WO2023184514A1

WO2023184514A1 - Dual-mass flywheel

Info

Publication number: WO2023184514A1
Application number: PCT/CN2022/084930
Authority: WO
Inventors: 甄臻; 熊豪彦; 梁小立
Original assignee: 舍弗勒技术股份两合公司
Priority date: 2022-04-01
Filing date: 2022-04-01
Publication date: 2023-10-05

Abstract

A dual-mass flywheel, comprising: a first flywheel mass (10), comprising a first housing (11) and a cover plate (12) connected to each other; a second flywheel mass (20), wherein an accommodation space (30) is formed between the second flywheel mass and the first flywheel mass, and the second flywheel mass comprises a hub flange (21); a damping mechanism (40) located in the accommodation space, wherein the damping mechanism comprises a centrifugal-force pendulum unit (41) and a flange (42), the centrifugal-force pendulum unit is mounted on the flange, and the flange is fixedly mounted on one side of the hub flange; and a waterproof mechanism (50), comprising a diaphragm spring (51) and a first support plate (52) extending in a radial direction (Y), wherein the first support plate is fixed to the other side of the hub flange that is away from the first housing in an axial direction (X), and the diaphragm spring is arranged between the first support plate and the cover plate in the axial direction (X) in a compressed state, so as to seal the accommodation space.

Description

dual mass flywheel

Technical field

The invention relates to the field of vehicle vibration reduction, and in particular to a dual-mass flywheel.

Background technique

In related technologies, the torsional vibration of the automobile power transmission system is mainly caused by the irregular periodic excitation of the engine. The torsional vibration and the noise generated by the torsional vibration are an important aspect that affects the performance of the automobile. Therefore, in order to eliminate such undesirable noise and vibration, it is an urgent technical problem that those skilled in the art need to solve.

Contents of the invention

In order to overcome the problems existing in related technologies, the present disclosure provides a dual-mass flywheel.

According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a first flywheel mass, including a first housing and a cover plate connected to each other; a second flywheel mass, the second flywheel mass and the first flywheel mass An accommodation space is formed between them, and the second flywheel mass includes a hub flange; a vibration reduction mechanism is located in the accommodation space, the vibration reduction mechanism includes a centrifugal force pendulum unit and a flange, and the centrifugal force pendulum unit is installed on the flange , the flange is fixedly installed on one side of the hub flange; and a waterproof mechanism includes a diaphragm spring and a first support plate extending in a radial direction, wherein the first support plate is fixed in the axial direction. The hub flange is on the other side away from the first housing, and the diaphragm spring is axially disposed between the first support plate and the cover plate in a compressed state to seal the accommodation space. .

In some embodiments, the waterproof mechanism further includes a friction ring, the friction ring includes an axial portion extending along the axial direction and a radial portion extending along the radial direction, wherein all portions of the friction ring The radial portion is disposed between the first support plate and the diaphragm spring; or the radial portion of the friction ring is disposed between the diaphragm spring and the cover plate.

In some embodiments, the axial portion of the friction ring abuts the cover plate or the hub flange in the radial direction.

In some embodiments, the first support plate partially overlaps the cover plate in the radial direction, and/or the first support plate partially overlaps the centrifugal force pendulum unit in the radial direction.

In some embodiments, the radial length of the cover plate is greater than 2/5 of the radius of the dual-mass flywheel and less than 1/2 of the radius of the dual-mass flywheel.

In some embodiments, the first support plate is made of metal material, the diaphragm spring is made of metal material, and the friction ring is made of plastic.

In some embodiments, the cover plate is provided with a bending portion, and at the centrifugal force pendulum unit, the bending portion is bent in a direction away from the centrifugal force pendulum unit along the axial direction to increase the The axial dimension of the accommodation space at the centrifugal force pendulum unit.

In some embodiments, along the axial direction, the cover plate protrudes from the side of the hub flange on the side away from the centrifugal pendulum unit.

In some embodiments, the first support plate and the flange are respectively fixed on both sides of the hub flange through the same connecting member.

In some embodiments, the damping mechanism further includes an arc-shaped flywheel spring, a spring installation space is formed between the first housing and the cover plate, and the flywheel spring is installed in the spring installation space. .

The technical solutions provided by the embodiments of the present disclosure may include the following beneficial effects:

By arranging the first support plate and adjusting the radial length of the first support plate to match the cover plate, flange and hub flange, the flange can be waterproofed simultaneously in the radial or axial direction and the flange can be made waterproof. Enough space is left in the radial direction to install the centrifugal force pendulum unit to increase the damping and vibration reduction effect of the dual-mass flywheel. In addition, when the dual-mass flywheel is installed, for example, between the engine and the gearbox, the corresponding parts of the gearbox will not directly contact the diaphragm spring, which can avoid or reduce the deformation of the diaphragm spring during the assembly process.

Description of drawings

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

Figure 1 is a schematic structural diagram of a dual-mass flywheel in the related art;

Figure 2 is a schematic structural diagram of a dual-mass flywheel in the related art;

Figure 3 is a schematic structural diagram of a dual-mass flywheel according to an exemplary embodiment;

FIG. 4 is a schematic diagram showing dimensional relationships according to an exemplary embodiment.

Detailed ways

Exemplary embodiments will be described in detail herein, examples of which are illustrated in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings refer to the same or similar elements unless otherwise indicated. The implementations described in the following exemplary embodiments do not represent all implementations consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with aspects of the disclosure as detailed in the appended claims.

In the present invention, unless otherwise stated, the axial direction, radial direction and circumferential direction refer to the axial direction, radial direction and circumferential direction of the dual mass flywheel respectively; the axial direction refers to the axial direction in Figure 1, Figure 2 and Figure 3. on the left side (such as the side where the power source is located), the other axial side refers to the right side in Figures 1, 2 and 3 (such as the side where the transmission is located); the radially outer side refers to the radial direction away from the side in Figure 3 The side of the central axis O (the upper side in FIG. 3 ) and the radially inner side refer to the side that is radially close to the central axis O (the lower side in FIG. 3 ). In addition, "transmission connection" refers to the ability to transmit driving force/torque between two components. The two components can be directly connected or through various transmission mechanisms or connection structures to achieve the above functions.

Figures 1 and 2 are respectively schematic structural diagrams of dual-mass flywheels in related technologies.

As shown in Figure 1, the radial size of the cover plate 1 in the related art is small. When the dual-mass flywheel is assembled with the engine and gearbox (also known as the transmission), the input shaft of the gearbox will extend to the hub. In core 2, components such as the input shaft of the gearbox may cause the hub core 2 and flange 3 to skew, and even the structure of the gearbox may touch the diaphragm 4, causing the diaphragm 4 to rupture.

Moreover, the radial size of the diaphragm 4 is large, and the structure of the axially unsupported diaphragm 4 can easily cause the diaphragm to deform or break, whether during transportation, assembly, disassembly or operation, making the dual-mass flywheel waterproof ineffective.

In order to prevent the diaphragm 4 from deforming or breaking, the radial length of the cover plate 1 can be increased to extend further radially inward. However, it is expected that the dual-mass flywheel also has a waterproof function. Simply lengthening the cover plate 1 will make There is a large gap between the cover plate 1 and the diaphragm 4, and a certain amount of water can easily be stored in the gap. In this way, water can easily enter the inside of the flywheel from the gap that may appear between the diaphragm 4 and the cover plate 1, causing the grease inside the dual-mass flywheel to fail.

In order to solve the technical problem in Figure 1, the structural change shown in Figure 2 was made. The diaphragm was changed to a diaphragm spring 5, and a friction ring 6 was installed. The friction ring 6 was supported by the base circle of the flange 3. , therefore, the friction ring 6 occupies the radial dimension of the flange 3, and as shown in Figure 1, the centrifugal force pendulum unit 7 riveted to the flange 3 will also occupy the radial dimension of the flange 3. For this reason, the membrane is set After the leaf spring 5 and the friction ring 6 are installed, the radial size of the centrifugal force pendulum unit installed on the flange 3 is insufficient, resulting in poor damping and vibration reduction effect of the dual-mass flywheel.

Taking into account the above situation, the following embodiments of the dual-mass flywheel of the present disclosure are made. According to the embodiment of the present disclosure, a dual-mass flywheel is provided. As shown in Figure 3, it includes a first flywheel mass 10 and a second flywheel mass 20. , vibration reduction mechanism 40 and waterproof mechanism 50.

Among them, the first flywheel mass 10 (also called the main flywheel mass) is used for transmission connection with the output shaft of the vehicle's power source (eg, engine). The second flywheel mass 20 (also called the auxiliary flywheel mass) is used for transmission connection with the transmission. An accommodating space 30 is formed between the first flywheel mass 10 and the second flywheel mass 20 , and the vibration damping mechanism 40 is located in the accommodating space 30 to attenuate the torsional vibration between the engine output shaft and the transmission input shaft.

Specifically, the first flywheel mass 10 includes a first housing 11 and a cover plate 12 connected along the axial direction X; the first housing 11 may be provided with a plurality of holes 111 . Further, the first housing 11 is cylindrical, and the cover 12 is annular. As shown in FIG. 3 , the cover 12 is installed on the right side of the first housing 11 along the axial direction X, and the cover 12 and A spring installation space 31 is formed between the first housings 11 , and the spring installation space 31 is an annular space located radially outside the accommodation space 30 .

The damping mechanism 40 includes a centrifugal force pendulum unit 41, a flange 42 and a flywheel spring 43. The flywheel spring 43 may be a spiral arc spring. There may be two flywheel springs 43 (just for example). The two flywheel springs 43 are arranged at equal intervals in the spring installation space 31 along the circumferential direction of the dual-mass flywheel. The circumferential ends of adjacent flywheel springs 43 are mutually exclusive. Leave a certain gap between them.

The flange 42 may include a base round portion and a flange wing portion (also called a flange lug) extending radially outward from the base round portion, and the flange wing portion is deep into the gap between the two flywheel springs 43 . When the first flywheel mass 10 and the flange 42 rotate relative to each other, the flange wings of the flange 42 can compress the flywheel spring 43 to achieve the purpose of transmitting torque and attenuating torsional vibration.

The centrifugal force pendulum unit 41 is movably installed on the base circle portion of the flange 42 , that is, the centrifugal force pendulum unit 41 is located in the accommodation space 30 radially inside the spring installation space 31 .

Further, the centrifugal force pendulum unit 41 can be disposed on both sides of the flange 42 along the axial direction The centrifugal force swings the pendulum unit 41 to attenuate the torsional vibration.

The second flywheel mass 20 is disposed axially on the side of the first flywheel mass 10 with the cover plate 12; the second flywheel mass 20 includes a hub flange 21, and the hub flange 21 may be provided with through holes 22 for bolts to pass through. . The center part of the hub flange 21 is provided with a hub core, and the inner wall of the hub core is provided with splines, which are drivingly connected with the input shaft of the transmission through the splines.

Further, along the axial direction X, the cover plate 12 protrudes from the side of the hub flange 21 (the hub flange shown in FIG. 21), and there is a gap between the cover plate 12 and the hub flange 21 in the axial direction 11. The cover plate 12, the hub flange 21 and the waterproof mechanism 50 jointly surround the accommodation space 30.

The damping mechanism 40 is located in the accommodation space 30 , so the flange 42 is fixedly installed on one side of the hub flange 21 , that is, the left side of the hub flange 21 shown in FIG. 3 .

The waterproof mechanism 50 includes a diaphragm spring 51 and a first support plate 52 extending in the radial direction Y. The first support plate 52 is fixed on the other side of the hub flange 21 away from the flange 42 along the axial direction X, that is, the right side of the hub flange 21 shown in FIG. 3 .

In some embodiments, the first support plate 52 and the flange 42 are respectively fixed on both sides of the hub flange 21 through the same connecting member 44. Specifically, the same connecting member 44 (such as a rivet or bolt) moves from left to right along the axial direction X. Pass through the base circle part of the flange 42, the hub flange 21 and the first support plate 52 in sequence to the right, and fix the three.

In some embodiments, the first support plate 52 is annular, and the first support plate 52 and the cover plate 12 partially overlap in the radial direction Y, that is, when viewed along the axial direction X, the cover plate 12 and the first support plate 52 are in the radial direction Y. There is occlusion or overlap in the radial Y direction. Further, as shown in FIG. 4 , the overlapping length W2 of the first support plate 52 and the cover plate 12 in the radial direction Y is approximately equal to 1/6 of the radial length W1 of the cover plate 12 .

In this way, the water storage space formed by the cover plate 12 and the first support plate 52 in the axial direction X and the radial direction Y becomes smaller, so that even when wading, water is not easy to remain in the cover plate 12 and the first support plate 52 The gap between them can improve the waterproof performance of the dual-mass flywheel.

The diaphragm spring 51 is arranged in a compressed state between the first support plate 52 and the cover plate 12 along the axial direction X to seal the accommodating space 30 . Specifically, the diaphragm spring 51 has a substantially circular ring shape. The diaphragm spring 51 can prevent external water from entering the accommodation space 30 through the gap between the cover plate 12 and the first support plate 52. In addition, in the compressed state, the elastic force of the diaphragm spring 51 can also provide a limiting mechanism on the shaft. The limiting and frictional force in the direction X, as well as the friction between the radially outer and radially inner sides of the diaphragm spring 51 can also achieve a damping (vibration reduction) function.

In some embodiments, the waterproof mechanism 50 further includes a friction ring 53. The friction ring 53 includes an axial portion 531 extending along the axial direction X and a radial portion 532 extending along the radial direction Y. Specifically, the friction ring 53 is formed by Viewed in cross section, the axial portion 531 and the radial portion 532 of the friction ring 53 are generally L-shaped.

Further, the radial portion 532 of the friction ring 53 is disposed between the first support plate 52 and the diaphragm spring 51; at this time, the left side of the friction ring 53 and the right side of the first support plate 52 in Figure 3 fit, A diaphragm spring 51 is provided between the right side of the friction ring 53 and the cover plate 12 . The radially outer or radially inner sides of the diaphragm spring 51 are respectively in contact with the right side of the friction ring 53 or the left side of the cover plate 12 .

In addition, the diaphragm spring 51 makes the friction ring 53 and the first support plate 52 closely contact each other, so that there is basically no gap at the circumferential contact surface between the radial portion 532 of the friction ring 53 and the first support plate 52, thereby enabling Water is prevented from entering the accommodation space 30 of the dual-mass flywheel from the gap between the radial portion 532 and the first support plate 52 .

Alternatively, the radial portion 532 of the friction ring 53 is disposed between the diaphragm spring 51 and the cover plate 12 ; at this time, the right side of the friction ring 53 is in contact with the left side of the cover plate 12 , and the radial portion of the diaphragm spring 51 The outer side or the radially inner side is respectively in contact with the left side of the friction ring 53 or the right side of the first support plate 52 . The function of the friction ring 53 will not be described again here.

In some embodiments, the axial portion 531 of the friction ring 53 abuts the cover plate 12 or the hub flange 21 in the radial direction Y. In this way, water can be prevented from entering the interior of the dual-mass flywheel from the gap at the contact surface between the friction ring 53 and the cover plate 12 (which extends axially to the accommodating space 30 of the dual-mass flywheel).

In addition, in the waterproof mechanism 50, the separately provided first support plate 52 is used to form the friction ring 53, which can prevent the friction ring 53 from abutting the base circle of the flange 42, thereby occupying the diameter of the base circle of the flange 42. In this way, the radial direction of the base circular portion of the flange 42 has sufficient size to install the centrifugal force pendulum unit 41, so that the centrifugal force pendulum unit 41 can increase the torsional vibration attenuation effect and have a good waterproof effect at the same time.

In addition, the diaphragm spring 51 and the friction ring 53 in the waterproof mechanism 50 are small in radial size and high in strength, which can overcome the problem in the related art that the diaphragm is bent or even broken due to insufficient strength of the diaphragm.

In addition, the diaphragm spring 51 is arranged on the left side of the cover plate 12, that is, located inside the cover plate 12. When the dual-mass flywheel is installed between the engine and the gearbox, the corresponding parts of the gearbox will not directly contact the diaphragm spring. 51, which can avoid or reduce the deformation of the diaphragm spring 51 during the assembly process.

Moreover, the length of the diaphragm spring 51 in the radial direction Y (referring to half of the length in the axial cross-section) is small, so the diaphragm spring 51 is not easily deformed during use. The diaphragm spring 51 is not easily deformed and is different from the strength of the cover plate 12. Enhancement can enable the dual-mass flywheel to withstand greater axial force and torsional vibration input from the engine crankshaft to the dual-mass flywheel, which can improve the performance and durability of the dual-mass.

In some embodiments, the first support plate 52 is made of metal material, the diaphragm spring 51 is made of metal material, and the friction ring 53 is made of plastic. The above is only exemplary and is not intended to limit the scope of the present disclosure. The first support plate 52 can also be made of other strong and thin materials to reduce the weight of the entire dual-mass flywheel.

In some embodiments, the radial length W1 of the cover plate 12 is greater than 2/5 of the radius R of the dual-mass flywheel and less than 1/2 of the radius R of the dual-mass flywheel. The radial length W1 of the cover plate 12 refers to the length of the cover plate 12 located on one side of the central axis of the longitudinal section of the cover plate 12 .

By setting the radial length W1 of the cover plate 12 in this way, not only the strength of the cover plate 12 can be increased, but the size of the cover plate 12 can be the same diameter as the connector 44 when the first support plate 52, the hub flange 21 and the flange 42 are installed. Leave enough space when structuring inward.

In some embodiments, the cover plate 12 is provided with a bending portion 121 . Located at the centrifugal force pendulum unit 41 , the bending portion 121 is bent along the axial direction X in a direction away from the centrifugal force pendulum unit 41 to increase the accommodation space 30 under centrifugal force. Axial dimension at pendulum unit 41.

Specifically, the cover plate 12 protrudes in an arc shape at the flywheel spring 43 in a direction away from the flywheel spring 43. Then, after the cover plate 12 bypasses the flywheel spring 43, it recesses in a direction closer to the first housing 11. Then the cover plate 12 protrudes in a direction away from the first housing 11 , so the cover plate 12 is wavy. The wavy cover plate 12 can increase the strength of the cover plate 12 .

In addition, the cover 12 is bent in the direction away from the centrifugal force pendulum unit 41 along the axial After the support plate 52 , the first support plate 52 interferes with the base circle portion of the flange 42 or the centrifugal force pendulum unit 41 in the axial direction.

Further, the first support plate 52 partially overlaps the centrifugal force pendulum unit 41 in the radial direction Y. In this way, the radial dimension of the first support plate 52 can be increased, and the strength of the first support plate 52 can be increased. In addition, the radial outer side of the friction ring 53 can be lower than, higher than, or flush with the radial direction of the first support plate 52 . The outside is not specifically limited here.

Further, the first flywheel mass 10 also includes a balance load 13. The balance load 13 is installed on the side of the first housing 11 away from the cover 12 (ie, the left side shown in Figure 3) for adjusting the entire first flywheel. Mass 10 moment of inertia and other properties.

Further, the dual-mass flywheel also includes a second support plate 60 and a second friction ring 70 . The second support plate 60 is provided in the axial X gap between the first housing 11 and the hub flange 21 .

Among them, along the axial direction, one side of the second support plate 60 is in contact with the first housing 11 , and the other side of the second support plate 60 is in contact with one side of the second friction ring 70 .

The second friction ring 70 is annular, and the radially outer side of the second friction ring 70 is in contact with the second flywheel mass 20 .

The second support plate 60 and the second friction ring 70 realize the axial limitation of the second flywheel mass 20 in the axial direction X, because the flange 42 and the first support plate 52 are fixedly installed on the hub flange 21 via the connector 44 , therefore, the axial position of the flange 42 is also limited, making the overall dual-mass flywheel stronger and more stable.

Further, the second support plate 60 is made of metal material, and the second friction ring 70 is made of plastic material. The above are only examples and are not specifically limited here.

The dual-mass flywheel of the present disclosure can be applied to vehicles. The specific manner in which the functions of the dual-mass flywheel in the above embodiments are implemented in the vehicle have been described in detail in the embodiments related to the dual-mass flywheel, and will not be described here. Give a detailed explanation.

It can be understood that "plurality" in this disclosure refers to two or more, and other quantifiers are similar. "And/or" describes the relationship between related objects, indicating that there can be three relationships. For example, A and/or B can mean: A exists alone, A and B exist simultaneously, and B exists alone. The character "/" generally indicates that the related objects are in an "or" relationship. The singular forms "a", "the" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.

It will be further understood that the terms "first," "second," etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are used only to distinguish structures of the same type from each other and do not imply a specific order or importance. In fact, expressions such as "first" and "second" can be used interchangeably. For example, without departing from the scope of the present disclosure, a first structure may also be referred to as a second structure, and similarly, the second structure may also be referred to as a first structure.

It is further understood that the terms "center", "longitudinal", "transverse", "front", "rear", "upper", "lower", "left", "right", "vertical", "horizontal" ", "top", "bottom", "inner", "outer", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for convenience of describing this embodiment and simplifying the description, rather than instructions. or to imply that the device or element referred to must be oriented, constructed, and operate in a particular orientation.

It should be further understood that, unless otherwise specified, "connection" includes a direct connection without other components between the two, and also includes an indirect connection with other elements between the two.

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

Other embodiments of the 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 variations, uses, or adaptations of the disclosure that follow the general principles of the disclosure and include common knowledge or customary technical means in the technical field that are not disclosed in the disclosure. . It is intended that the specification and examples be considered as exemplary only, with a true scope and spirit of the disclosure being indicated by the following claims.

It is to be understood that the present disclosure is not limited to the precise structures described above and illustrated in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the disclosure is limited only by the appended rights.

Claims

A dual-mass flywheel is characterized by including:

The first flywheel mass (10) includes a first housing (11) and a cover plate (12) connected to each other;

A second flywheel mass (20). An accommodation space (30) is formed between the second flywheel mass (20) and the first flywheel mass (10). The second flywheel mass (20) includes a hub flange (21) ;

The vibration reduction mechanism (40) is located in the accommodation space (30). The vibration reduction mechanism (40) includes a centrifugal force pendulum unit (41) and a flange (42). The centrifugal force pendulum unit (41) is installed on the The flange (42) is fixedly installed on one side of the hub flange (21); and

The waterproof mechanism (50) includes a diaphragm spring (51) and a first support plate (52) extending in the radial direction (Y),

Wherein, the first support plate (52) is fixed on the other side of the hub flange (21) away from the first housing (11) along the axial direction (X), and the diaphragm spring (51) It is arranged between the first support plate (52) and the cover plate (12) in a compressed state along the axial direction (X) to seal the accommodation space.
The dual-mass flywheel according to claim 1, characterized in that:

The waterproof mechanism (50) also includes a friction ring (53). The friction ring (53) includes an axial portion (531) extending along the axial direction (X) and an axial portion extending along the radial direction (Y). Radial part (532),

Wherein, the radial portion (532) of the friction ring (53) is provided between the first support plate (52) and the diaphragm spring (51); or the radial portion (532) of the friction ring (53) The radial portion (532) is provided between the diaphragm spring (51) and the cover plate (12).
The dual-mass flywheel according to claim 2, characterized in that:

The axial portion (531) of the friction ring (53) abuts the cover plate (12) or the hub flange (21) in the radial direction (Y).
The dual-mass flywheel according to any one of claims 1 to 3, characterized in that,

The first support plate (52) partially overlaps the cover plate (12) in the radial direction (Y), and/or,

The first support plate (52) partially overlaps the centrifugal force pendulum unit (41) in the radial direction (Y).
The dual-mass flywheel according to any one of claims 1 to 4, characterized in that,

The radial length (W1) of the cover plate (12) is greater than 2/5 of the radius (R) of the dual-mass flywheel and less than 1/2 of the radius (R) of the dual-mass flywheel.
The dual-mass flywheel according to any one of claims 1 to 5, characterized in that,

The first support plate (52) is made of metal material, the diaphragm spring (51) is made of metal material, and the friction ring (53) is made of plastic.
The dual-mass flywheel according to any one of claims 1 to 6, characterized in that,

The cover plate (12) is provided with a bending portion (121). At the centrifugal force pendulum unit (41), the bending portion (121) is away from the centrifugal force pendulum along the axial direction (X). The direction of the unit (41) is bent to increase the axial size of the accommodation space at the centrifugal force pendulum unit (41).
The dual-mass flywheel according to any one of claims 1 to 7, characterized in that,

Along the axial direction (X), the cover plate (12) protrudes from the side of the hub flange (21) on the side away from the centrifugal pendulum unit (41).
The dual-mass flywheel according to any one of claims 1 to 8, characterized in that,

The first support plate (52) and the flange (42) are respectively fixed on both sides of the hub flange (21) through the same connector.
The dual-mass flywheel according to any one of claims 1 to 9, characterized in that,

The damping mechanism (40) also includes an arc-shaped flywheel spring (43). A spring installation space (31) is formed between the first housing (11) and the cover plate (12). The flywheel The spring (43) is installed in the spring installation space (31).