a receiving space with the first mass flywheel (10); a damping device (30) located in the receiving space, the damping device (30) comprising a flange (31); a support assembly comprising a radial support portion (80), the radial support portion (80) being supported on the radially inner side of the flange (31); and a diaphragm spring (40), wherein the radially outer side of the diaphragm spring (40) bears against the first mass flywheel (10), wherein the middle part of the diaphragm spring (40) is arranged between the second mass flywheel and the flange (31), wherein the radially inner side of the diaphragm spring (40) extends to the radially inner side of the radial support section (80). [2] Dual-mass flywheel according to claim 1, characterized by in that the second mass flywheel (20) is bent in the axial direction (A) away from the first mass flywheel (10) and then bent radially inward to form a first bending region (21); wherein the radially inner side of the diaphragm spring (40) is provided with a second bent portion (42), wherein the second bent portion (42) is bent in the bending direction of the first bent portion (21) of the second mass flywheel (20). [3] Dual-mass flywheel according to claim 1 or 2, characterized by that the diaphragm spring (40) is bent in the direction of the first mass flywheel (10) to form an overflow protection plate (41), wherein the overflow protection plate is located on the radially inner side of the radial support section. [4] Dual-mass flywheel according to claim 1, characterized by that the support arrangement further comprises: a first support plate (70), wherein the first support plate (70) is located wholly or partly between the first mass flywheel (10) and the flange (31) and serves to axially support the flange (31); a second support plate (50) located on the radially inner side of the first support plate (70) and serving to radially support the first support plate (70), the second support plate (50) being fixedly connected to the axially inner side of the first mass flywheel (10); wherein the first support plate (70) or the second support plate (50) extends in the axial direction (A) to form the radial support structure. [5] Dual-mass flywheel according to claim 1, characterized byin that the diaphragm spring (40) further comprises a radial portion, wherein the radial portion is connected to an end of the overflow protection plate (41) which is closer to the first mass flywheel (10), and wherein the radial portion extends radially outward and forms an overflow protection groove with the overflow protection plate (41). [6] Dual-mass flywheel according to claim 1, characterized by in that the first mass flywheel (10) comprises a first housing (11) and a cover plate (12); wherein the first housing (11) and the cover plate (12) are arranged in the axial direction (A), and wherein the radially outer side of the cover plate (12) is connected in a rotationally fixed manner to the radially outer side of the first housing (11), and the radially inner side of the cover plate (12) bears against the radially outer side of the diaphragm spring (40). [7] Dual-mass flywheel according to claim 6, characterized bythat the dual-mass flywheel further comprises a first friction ring (60), wherein the first friction ring (60) is provided between the radially outer side of the diaphragm spring (40) and the radially inner side of the cover plate (12). [8] Dual-mass flywheel according to claim 1, characterized by in that the damping device (30) further comprises arcuate flywheel springs (32), wherein a spring chamber is formed between the first housing (11) and the cover plate (12), and wherein the flywheel springs (32) are mounted in the spring chamber and bear against the flange (31).

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