CN113898699B

CN113898699B - Dual mass flywheel

Info

Publication number: CN113898699B
Application number: CN202111147892.4A
Authority: CN
Inventors: 颜克志; 吴春华; 易铭翰; 梁小立; 甄臻
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2021-09-29
Filing date: 2021-09-29
Publication date: 2023-10-27
Anticipated expiration: 2041-09-29
Also published as: CN113898699A; DE102022123280A1

Abstract

There is provided a dual mass flywheel comprising: a spring (200); a primary mass (100) comprising a first housing (110) and a second housing (120), the first housing (110) for connection to a power source; a hub member (300) and a flange (400) integrally formed or connected to each other, the spring (200) being disposed between the primary mass (100) and the flange (400) to attenuate torsional vibrations, the hub member (300) serving as an output; and a diaphragm spring (500) that is disposed in a compressed state between the flange (400) and the second housing (120) in the axial direction (AX). The radially inner end (122) of the second housing (120) is closer to the radially inner side of the dual mass flywheel than the radially inner end of the diaphragm spring (500), or the radially inner end (122) of the second housing (120) is flush with the radially inner end of the diaphragm spring (500) in the radial direction (RA).

Description

Dual mass flywheel

Technical Field

The present utility model relates to dual mass flywheels, and in particular to dual mass flywheels having improved waterproof properties.

Background

The inventor's utility model patent CN210371835U discloses a dual mass flywheel with centrifugal force pendulum units. Referring to fig. 1A, the dual mass flywheel includes: a primary mass 1 for driving connection with an output shaft of an engine; a secondary mass 3 and a hub 4, the hub 4 for driving an input shaft coupled to the gearbox; a flange 5 fixedly mounted to the secondary mass 3; at least two arcuate springs 6 which are arranged in the spring receiving space defined by the primary mass 1 and which can press the flange 5; and two or three centrifugal force pendulum units 7, the centrifugal force pendulum units 7 being mounted to the flange 5 at intervals in the circumferential direction of the dual mass flywheel.

The primary mass 1 comprises a first housing 11 and a second housing 12, the first housing 11 and the second housing 12 being connected together at the radially outer side of the dual mass flywheel and forming a spring receiving space for receiving at least two arcuate springs 6.

The dual mass flywheel further includes a diaphragm spring 8, an inner peripheral portion of the diaphragm spring 8 being fixedly mounted between the secondary mass 3 and the flange 5, an outer peripheral portion of the diaphragm spring 8 being pressed against the second housing 12. A friction pad made of plastic may be provided between the outer peripheral portion of the diaphragm spring 8 and the second housing 12. The diaphragm spring 8 (and the friction pad) can realize not only the axial limit of the secondary mass 3 on the axial side (right side in fig. 1A) but also a damping (vibration reduction) function by friction.

Disclosure of Invention

The object of the present utility model is to provide a dual mass flywheel with improved waterproof properties.

There is provided a dual mass flywheel comprising:

a spring;

a primary mass including a first housing and a second housing, the first housing and the second housing defining a spring receiving space that receives the spring;

a secondary mass, the spring being disposed between the primary mass and the secondary mass to dampen torsional vibrations; and

a diaphragm spring disposed in a compressed state in an axial direction of the dual mass flywheel between the secondary mass and the second housing,

the radial inner end of the second shell is closer to the radial inner side of the dual-mass flywheel than the radial inner end of the diaphragm spring, or the radial inner end of the second shell is flush with the radial inner end of the diaphragm spring in the radial direction of the dual-mass flywheel.

In at least one embodiment, the flange includes a base circle portion and a flange wing portion protruding radially outward from the base circle portion, the second housing and the base circle portion of the flange overlapping in a radial direction of the dual mass flywheel.

In at least one embodiment, the radial length of the second housing is greater than 1/3 of the radius of the dual mass flywheel,

preferably, the radial length of the second housing 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 at least one embodiment, the radial length of the diaphragm spring is less than 1/5 of the radius of the dual mass flywheel,

preferably, the radial length of the diaphragm spring is less than 1/9 of the radius of the dual mass flywheel.

In at least one embodiment, the radial length of the diaphragm spring is less than 2/5 of the radial length of the second housing,

preferably, the radial length of the diaphragm spring is less than 1/4 of the radial length of the second housing.

In at least one embodiment, the dual mass flywheel further comprises a first friction ring arranged at least partially between the secondary mass and the diaphragm spring, in particular at least partially between the flange as at least part of the secondary mass and the diaphragm spring, in the axial direction, the diaphragm spring being arranged between the first friction ring and the second housing; or,

in the axial direction, the first friction ring is at least partially disposed between the second housing and the diaphragm spring, the diaphragm spring being disposed between the first friction ring and the secondary mass.

Further, the first friction ring includes:

an axial portion extending along the axial direction; and

a radial portion connected to the axial portion and extending in a radial direction of the dual mass flywheel;

the axial portion has a first structure, wherein a second structure corresponding to the first structure is provided on a radially inner end or flange of the second housing, the first structure being coupled with the second structure such that the first friction ring is torsionally connected with the second housing or flange.

Further, the radial portion axially bears against the secondary mass or the second housing under the action of the diaphragm spring; the axial portion radially abuts the second housing or the secondary mass.

Further, one or more protrusions protruding radially outward are provided at an outer peripheral portion of the axial portion, and one or more recesses corresponding to the protrusions are provided at a radially inner end of the second housing, the protrusions being correspondingly coupled with the recesses; or,

one or more recesses recessed toward the radial inside are provided at the outer peripheral portion of the axial portion, and one or more protrusions corresponding to the recesses are provided at the radial inside end of the second housing, the protrusions being correspondingly coupled with the recesses.

Further, an auxiliary mounting structure is further arranged on the first friction ring.

Further, the diaphragm spring is made of metal, and the first friction ring is made of plastic.

Further, the dual mass flywheel further comprises a support and a second friction ring arranged between the first housing and the secondary mass, in particular between the first housing and a hub part being part of the secondary mass, thereby defining an axial gap between the first housing and the secondary mass or the hub part,

the second friction ring is stepped in cross section and includes an axial portion, a first radial portion extending radially outward from the axial portion, and a second radial portion extending radially inward from the axial portion, the second radial portion being pressed against the secondary mass or the hub member by the support.

Here, the radially inner end of the second housing is radially inward of the diaphragm spring of the dual mass flywheel. Thus, when the dual mass flywheel is installed, for example, between an engine and a gearbox, the respective components of the gearbox do not directly contact the diaphragm spring, and deformation of the diaphragm spring during assembly may be avoided or reduced.

Drawings

Fig. 1A is a cross-sectional view of a dual mass flywheel of the prior art.

Fig. 1B is a schematic view of a prior art dual mass flywheel with the second housing 12 extended.

Fig. 2 is a front view of a dual mass flywheel according to one embodiment of the utility model.

Fig. 3 is an oblique perspective view of the dual mass flywheel shown in fig. 2.

Fig. 4A is a cross-sectional view of the dual mass flywheel taken along line Y-Y in fig. 2.

Fig. 4B is a cross-sectional view of the dual mass flywheel taken along line X-X in fig. 2.

Fig. 5A is an enlarged schematic view of the upper half in fig. 4A, and fig. 5B is an enlarged schematic view of the lower half in fig. 4A.

Fig. 6A is a partially enlarged perspective view of the dual mass flywheel shown in fig. 2, and fig. 6B is a partially sectional enlarged schematic view of the dual mass flywheel shown in fig. 2.

Description of the reference numerals

1. Primary mass

3. Secondary mass

4. Hub core

5. Flange

6. Arc spring

7. Centrifugal force pendulum unit

8. Diaphragm spring

11. First shell body

12. Second shell

12A extension of the second housing

100. Primary mass

110. First shell body

111. Radial portion of first housing

112. Axial portion of first housing

120. Second shell

121. Radially outer end of the second housing

122. Radially inner end of the second housing

122G groove

200. Spring

300. Hub component

310. Hub core

320. Hub flange

330. Through hole for mounting bolt

400. Flange

410. Rivet

500. Diaphragm spring

600. First friction ring

610. Radial portion of first friction ring

620. Axial portion of first friction ring

700. Support member

800. Second friction ring

810. Axial portion of second friction ring

820. First radial portion of second friction ring

830. Second radial portion of second friction ring

O central axis

AX axial direction

Radial RA

C circumference direction

Detailed Description

Exemplary embodiments of the present utility model are described below with reference to the accompanying drawings. It should be understood that these specific illustrations are for the purpose of illustrating how one skilled in the art may practice the utility model, and are not intended to be exhaustive of all of the possible ways of practicing the utility model, nor to limit the scope of the utility model.

In the present utility model, unless otherwise specified, the axial direction, the radial direction, and the circumferential direction refer to the axial direction AX, the radial direction RA, and the circumferential direction C of the dual mass flywheel, respectively, the axial inside refers to the side near the center of the dual mass flywheel in the axial direction AX, and the axial outside refers to the side far from the center of the dual mass flywheel in the axial direction AX; the radially inner side means a side close to the center axis O of the dual mass flywheel in the radial direction RA, and the radially outer side means a side away from the center axis O of the dual mass flywheel in the radial direction RA.

As shown in fig. 1A, the radial length of the second housing 12 (sometimes also referred to as a cover plate) is small. When the dual mass flywheel (hereinafter, sometimes simply referred to as flywheel) is assembled with the engine and the transmission, an input shaft of the transmission may extend into the hub 4, and the input shaft of the transmission and the like may cause the hub 4 and the flange 5 to be skewed, causing the diaphragm spring 8 to be deformed.

In order to prevent the diaphragm spring from being deformed, as shown in fig. 1B, the applicant has conceived a solution of lengthening the second housing 12 shown in fig. 1A, i.e., increasing the radial length of the second housing 12 so that it extends further toward the radial inside, to form the extension 12A shown in fig. 1B.

However, it is desirable that the dual mass flywheel also have a waterproof function, simply lengthening the second housing 12 shown in fig. 1A would allow a large gap S to exist between the second housing 12 (including the extension 12A) and the diaphragm spring 8, which gap S would easily store some water. In this way, water is liable to enter the flywheel interior from the gap that may occur between the diaphragm spring 8 and the second housing 12, resulting in grease failure inside the flywheel.

The following embodiments of the dual mass flywheel of the present utility model are made in view of the above.

As shown in fig. 2-6B, one embodiment of the present utility model provides a dual mass flywheel that may include a primary mass 100, a spring 200, a secondary mass (which may include a hub member 300, a flange 400), and a diaphragm spring 500.

The primary mass 100 may include a first housing 110 and a second housing 120, the first housing 110 and the second housing 120 defining a spring receiving space that receives the spring 200. Here, the first housing 110 may be used to connect to a power source such as an engine.

Here, for example, the first housing 110 may include a radial portion 111 extending substantially along the radial direction RA and an axial portion 112 extending from the radial portion 111 toward the second housing 120. The radially outer end 121 of the second housing 120 may be welded to the axial portion 112, for example.

Here, as an example, the first housing 110 may be connected to a crankshaft of the engine.

The spring 200 may be an arc spring or a linear spring. By way of example only, the spring 200 may be a composite spring such as a metal spring, a rubber spring, an air spring, or a rubber metal coil composite spring.

The hub member 300 and the flange 400 may be integrally formed or separately provided and connected to each other. The spring 200 is disposed between the primary mass 100 and the secondary mass to attenuate torsional vibrations, and more particularly, the spring 200 may be disposed between the primary mass 100 and the flange 400 to attenuate torsional vibrations. Here, the hub member 300 may serve as an output portion for outputting torque from the first housing 110. Alternatively, the hub member 300 may also serve as an input, while the first housing 110 serves as an output.

Here, as an example, the hub part 300 may include a hub core 310 and a hub flange 320, and the hub flange 320 and the flange 400 may be fixedly coupled to each other by a plurality of coupling members such as rivets 410.

The diaphragm spring 500 is disposed in a compressed state between the secondary mass (more specifically, may be the flange 400) and the second housing 120 in the axial direction AX of the dual mass flywheel.

Here, the radially inner end 122 of the second housing 120 (or, in other words, the inner circumferential surface of the second housing 120) may be located closer to the radially inner side of the dual mass flywheel than the radially inner end of the diaphragm spring 500; of course, the radially inner end 122 of the second housing 120 may also be flush with the radially inner end of the diaphragm spring 500 in the radial direction RA. Thus, when the dual mass flywheel is installed, for example, between an engine and a transmission, the respective components of the transmission do not directly contact the diaphragm spring 500, and deformation of the diaphragm spring 500 during assembly may be avoided or reduced.

The diaphragm spring 500 is integrally located at the radially inner end 122 of the second housing 120, and both the radially outer end of the diaphragm spring 500 and the radially inner end 122 of the second housing 120 are located radially inward of the dual mass flywheel, which means that the gap or space between the diaphragm spring 500 and the second housing 120 is small, water is not easily accumulated, and thus the waterproof performance of the dual mass flywheel can be improved. Here, the flange 400 may include a base circle portion and flange wings protruding from the base circle portion toward the radial outside, and the flange wings may be pressed by the spring 200 to rotate the flange 400. Optionally, the base circles of the second housing 120 and flange 400 overlap in the radial direction RA of the dual mass flywheel. That is, the second casing 120 and the base circle portion have portions at the same radial height, or, viewed in the axial direction AX, there is a shade or overlap between the second casing 120 and the base circle portion.

Alternatively, referring to FIG. 4B, the radial length W1 of the second housing 120 is greater than 1/3 of the radius R of the dual mass flywheel. Preferably, the radial length W1 of the second housing 120 is greater than 2/5 of the radius R of the dual mass flywheel.

Here, the radial length W1 of the second casing 120 refers to a length located in half of the axial cross section of the second casing 120.

Here, a larger length or lengthened second housing 120 is proposed, the radial length W1 of the second housing 120 being increased, meaning that the waterproof height of the dual mass flywheel is increased. The dual-mass flywheel is less prone to water inflow, and the waterproof performance is improved.

Here, the radial length W1 of the second housing 120 is preferably less than 1/2 of the radius R of the dual mass flywheel. The radial length W1 of the second housing 120 being smaller than 1/2 of the radius R of the dual mass flywheel ensures that the second housing 120 is not unnecessarily lengthened, and that sufficient space is provided for radially inner structures such as the rivet 410, the mounting bolt through-hole 330, and the hub core 310, which will be described later.

Alternatively, referring to fig. 4B and 5B, the radial length W2 of the diaphragm spring 500 is less than 1/5 of the radius R of the dual mass flywheel, and more preferably less than 1/9 of the radius R of the dual mass flywheel.

Optionally, the radial length W2 of the diaphragm spring 500 is less than 2/5 of the radial length W1 of the second housing 120, preferably the radial length W2 of the diaphragm spring 500 is less than 1/4 of the radial length W1 of the second housing 120.

Alternatively, referring to fig. 5A and 5B, the dual mass flywheel further includes a first friction ring 600 (may also be referred to as a friction ring for a diaphragm spring), the first friction ring 600 being at least partially disposed between the secondary mass (particularly, the flange 400) and the diaphragm spring 500 in the axial direction AX, the diaphragm spring 500 being disposed between the first friction ring 600 and the second housing 120, and a length of the diaphragm spring 500 protruding from the first friction ring 600 may be less than 1/2 of a radial length W2 of the diaphragm spring 500. Alternatively, in the axial direction AX, the first friction ring 600 may also be at least partially disposed between the second housing and the diaphragm spring 500, the diaphragm spring 500 being disposed between the first friction ring 600 and the secondary mass.

Here, the diaphragm spring 500 having a small radial length is defined from different angles, which makes a gap between the diaphragm spring 500 and the second housing 120, which may constitute a water storage space, smaller, so that water is not easily left in the gap between the diaphragm spring 500 and the second housing 120 even when wading, and the waterproof performance of the dual mass flywheel can be improved.

Alternatively, referring to fig. 6B, the first friction ring 600 may include: an axial portion 620 extending along the axial direction AX; and a radial portion 610 extending from an axial end of the axial portion 620 along a radial direction RA of the dual mass flywheel.

Here, an inner circumferential portion of the diaphragm spring 500 may abut against the radial portion 610, and an outer circumferential portion of the diaphragm spring 500 may abut against the second housing 120. Alternatively, the inner peripheral portion of the diaphragm spring 500 may abut against the second housing 120, and the outer peripheral portion of the diaphragm spring 500 may abut against the radial portion 610.

Preferably, the axial portion 620 of the first friction ring 600 abuts against the radially inner end 122 of the second housing 120 in the radial direction RA, so that at the circumferential contact surface of the axial portion 620 opposite to the radially inner end 122, there is substantially no gap, whereby water can be prevented from entering the interior of the dual mass flywheel from the gap between the axial portion 620 and the radially inner end 122. While the radial portion 610 of the first friction ring 600 is abutted against the flange 400 by the axial force of the diaphragm spring 500, so that there is substantially no gap at the circumferential contact surface of the radial portion 610 opposite to the flange 400, whereby water can be prevented from entering the inside of the dual mass flywheel from the gap between the radial portion 610 and the flange 400. In this arrangement, it is possible to prevent water from entering the inside of the dual mass flywheel from the gap (extending radially to the inside of the dual mass flywheel) at the contact surface of the first friction ring 600 and the flange 400, and also to prevent water from entering the inside of the dual mass flywheel from the gap (extending axially to the inside of the dual mass flywheel) at the contact surface of the first friction ring 600 and the second housing 120, at the first friction ring 600, so that the gap between the flange 400 and the second housing 120 can be sealed well with the first friction ring 600 and the diaphragm spring 500, preventing water from entering the inside of the dual mass flywheel from between the flange 400 and the second housing 120.

Alternatively, referring to fig. 2, 6A and 6B, the radially inner end 122 of the second housing 120 may be formed with a plurality of (e.g., three) grooves 122G, the axial portion 620 includes a plurality of (e.g., three) protrusions 620P protruding radially outward from the outer circumferential surface of the axial portion 620, and the number and circumferential positions of the protrusions 620P correspond to the number and circumferential positions of the grooves 122G. Here, the protrusion 620P may be an example of the first structure, and the groove 122G may be an example of the second structure. The second structure may also be formed at the flange 400. The first structure is coupled with the second structure such that the first friction ring 600 is connected with the second housing 120 or the flange in a torsion-proof manner. When the dual mass flywheel is assembled, the protrusion 620P is received in the groove 122G, thereby preventing the first friction ring 600 from rotating with respect to the second housing 120, so that the diaphragm spring 500 does not rotate with respect to the second housing 120 or the first friction ring 600, and water does not easily enter the inside of the dual mass flywheel and from the gap between the diaphragm spring 500 and the second housing 120 or the first friction ring 600. Here, the diaphragm spring 500 may be made of metal, and the first friction ring 600 may be made of plastic. The first friction ring 600 made of plastic is in direct contact with the diaphragm spring 500 made of metal, compared to the flange 400 made of, for example, metal being in direct contact with the diaphragm spring 500 made of metal.

When the first friction ring 600 is installed, as shown in fig. 6A to 6B, the diaphragm spring 500 is first assembled with the first friction ring 600; then, each protrusion 620P is aligned with a corresponding groove 122G, and then each protrusion 620P is inserted into the groove 122G. During this insertion, the axial portion 620 of the first friction ring 600 is correspondingly inserted into the inside of the second housing 120. In addition, an auxiliary mounting (or tooling) structure may be provided at an end of the axial portion 620 opposite the radial portion 610 to retain the first friction ring 600 during installation and transport.

Although in this embodiment, the protrusion 620P is provided at the outer peripheral portion of the axial portion 620 of the first friction ring 600, the groove 122G is provided at the radially inner end 122 of the second housing 120; however, the recess may be a through hole. Alternatively, the outer peripheral portion of the axial portion 620 is provided as a groove, while the radially inner end 122 is provided with a projection, the groove being coupled with the projection; alternatively, protrusions and grooves are provided at the outer circumferential portion of the axial portion 620 of the first friction ring 600, and grooves and protrusions are provided at the radially inner end 122 of the second housing 120 correspondingly and couplably, the protrusions of the axial portion 620 being coupled with the grooves of the radially inner end 122, the grooves of the axial portion 620 being coupled with the protrusions of the radially inner end 122.

Although in this embodiment the first friction ring 600 is connected to the second housing 120 in a rotationally fixed manner, alternatively the first friction ring 600 can also be connected to the flange 400 in a rotationally fixed manner, in which case, for example, the first friction ring 600 can be inserted through its axial portion 620 into a corresponding structure on the flange 400, preferably in which case the axial portion 620 is of circumferentially discontinuous structure, i.e. has a plurality of fingers, and in which a plurality of recesses (in particular through holes) are provided in the flange 400, respectively, into which the fingers are inserted in order to rotationally fix the first friction ring 600 to the flange 400; while the radial portion 610 of the first friction ring 600 abuts against the first housing 120.

Alternatively, referring to fig. 5A and 5B, the dual mass flywheel may further include a support 700 and a second friction ring 800 (may also be referred to as a friction ring for a support), the support 700 and the second friction ring 800 being disposed between the first housing 110 and the hub member 300 to define an axial gap between the first housing 110 and the hub member 300. The cross section (axial cross section) of the second friction ring 800 may be stepped and include an axial portion 810, a first radial portion 820 extending radially outward from the axial portion 810, and a second radial portion 830 extending radially inward from the axial portion 810, the second radial portion 830 being pressed against the hub member 300 by the support 700.

The support 700 and the second friction ring 800 may prevent water from entering the interior of the dual mass flywheel, particularly into the location of the spring 200, from the gap between the hub member 300 and the first housing 110; and in particular, to restrict water entering the space between the hub member 300 and the first housing 110 from the through-holes 330 for mounting bolts from entering the inside of the dual mass flywheel.

Here, the support 700 may have a structure bent toward the second friction ring 800 and be in surface contact with the second radial portion 830. Here, the outer circumferential surface of the axial portion 810 may be substantially in contact with the inner circumferential surface of the flange 400, and the inner circumferential surface of the axial portion 810 may be substantially in contact with the outer Zhou Buda of the supporter 700, which facilitates the radial positioning of the second friction ring 800. Alternatively, since the support 700 and the second radial portion 830 and the hub member 300 are pressed against each other in the axial direction such that there is no gap between the contact portions of the three, the outer circumferential surface of the axial portion 810 may not contact the inner circumferential surface of the flange 400, and the inner circumferential surface of the axial portion 810 may not contact the outer circumferential portion of the support 700.

The curved structure and large contact area of the support 700 and the second friction ring 800 improves the waterproof performance of the dual mass flywheel.

Referring to, for example, fig. 5A, a plurality of through holes 330 for mounting bolts may be formed on the hub flange 320 of the hub member 300, and bolts may pass through the through holes 330 for mounting bolts to fix the support 700 together with the first housing 110 to, for example, a crankshaft of an engine.

The second friction ring 800 is located radially outside the mounting bolt through hole 330.

As described above, the present utility model provides a dual mass flywheel employing an elongated second housing 120 and a small diaphragm spring 500, on the one hand, the elongated second housing 120 increases the waterproof height of the dual mass flywheel; on the other hand, the diaphragm spring 500 is not easily deformed, the radius of action of the diaphragm spring 500 is reduced, and the diaphragm spring capable of providing a larger axial force can be designed.

In the dual-mass flywheel, almost no water storage space exists near the diaphragm spring 500, and water is not easy to enter the flywheel from the diaphragm spring 500, so that the failure of grease in the flywheel due to water inflow can be prevented, the waterproof performance of the flywheel can be remarkably improved, and the performance and durability of the dual-mass flywheel can be improved.

It should be understood that the above-described embodiments are merely exemplary and are not intended to limit the present utility model. Those skilled in the art can make various modifications and changes to the above-described embodiments without departing from the scope of the present utility model.

Claims

1. A dual mass flywheel, comprising:

a spring (200);

a primary mass (100) comprising a first housing (110) and a second housing (120), the first housing (110) and the second housing (120) defining a spring receiving space for receiving the spring (200);

a secondary mass, the spring (200) being arranged between the primary mass (100) and the secondary mass to dampen torsional vibrations; and

a diaphragm spring (500), the diaphragm spring (500) being arranged in a compressed state between the secondary mass and the second housing (120) in an axial direction (AX) of the dual mass flywheel,

it is characterized in that the method comprises the steps of,

the radially inner end (122) of the second housing (120) is closer to the radially inner side of the dual mass flywheel than the radially inner end of the diaphragm spring (500), or the radially inner end (122) of the second housing (120) is flush with the radially inner end of the diaphragm spring (500) in the radial direction (RA) of the dual mass flywheel, the dual mass flywheel further comprising a first friction ring (600), the first friction ring (600) comprising: an axial portion (620) extending along the axial direction (AX); and a radial portion (610) connected to the axial portion (620) and extending in a radial direction (RA) of the dual mass flywheel, the radial portion (610) being axially abutted against the flange (400) of the secondary mass or the second housing (120) under the action of the diaphragm spring (500); the axial portion (620) radially abuts the flange (400) of the secondary mass or the second housing (120).

2. A dual mass flywheel according to claim 1, characterized in that the radial length (W1) of the second housing (120) is greater than 1/3 of the radius (R) of the dual mass flywheel.

3. A dual mass flywheel according to claim 1, characterized in that the radial length (W1) of the second housing (120) 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.

4. A dual mass flywheel according to claim 1, characterized in that the radial length (W2) of the diaphragm spring (500) is less than 1/5 of the radius (R) of the dual mass flywheel.

5. A dual mass flywheel according to claim 1, characterized in that the radial length (W2) of the diaphragm spring (500) is less than 1/9 of the radius (R) of the dual mass flywheel.

6. The dual mass flywheel according to any of claims 1 to 5, further comprising a first friction ring (600), said first friction ring (600) being at least partially arranged between said secondary mass and said diaphragm spring (500) in said axial direction (AX), said diaphragm spring (500) being arranged between said first friction ring (600) and said second housing (120); or,

in the axial direction (AX), the first friction ring (600) is at least partially arranged between the second housing and the diaphragm spring (500), the diaphragm spring (500) being arranged between the first friction ring (600) and the secondary mass.

7. The dual mass flywheel of claim 6, characterized in that the first friction ring (600) is at least partially disposed between a flange (400) as at least a portion of the secondary mass and the diaphragm spring (500).

8. The dual mass flywheel of claim 6, characterized in that one or more protrusions protruding radially outwards are provided at the outer peripheral portion of the axial portion, and one or more recesses corresponding to the protrusions are provided at the radially inner end (122) of the second housing (120), the protrusions being correspondingly coupled with the recesses; or,

one or more recesses recessed toward the radial inside are provided at the outer peripheral portion of the axial portion, and one or more projections corresponding to the recesses are provided at the radial inside end (122) of the second housing (120), the projections being correspondingly coupled with the recesses.

9. The dual mass flywheel of claim 7, characterized in that one or more protrusions protruding radially outwards are provided at the outer peripheral portion of the axial portion, and one or more recesses corresponding to the protrusions are provided at the radially inner end (122) of the second housing (120), the protrusions being correspondingly coupled with the recesses; or,

10. The dual mass flywheel of claim 6, wherein the first friction ring further has an auxiliary mounting structure disposed thereon.

11. The dual mass flywheel of claim 7, wherein the first friction ring further has an auxiliary mounting structure disposed thereon.

12. The dual mass flywheel of claim 1, characterized in that the diaphragm spring (500) is made of metal and the first friction ring (600) is made of plastic.

13. The dual mass flywheel of any of claims 1-5, further comprising a support (700) and a second friction ring (800), the support (700) and the second friction ring (800) being disposed between the first housing (110) and the secondary mass, thereby defining an axial gap between the first housing (110) and the secondary mass,

the second friction ring (800) is stepped in cross section and comprises an axial portion (810), a first radial portion (820) extending radially outward from the axial portion (810), and a second radial portion (830) extending radially inward from the axial portion (810), the second radial portion (830) being pressed against the secondary mass by the support (700).

14. The dual mass flywheel of claim 13, characterized in that the support (700) and the second friction ring (800) are disposed between the first housing (110) and a hub member (300) that is part of the secondary mass, thereby defining an axial gap between the first housing (110) and the hub member (300),

the second radial portion (830) is pressed against the hub component (300) by the support (700).