Dual mass flywheel and vehicle

Abstract

The invention relates to a dual mass flywheel which comprises a first flywheel and a second flywheel which are coaxially arranged and can rotate relative to each other around an axis X; the driving disc is arranged between the first flywheel and the second flywheel and rotates synchronously with the second flywheel; the first spring and the second spring are arranged between the first flywheel and the second flywheel. When the second flywheel rotates within a first angle range relative to the first flywheel, both the first spring and the second spring are not compressed by the driving disc, and when the second flywheel rotates within a second angle range relative to the first flywheel, one of the first spring and the second spring is compressed by the driving disc. And when the second flywheel rotates within a third angle range relative to the first flywheel, both the first spring and the second spring are compressed by the driving disc. The present disclosure also relates to a vehicle comprising such a dual mass flywheel.

Description

Technical Field

[0001] The present disclosure relates to a dual mass flywheel. In particular, the dual mass flywheel can reduce the idle noise of a vehicle. The present disclosure also relates to a vehicle comprising such a dual mass flywheel. Background Art

[0002] The torque generated by a vehicle engine is usually not constant. This inconstant torque can be transmitted to the transmission gearbox, causing vibrations in the transmission gearbox and thus generating particularly undesirable noise or knocks, etc. In order to reduce the adverse effects of vibrations and improve the driving comfort of the vehicle, it is known to equip the torque transmission device of the vehicle drive train with a torsional vibration damping device. The torsional vibration damping device can allow the vibrations generated by the vehicle engine to be absorbed and damped.

[0003] A known torsional vibration damping device is a dual mass flywheel, which has two flywheels that can rotate relative to each other about a rotation axis and a spring arranged between the two flywheels. When the torque and / or speed generated by the engine fluctuate, the two flywheels rotate relative to each other, and the spring is compressed or extended, thereby absorbing and reducing the vibration generated by the vehicle engine.

[0004] However, the spring in the dual-mass flywheel will contact the actuator and produce a knocking noise when it starts to be compressed. This noise is more prominent when the vehicle is idling, becoming an important source of vehicle idling noise. Summary of the invention

[0005] Therefore, the present disclosure aims to solve the above-mentioned problems existing in the conventional dual mass flywheel, and its object is to provide a dual mass flywheel, in which the knocking noise generated by the knocking spring is suppressed, thereby reducing the idle noise of the vehicle as a whole.

[0006] The objective is achieved by a dual mass flywheel according to an embodiment of the present disclosure. The dual mass flywheel comprises: a first flywheel and a second flywheel arranged coaxially, the first flywheel and the second flywheel being able to rotate relative to each other around an axis X; a drive plate, which is arranged between the first flywheel and the second flywheel and rotates synchronously with one of the first flywheel and the second flywheel; a first spring and a second spring disposed between the first flywheel and the second flywheel. When the second flywheel rotates relative to the first flywheel within a first angular range, neither the first spring nor the second spring is compressed by the drive plate; when the second flywheel rotates relative to the first flywheel within a second angular range, one of the first spring and the second spring is compressed by the drive plate; and when the second flywheel rotates relative to the first flywheel within a third angular range, both the first spring and the second spring are compressed by the drive plate.

[0007] One of the purposes of the present disclosure is to provide a dual-mass flywheel that can suppress the knocking noise generated by knocking springs. The dual-mass flywheel according to the present disclosure has two springs, and the relative rotation between the first flywheel and the second flywheel is divided into three angle ranges. In the first angle range, the drive disk does not interact with the spring. In the second angle range, the drive disk only compresses one of the two springs, that is, only knocks one spring. Compared with knocking two springs at the same time, this design reduces the knocking force and achieves the effect of reducing noise.

[0008] The dual mass flywheel according to the present disclosure may also have one or more of the following features, alone or in combination.

[0009] According to an optional embodiment of the present disclosure, the driving plate includes a first driving portion and a second driving portion, and the first driving portion and the second driving portion can contact the end of the first spring or the second spring to compress the first spring or the second spring.

[0010] According to an optional embodiment of the present disclosure, both the first spring and the second spring have an arc shape, and the dual mass flywheel further includes: an annular guide fixed relative to the other of the first flywheel and the second flywheel; and a first stopper and a second stopper having an arc shape fixed relative to the other of the first flywheel and the second flywheel. The first stopper and the second stopper separate the annular guide into a first guide portion and a second guide portion, and the first guide portion is used to accommodate and guide the first spring, and the second guide portion is used to accommodate and guide the second spring.

[0011] According to an optional embodiment of the present disclosure, the circumferential angle of the first guide portion is greater than or equal to the circumferential angle of the first spring, so that the first spring can freely move a first distance in the first guide portion without being compressed, and the first distance is greater than or equal to zero; the circumferential angle of the second guide portion is greater than or equal to the circumferential angle of the second spring, so that the second spring can freely move a second distance in the second guide portion without being compressed, and the second distance is greater than or equal to zero, wherein the second distance is not equal to the first distance. In particular, one of the first distance and the second distance can be zero, and the other of the first distance and the second distance is not zero. Accordingly, when the drive disk begins to compress one of the first spring and the second spring, the other of the first spring and the second spring can also freely move a distance in the second guide portion without being compressed.

[0012] According to an optional embodiment of the present disclosure, the first guide portion and the second guide portion are radially opposite to each other and have the same circumferential angle, and the first spring and the second spring have the same circumferential angle.

[0013] According to an optional embodiment of the present disclosure, the first driving part and the second driving part are diametrically opposite and have the same circumferential angle, and the dual mass flywheel further includes a spring seat. The spring seat is attached to one end of the first spring, and the circumferential angle of the first guide part is greater than or equal to the circumferential angle of the first spring plus the spring seat; or the spring seat is attached to one end of the second spring, and the circumferential angle of the second guide part is greater than or equal to the circumferential angle of the second spring plus the spring seat. In this embodiment, when the spring to which the spring seat is attached begins to be compressed, the drive plate will not yet contact the other spring, so that the spring will not be compressed.

[0014] According to an optional embodiment of the present disclosure, the first driving part and the second driving part have the same circumferential angle but are not radially opposite. Thus, when the driving disk rotates to make one of the first driving part and the second driving part contact one spring, the other of the first driving part and the second driving part has not yet contacted the other spring, so that the spring will not be compressed.

[0015] According to an optional embodiment of the present disclosure, the first driving portion and the second driving portion are radially opposite to each other but have different circumferential angles.

[0016] According to an optional embodiment of the present disclosure, the first driving portion and the second driving portion are radially opposite to each other and have the same circumferential angle, and the first spring and the second spring have the same circumferential angle.

[0017] According to an optional embodiment of the present disclosure, the first stopper and the second stopper are radially opposite to each other, and the circumferential angles of the first stopper and the second stopper are unequal.

[0018] According to an optional embodiment of the present disclosure, the first guide portion and the second guide portion are radially opposite to each other and have the same circumferential angle, the first drive portion and the second drive portion are radially opposite to each other and have the same circumferential angle, and the circumferential angles of the first spring and the second spring are unequal.

[0019] According to an optional embodiment of the present disclosure, the first guide portion and the second guide portion are radially opposite to each other, and the circumferential angles of the first guide portion and the second guide portion are unequal.

[0020] The present disclosure also provides a vehicle, which includes the dual mass flywheel as described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The above and other features and advantages of the present disclosure will become more apparent through the following detailed description of exemplary embodiments in conjunction with the accompanying drawings, and the description and drawings are only for illustrative purposes and are not intended to limit the scope of the present disclosure in any way. The following drawings are not deliberately drawn to scale with actual size, and the focus is on illustrating the subject matter of the present disclosure.

[0022] Figure 1 is a schematic diagram of a dual mass flywheel according to one embodiment of the present disclosure.

[0023] Figure 2 is a schematic diagram of a dual mass flywheel according to another embodiment of the present disclosure.

[0024] Figure 3 A graph of spring force versus torsion angle is shown.

[0025] Throughout the drawings, the same or similar components are indicated by the same reference numerals. DETAILED DESCRIPTION

[0026] In order to make the purpose, technical solution and advantages of the embodiments of the present disclosure clearer, the technical solution of the embodiments of the present disclosure will be clearly and completely described below in conjunction with the drawings of the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, not all of them.

[0027] Unless otherwise defined, the technical terms or scientific terms used herein should be the common meanings understood by ordinary technicians in the field to which the present disclosure belongs. Similar words such as "one", "one" or "the" used in the present patent application specification and claims do not indicate a quantitative limitation, but indicate the existence of at least one. The terms "including", "having" and the like are used in the present disclosure to specify the existence of the features, numbers, steps, operations, elements, parts or combinations thereof, but do not exclude the existence or addition of one or more other features, numbers, steps, operations, elements, parts or combinations thereof. In addition, even if terms including ordinal numbers such as "first" and "second" can be used to describe various parts, these parts are not limited by these terms, and these terms are only used to distinguish one element from other elements. For example, without departing from the scope of the present disclosure, the first component can be referred to as the second component, and similarly, the second component can be referred to as the first component.

[0028] In the description of the present disclosure, it is to be understood that the terms "upper", "lower", "left", "right", "inner", "outer", etc. are only for the convenience of describing the present disclosure and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present disclosure. Directions such as "axial", "radial" and "circumferential" are defined relative to the axis of rotation of the dual mass flywheel, the axial direction is the direction in which the axis of rotation X extends, the radial direction is the direction perpendicular to the axis of rotation X, and the circumferential direction is the circumferential direction around the axis of rotation X. "Circumferential angle" refers to the angle at which a component or feature extends in the circumferential direction around the axis of rotation X.

[0029] Figure 1 and Figure 2 The dual mass flywheel 100 according to the first embodiment and the second embodiment of the present disclosure are respectively shown. For the sake of clarity, parts of the dual mass flywheel that are not related to the understanding of the technical solution of the present disclosure are omitted.

[0030] exist Figure 1 In the first embodiment shown, the dual mass flywheel 100 includes a first flywheel 1 and a second flywheel 2 arranged coaxially, which can rotate relative to each other around an axis X. The first flywheel 1 and the second flywheel 2 can be connected to an engine and a gearbox, respectively, to serve as an input side and an output side of the dual mass flywheel 100. Two springs, namely a first spring 4a and a second spring 4b, are disposed between the first flywheel 1 and the second flywheel 2. The first spring 4a and the second spring 4b are, for example, arc-shaped helical compression springs, and can act with the first flywheel 1 and the second flywheel 2 to suppress fluctuations in the torque transmitted between the first flywheel 1 and the second flywheel 2.

[0031] The dual mass flywheel 100 includes a drive disc 3 arranged between a first flywheel 1 and a second flywheel 2 and rotating synchronously with the second flywheel 2. The drive disc 3 includes a first drive portion 31 and a second drive portion 32. The dual mass flywheel 100 also includes an annular guide 11 fixed relatively to the first flywheel 1. The annular guide 11 is, for example, an annular channel formed by the curling of the first flywheel 1. The annular guide 11 is divided into two parts, a first guide portion 11a and a second guide portion 11b, by a first stopper 12a and a second stopper 12b fixed relatively to the first flywheel 1 and having an arc shape. The circumferential angle of the first guide portion 11a is greater than or equal to the circumferential angle of the first spring 4a, so that the first spring 4a can be accommodated in the first guide portion 11a and guided by it. Similarly, the second spring 4b is accommodated in the second guide portion 11b and guided by it.

[0032] It is understandable that the drive disc 3 can also be set to rotate synchronously with the first flywheel 1, and the annular guide 11 and the first stopper 12a and the second stopper 12b can be set to be relatively fixed with the second flywheel 2. When relative rotation occurs between the first flywheel 1 and the second flywheel 2, the first drive portion 31 and the second drive portion 32 of the drive disc 3 can contact the end of the first spring 4a or the second spring 4b respectively, thereby actuating the first spring 4a or the second spring 4b. For example, as Figure 1 As shown, when the second flywheel 2 rotates clockwise relative to the first flywheel 1, the first drive portion 31 contacts the upper end of the first spring 4a, and pushes the first spring 4a to rotate clockwise around the axis X in the first guide portion 11a. When the lower end of the first spring 4a abuts against the second stopper 12b, the first spring 4a can no longer continue to rotate, and is compressed by the first drive portion 31. Similarly, the second spring 4b can be pushed by the second drive portion 32 to rotate in the second guide portion 11b and be compressed against the first stopper 12a. When the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the first drive portion 31 pushes the second spring 4b to rotate in the second guide portion 11b and makes it abut against the second stopper 12b to be compressed; the second drive portion 32 pushes the first spring 4a to rotate in the first guide portion 11a and makes it abut against the first stopper 12a to be compressed.

[0033] When the dual mass flywheel 100 has a symmetrical structure, the driving plate 3 compresses the first spring 4a and the second spring 4b simultaneously through the first driving part 31 and the second driving part 32, so that the dual mass flywheel 100 has a large torsional rigidity. The acting force between the first and second driving parts and the first and second springs is large, which produces a large knocking noise. In order to reduce this knocking noise, it is necessary to reduce the torsional rigidity of the dual mass flywheel. In the dual mass flywheel, the torsional rigidity is proportional to the square root of the elastic coefficient of the spring. Therefore, the dual mass flywheel 100 can be set so that only one spring is compressed within a certain torsional angle range. Compared with the two springs being compressed at the same time, the torsional rigidity of the dual mass flywheel can be reduced by about 30%.

[0034] refer to Figure 3, the rotation angle of the second flywheel 2 relative to the first flywheel 1 (i.e., the torsion angle of the dual mass flywheel 100) can be divided into three sections. Taking clockwise rotation (without loss of generality, the torsion angle of clockwise rotation can be set as positive, and the torsion angle of counterclockwise rotation can be set as negative) as an example, in the first angle range where the torsion angle is less than θ0, the first spring 4a and the second spring 4b are not compressed, corresponding to the idle stroke range of the dual mass flywheel 100; when the torsion angle is in the second angle range between θ0 and θ1, only one of the first spring 4a and the second spring 4b is compressed by the drive disc 3, corresponding to the stroke range where the dual mass flywheel 100 has a smaller torsional stiffness; when the torsion angle is in the third angle range between θ1 and θ3 (θ3 is the predetermined maximum torsion angle of the dual mass flywheel 100), both the first spring 4a and the second spring 4b are compressed by the drive disc 3, corresponding to the stroke range where the dual mass flywheel 100 has a larger torsional stiffness. Counterclockwise rotation also has a similar segmented stroke. The above design reduces the knocking noise by the segmented travel of the dual mass flywheel. In particular, when the vehicle is idling, the torque transmitted by the dual mass flywheel 100 is small, and the torsion angle in the second angle range can meet most situations, thereby further suppressing the knocking noise and reducing the idling noise of the vehicle as a whole.

[0035] The above-mentioned segmented stroke can be realized by various asymmetric structures of the dual mass flywheel 100 .

[0036] For example, the distances that the first spring 4a and the second spring 4b can freely move in the first guide portion 11a and the second guide portion 11b can be set to be unequal, thereby obtaining an asymmetric dual mass flywheel 100. Figure 1 In the first embodiment shown, the annular guide 11 and the drive plate 3 are symmetrical, and both can overlap after 180° rotation. That is, the first guide portion 11a and the second guide portion 11b are diametrically opposed and have the same circumferential angle, and the first drive portion 31 and the second drive portion 32 are diametrically opposed and have the same circumferential angle. Naturally, the first stopper 12a and the second stopper 12b separating the first guide portion 11a and the second guide portion 11b are also diametrically opposed and have the same circumferential angle. In this embodiment, the first spring 4a and the second spring 4b also have the same circumferential angle. The asymmetric structure of the dual mass flywheel 100 is embodied in that a spring seat 5 is attached to the end of the first spring 4a close to the first stopper 12a. The circumferential angle of the assembly consisting of the first spring 4a and the spring seat 5 is greater than the circumferential angle of the second spring 4b.

[0037] When the second flywheel 2 rotates clockwise relative to the first flywheel 1, the driving disc 3 can first push the assembly consisting of the first spring 4a and the spring seat 5 and the second spring 4b to move freely in the first guide portion 11a and the second guide portion 11b respectively. At this time, neither of the two springs is compressed, and the torsion angle of the dual mass flywheel 100 is within a first angle range less than θ0. After moving the first distance, the assembly consisting of the first spring 4a and the spring seat 5 abuts against the second stopper 12b, thereby being compressed by the first driving portion 31. Since the circumferential angle is relatively small, the second spring 4b will not be compressed at this time, but will abut against the first stopper 12a and be compressed by the second driving portion 32 after moving the second distance greater than the first distance. Similarly, when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the assembly consisting of the first spring 4a and the spring seat 5 first abuts against the first stopper 12a and is compressed by the first driving portion 31, and then the second spring 4b abuts against the second stopper 12b and is compressed by the second driving portion 32. The second angular range and the third angular range of the torsion angle of dual mass flywheel 100 are thereby defined.

[0038] It is easy to understand that the spring seat 5 can also be attached to the end of the first spring 4a close to the second stopper 12b, or attached to either end of the second spring 4b.

[0039] Figure 2 1 shows a second embodiment of the present disclosure. Different from the first embodiment, no spring seat is added to the first spring 4a and the second spring 4b, and the drive plate 3 in the dual mass flywheel 100 is asymmetrical. Specifically, the first drive portion 31 and the second drive portion 32 have the same circumferential angle, but the two are not radially opposite. The drive plate 3 can no longer overlap after rotating 180°. Figure 2 As shown, compared with the radially opposite position, the second driving portion 32 is offset by a certain angle in the clockwise direction.

[0040] In this embodiment, when the second flywheel 2 rotates clockwise relative to the first flywheel 1, the second spring 4b is first pushed by the second drive unit 32 to abut against the first stopper 12a and compressed, and then the first spring 4a is pushed by the first drive unit 31 to abut against the second stopper 12b and compressed; when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the second spring 4b is first pushed by the first drive unit 31 to abut against the second stopper 12b and compressed, and then the first spring 4a is pushed by the second drive unit 32 to abut against the first stopper 12a and compressed. The second angle range and the third angle range of the torsion angle of the dual mass flywheel 100 are thus defined.

[0041] Although not shown in the drawings, it is conceivable that the first drive portion 31 and the second drive portion 32 of the drive disc 3 can also be arranged to be diametrically opposed, but have different circumferential angles. That is, the drive disc 3 is mirror-symmetrical, but can no longer overlap after rotating 180°. Without loss of generality, it can be assumed that the second drive portion 32 has a larger circumferential angle. When the second flywheel 2 rotates clockwise relative to the first flywheel 1, the second spring 4b is first pushed against the first stopper 12a by the second drive portion 32 and compressed, and then the first spring 4a is pushed against the second stopper 12b by the first drive portion 31 and compressed; when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the first spring 4a is first pushed against the first stopper 12a by the second drive portion 32 and compressed, and the second spring 4b is pushed against the second stopper 12b by the first drive portion 31 and compressed. The second angle range and the third angle range of the torsion angle of the dual mass flywheel 100 are thus defined.

[0042] The asymmetric structure of the dual mass flywheel 100 can also be achieved by setting the annular guide 11 to be asymmetric. In such an embodiment, the drive plate 3 is symmetrical, and the first drive portion 31 and the second drive portion 32 are diametrically opposite and have the same circumferential angle. The first spring 4a and the second spring 4b also have the same circumferential angle, and no spring seat is added.

[0043] Specifically, the first stopper 12a and the second stopper 12b separating the annular guide 11 may be arranged to be diametrically opposed but have unequal circumferential angles. Correspondingly, the first guide portion 11a and the second guide portion 11b of the annular guide 11 have equal circumferential angles but are not diametrically opposed. In other words, the annular guide 11 is mirror-symmetrical, but can no longer overlap after being rotated 180°. Without loss of generality, it can be assumed that the second stopper 12b has a larger circumferential angle. When the second flywheel 2 rotates clockwise relative to the first flywheel 1, the first spring 4a is first pushed by the first drive unit 31 to abut against the second stopper 12b and is compressed, and then the second spring 4b is pushed by the second drive unit 32 to abut against the first stopper 12a and is compressed; when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the second spring 4b is first pushed by the first drive unit 31 to abut against the second stopper 12b and is compressed, and then the second spring 4a is pushed by the second drive unit 32 to abut against the first stopper 12a and is compressed. The second angle range and the third angle range of the torsion angle of the dual mass flywheel 100 are thus defined.

[0044] Optionally, the first stopper 12a and the second stopper 12b separating the annular guide 11 may also be arranged to have equal circumferential angles but not be diametrically opposed. Correspondingly, the first guide portion 11a and the second guide portion 11b of the annular guide 11 are diametrically opposed, but the circumferential angles are unequal. In other words, the annular guide 11 is mirror-symmetrical, but can no longer overlap after rotating 180°. Without loss of generality, it can be assumed that the second stopper 12b is offset clockwise by a certain angle, and the circumferential angle of the first guide portion 11a is greater than that of the second guide portion 11b. In this way, when the second flywheel 2 rotates clockwise relative to the first flywheel 1, the second spring 4b is first pushed by the second drive unit 32 to abut against the first stopper 12a and compressed, and then the first spring 4a is pushed by the first drive unit 31 to abut against the second stopper 12b and compressed; when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the second spring 4b is first pushed by the first drive unit 31 to abut against the second stopper 12b and compressed, and then the first spring 4a is pushed by the second drive unit 32 to abut against the first stopper 12a and compressed. The second angle range and the third angle range of the torsion angle of the dual mass flywheel 100 are thus defined.

[0045] The first spring 4a and the second spring 4b in the above-mentioned embodiments have the same circumferential angle and are interchangeable. It is conceivable that the asymmetric structure of the dual mass flywheel 100 can also be achieved by making the first spring 4a and the second spring 4b have unequal circumferential angles. In such an embodiment, the annular guide 11 and the drive plate 3 are symmetrical. Without loss of generality, it can be assumed that the circumferential angle of the first spring 4a is greater than that of the second spring 4b. In this way, when the second flywheel 2 rotates clockwise relative to the first flywheel 1, the first spring 4a is first pushed against the second stopper 12b by the first drive part 31 and compressed, and then the second spring 4b is pushed against the first stopper 12a by the second drive part 32 and compressed; when the second flywheel 2 rotates counterclockwise relative to the first flywheel 1, the first spring 4a is first pushed against the first stopper 12a by the second drive part 32 and compressed, and then the second spring 4b is pushed against the second stopper 12b by the first drive part 31 and compressed. The second angular range and the third angular range of the torsion angle of dual mass flywheel 100 are thereby defined.

[0046] Multiple embodiments of the dual mass flywheel 100 are described above. The above embodiments achieve a segmented stroke of the dual mass flywheel 100 through a variety of asymmetric structures, reducing the torsional stiffness of the dual mass flywheel 100 at low torsion angles, thereby suppressing the knocking noise of the dual mass flywheel 100 and achieving the effect of reducing the idling noise of the vehicle.

[0047] Although not shown in the drawings, it can be imagined by those skilled in the art that the number of springs of the dual mass flywheel 100 can be greater than two. Correspondingly, the number of driving parts of the driving plate, the number of stoppers, and the number of guide parts of the separated annular guides can all be greater than two.

[0048] According to yet another aspect of the present disclosure, a vehicle is provided, comprising the dual mass flywheel 100 as described above.

[0049] Certain features, structures or characteristics in one or more embodiments of the present disclosure may be appropriately combined.

[0050] The above is an explanation of the present disclosure and should not be considered as a limitation thereof. Although several exemplary embodiments of the present disclosure are described, it will be readily appreciated by those skilled in the art that many modifications may be made to the exemplary embodiments without departing from the novel teachings and advantages of the present disclosure. Therefore, all such modifications are intended to be included within the scope of the present disclosure as defined in the claims. It should be understood that the above is an explanation of the present disclosure and the present disclosure should not be considered to be limited to the specific embodiments disclosed, and modifications to the disclosed embodiments and other embodiments are intended to be included within the scope of the present disclosure.

Claims

1. A dual mass flywheel (100), characterized in that: The dual mass flywheel (100) comprises: A first flywheel (1) and a second flywheel (2) are coaxially arranged, wherein the first flywheel (1) and the second flywheel (2) are capable of rotating relative to each other around an axis X; a driving disc (3) arranged between the first flywheel (1) and the second flywheel (2) and rotating synchronously with one of the first flywheel (1) and the second flywheel (2); A first spring (4a) and a second spring (4b) are disposed between the first flywheel (1) and the second flywheel (2), wherein When the second flywheel (2) rotates relative to the first flywheel (1) within a first angular range, neither the first spring (4a) nor the second spring (4b) is compressed by the driving disc (3). When the second flywheel (2) rotates relative to the first flywheel (1) within a second angular range, one of the first spring (4a) and the second spring (4b) is compressed by the driving disc (3), and When the second flywheel (2) rotates relative to the first flywheel (1) within a third angular range, both the first spring (4a) and the second spring (4b) are compressed by the driving plate (3).

2. The dual mass flywheel (100) according to claim 1, characterized in that The driving disk (3) comprises a first driving portion (31) and a second driving portion (32), wherein the first driving portion (31) and the second driving portion (32) are capable of contacting an end of a first spring (4a) or a second spring (4b) to compress the first spring (4a) or the second spring (4b).

3. The dual mass flywheel (100) according to claim 2, characterized in that The first spring (4a) and the second spring (4b) both have an arc shape, and the dual mass flywheel further comprises: an annular guide (11) fixed relative to the other of the first flywheel (1) and the second flywheel (2); and A first stopper (12a) and a second stopper (12b) having an arc shape and fixed relatively to the other of the first flywheel (1) and the second flywheel (2); The first stopper (12a) and the second stopper (12b) separate the annular guide (11) into a first guide portion (11a) and a second guide portion (11b), and The first guide portion (11a) is used to accommodate and guide the first spring (4a), and the second guide portion (11b) is used to accommodate and guide the second spring (4b).

4. The dual mass flywheel (100) according to claim 3, characterized in that The circumferential angle of the first guide portion (11a) is greater than or equal to the circumferential angle of the first spring (4a), so that the first spring (4a) can freely move a first distance in the first guide portion (11a) without being compressed, and the first distance is greater than or equal to zero, The circumferential angle of the second guide portion (11b) is greater than or equal to the circumferential angle of the second spring (4b), so that the second spring (4b) can freely move a second distance in the second guide portion (11b) without being compressed, and the second distance is greater than or equal to zero, wherein the second distance is not equal to the first distance.

5. The dual mass flywheel (100) according to claim 3, characterized in that The first guide portion (11a) and the second guide portion (11b) are radially opposite to each other and have the same circumferential angle, and The first spring (4a) and the second spring (4b) have the same circumferential angle.

6. The dual mass flywheel (100) according to claim 5, characterized in that The first driving part (31) and the second driving part (32) are radially opposite to each other and have the same circumferential angle, and the dual mass flywheel (100) further comprises a spring seat (5), wherein The spring seat (5) is attached to one end of the first spring (4a), and the circumferential angle of the first guide portion (11a) is greater than or equal to the circumferential angle of the first spring (4a) plus the spring seat (5); or The spring seat (5) is attached to one end of the second spring (4b), and the circumferential angle of the second guide portion (11b) is greater than or equal to the circumferential angle of the second spring (4b) plus the spring seat (5).

7. The dual mass flywheel (100) according to claim 5, characterized in that The first driving portion (31) and the second driving portion (32) have the same circumferential angle but are not radially opposite.

8. The dual mass flywheel (100) according to claim 5, characterized in that The first driving portion (31) and the second driving portion (32) are radially opposite to each other but have different circumferential angles.

9. The dual mass flywheel (100) according to claim 3, characterized in that The first driving part (31) and the second driving part (32) are radially opposite to each other and have the same circumferential angle, and The first spring (4a) and the second spring (4b) have the same circumferential angle.

10. The dual mass flywheel (100) according to claim 9, characterized in that The first stopper (12a) and the second stopper (12b) are radially opposite to each other, and the circumferential angles of the first stopper (12a) and the second stopper (12b) are unequal.

11. The dual mass flywheel (100) according to claim 9, characterized in that The first guide portion (11a) and the second guide portion (11b) are radially opposite to each other, and the circumferential angles of the first guide portion (11a) and the second guide portion (11b) are unequal.

12. The dual mass flywheel (100) according to claim 3, characterized in that The first guide portion (11a) and the second guide portion (11b) are radially opposite to each other and have the same circumferential angle. The first driving part (31) and the second driving part (32) are radially opposite to each other and have the same circumferential angle, and The circumferential angles of the first spring (4a) and the second spring (4b) are unequal.

13. A vehicle, characterized in that: The vehicle comprises a dual mass flywheel (100) according to any one of claims 1 to 12.

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