Dual mass flywheel and vehicle

Abstract

The present disclosure relates to a dual mass flywheel (100) comprising a primary mass assembly (100a), a secondary mass assembly (100b) and a spring assembly (100c) arranged between the primary mass assembly (100a) and the secondary mass assembly (100b). The primary mass assembly (100a) and the secondary mass assembly (100b) are rotatable about an axis of rotation (X) and are able to rotate relative to each other against the spring assembly (100c). The secondary mass assembly (100b) comprises a torque limiter (10) comprising: two support discs (20) axially superposed; an intermediate disc (30) arranged axially between the two support discs (20). At least one of the two support discs (20) has an elastically deformable zone (d), the two support discs (20) being fastened together so that the elastically deformable zone (d) is elastically deformed, clamping the intermediate disc (30) between the two support discs (20). The present disclosure also relates to a vehicle comprising such a dual mass flywheel (100).

Description

Technical Field

[0001] This disclosure relates to a dual-mass flywheel. This disclosure also relates to a vehicle comprising such a dual-mass flywheel. Background Technology

[0002] The torque produced by a motor vehicle engine is typically non-constant and frequently fluctuates. This non-constant torque can be transmitted to the gearbox, causing gearbox vibration and thus generating particularly undesirable noise or impacts. To reduce the adverse effects of vibration and improve vehicle driving comfort, it is known to equip the vehicle's drivetrain with torque fluctuation absorption mechanisms. These mechanisms allow for the limitation and absorption of fluctuations in the torque generated by the vehicle's engine.

[0003] One known torque fluctuation absorption mechanism is a dual-mass flywheel having a primary mass, a secondary mass, and a spring arranged between the two masses, all capable of rotating relative to each other about a rotational axis. When the torque and / or speed generated by the engine fluctuates, the relative rotation between the primary and secondary masses causes the spring to compress or extend, thereby absorbing and mitigating the torque fluctuations.

[0004] Furthermore, it is known that a torque limiter is integrated into the secondary mass of a dual-mass flywheel to limit the maximum torque that the dual-mass flywheel can transmit. Specifically, the torque limiter transmits torque through friction; when the torque fluctuates beyond a preset maximum torque, the torque limiter slips, thereby limiting the transmitted torque.

[0005] However, the torque limiter itself has a relatively complex structure, and integrating it into a dual-mass flywheel further increases the assembly difficulty, manufacturing costs, and component costs. Summary of the Invention

[0006] Therefore, this disclosure aims to solve the aforementioned problems existing in conventional dual-mass flywheels, and its purpose is to provide a dual-mass flywheel that integrates a torque limiter and has an improved structure that simplifies assembly steps and reduces manufacturing and component costs.

[0007] The objective is achieved by a dual-mass flywheel according to an embodiment of the present disclosure, the dual-mass flywheel comprising a primary mass assembly, a secondary mass assembly, and a spring assembly disposed between the primary and secondary mass assemblies, the primary and secondary mass assemblies rotating about a rotation axis and capable of resisting rotation of the spring assembly relative to each other. The secondary mass assembly includes a torque limiter comprising: two axially stacked support discs; and an intermediate disc axially disposed between the two support discs; wherein at least one of the two support discs has an elastic deformation region, the two support discs being fastened together such that the elastic deformation region elastically deforms, clamping the intermediate disc between the two support discs.

[0008] One objective of this disclosure is to provide a dual-mass flywheel with an integrated torque limiter, featuring an improved structure that allows for simple and cost-effective manufacturing and assembly. The torque limiter integrated in the dual-mass flywheel of this disclosure includes two support discs and an intermediate disc clamped therebetween. The torque limiter transmits torque through friction between the support discs and the intermediate disc. To generate sufficient friction, a certain axial force needs to be applied to the intermediate disc. Conventional torque limiters typically employ a dedicated axial force generating mechanism (e.g., disc springs and pressure plates) between the two support discs to generate this axial force. In the torque limiter of this disclosure, at least one of the two support discs includes an elastic deformation zone. When the two support discs are fastened together, the elastic deformation zone undergoes elastic deformation, generating an axial force that clamps the intermediate disc between the two support discs. Therefore, the torque limiter integrated in the dual-mass flywheel of this disclosure eliminates the need for a dedicated axial force generating mechanism, simplifying the torque limiter's construction and reducing component costs. Furthermore, since the assembly of a dedicated axial force generating mechanism is unnecessary, the torque limiter of this disclosure is easier to assemble, reducing its manufacturing cost.

[0009] The dual-mass flywheel according to this disclosure may also have one or more of the following features, individually or in combination.

[0010] According to one embodiment of this disclosure, the support disk includes: a fastening ring configured to fasten two support disks together; a clamping ring configured to clamp the intermediate disk, the clamping ring being spaced a certain distance from the fastening ring in the axial and / or radial directions; and a connecting portion configured to connect the clamping ring and the fastening ring, wherein the elastic deformation zone is formed by at least one of the fastening ring, the clamping ring, or the connecting portion. That is, the two support disks are fastened together at the fastening ring, and one or more of the fastening ring, the clamping ring, and the connecting portion undergo elastic deformation, clamping the intermediate disk between the two clamping rings.

[0011] According to one embodiment of this disclosure, the clamping ring and / or the fastening ring have an inclination angle formed relative to the radial direction to constitute the elastic deformation zone.

[0012] According to one embodiment of this disclosure, both the clamping ring and the fastening ring have the tilt angle, and the tilt angles of the clamping ring and the fastening ring are equal or unequal.

[0013] According to one embodiment of this disclosure, the clamping rings of both support discs have the tilt angle, and the tilt angles of the clamping rings of the two support discs are equal or unequal; and / or the fastening rings of both support discs have the tilt angle, and the tilt angles of the fastening rings of the two support discs are equal or unequal.

[0014] According to one embodiment of this disclosure, when the two support discs are fastened together, the clamping ring and / or the fastening ring undergoes elastic deformation, thereby reducing the tilt angle. Preferably, the tilt angle can be reduced to zero. That is, when the two support discs are fastened together, the clamping ring and / or the fastening ring extends substantially in the radial direction.

[0015] According to one embodiment of this disclosure, the torque limiter further includes a friction lining disposed on at least one of the axial sides adjacent to the intermediate disk. The friction lining can increase the coefficient of friction, thereby increasing the frictional force between the support disk and the intermediate disk.

[0016] According to one embodiment of this disclosure, the friction lining is a dry friction lining. Dry friction linings have a stable coefficient of friction, reduce fluctuations in frictional force in the torque limiter, have a long service life, and are relatively inexpensive.

[0017] According to one embodiment of this disclosure, the friction lining is riveted to the intermediate disk, or the friction lining is circumferentially locked to a support disk located on the same axial side of the intermediate disk as the friction lining.

[0018] According to one embodiment of this disclosure, the fastening ring is located radially outside the clamping ring and the intermediate disk, and the fastening ring of at least one support disk has a radially outwardly extending extension, the end of the spring assembly contacts the extension and transmits torque, such that the support disk constitutes at least a part of the drive assembly of the torque limiter, and the intermediate disk constitutes at least a part of the output assembly of the torque limiter.

[0019] According to one embodiment of this disclosure, the end of the spring assembly contacts the extension approximately at its axial midpoint. This arrangement helps to enhance the stability of torque transmission from the spring assembly to the support plate.

[0020] According to one embodiment of this disclosure, two support discs are fastened together by riveting at the fastening rings, wherein the torque limiter further includes a sealing gasket clamped between the fastening rings. The sealing gasket increases the sealing performance of the fastened support discs, helping to reduce or prevent contact between the lubricating oil at the spring assembly of the dual-mass flywheel and the dry friction plates.

[0021] According to one embodiment of this disclosure, the two support discs are fastened together by welding at the fastening ring.

[0022] According to one embodiment of this disclosure, the primary mass assembly includes a primary flywheel and a cover plate fastened to the primary flywheel. The torque limiter is arranged axially between the primary flywheel and the cover plate. The dual-mass flywheel further includes a first friction ring disposed between the cover plate and a support disc near the cover plate, and the first friction ring is centered with the cover plate or the support disc. During relative rotation between the primary and secondary mass assemblies of the dual-mass flywheel, friction occurs between the first friction ring and the cover plate or support disc. This friction hysteresis hysteresis in the torque transmission of the dual-mass flywheel can adjust the dynamic response characteristics of the dual-mass flywheel and attenuate torque fluctuations.

[0023] According to one embodiment of this disclosure, the first friction ring includes a plurality of axially extending protrusions, and the cover plate includes a plurality of centering holes, with each protrusion inserted into a corresponding centering hole, such that the first friction ring is centered with the cover plate.

[0024] According to one embodiment of this disclosure, the protrusion is provided with an elastic buckle, which cooperates with the centering hole, so that the first friction ring is pre-assembled on the cover plate.

[0025] According to one embodiment of this disclosure, the dual-mass flywheel further includes an elastic element disposed between the first friction ring and the cover plate, the elastic element biasing the first friction ring axially toward the support plate.

[0026] According to one embodiment of this disclosure, the dual-mass flywheel further includes a second friction ring disposed between the primary flywheel and a support disc adjacent to the primary flywheel, the second friction ring being centered with respect to the primary flywheel or the support disc.

[0027] According to one embodiment of this disclosure, the second friction ring includes a plurality of axially extending protrusions, and the primary flywheel is provided with a centering groove. The protrusions are inserted into the centering groove, thereby centering the second friction ring with the primary flywheel.

[0028] According to one embodiment of this disclosure, the first friction ring forms a sealing contact between the cover plate and the corresponding support plate; and / or the second friction ring forms a sealing contact between the primary flywheel and the corresponding support plate.

[0029] According to one embodiment of this disclosure, the secondary mass assembly further includes an output hub for outputting torque, the output hub being configured to be fastened to the intermediate disk, and a clamping ring of at least one of the two support disks being fitted onto the output hub such that the clamping ring is centered with the output hub.

[0030] According to one embodiment of the present disclosure, the output hub includes an axially extending central connection portion, and the dual-mass flywheel further includes a pressure pad fastened to the primary flywheel, the pressure pad including a centering ring that extends axially and is fitted onto the central connection portion, such that the torque limiter is centered with the primary flywheel.

[0031] This disclosure also relates to a vehicle comprising a dual-mass flywheel as described above. Attached Figure Description

[0032] The above and other features and advantages of this disclosure will become more apparent from the following detailed description of exemplary embodiments taken in conjunction with the accompanying drawings, which are for illustrative purposes only and are not intended to limit the scope of this disclosure in any way. The following drawings are not intentionally drawn to scale with actual dimensions; their focus is on illustrating the gist of this disclosure. In the figures:

[0033] Figure 1 This is an exploded view of a dual-mass flywheel according to an embodiment of the present disclosure.

[0034] Figure 2 This is a cross-sectional view of a dual-mass flywheel.

[0035] Figure 3 This is a partial sectional view of a dual-mass flywheel.

[0036] Figure 4A and Figure 4B A schematic diagram of the torque limiter of the dual-mass flywheel before and after the support plate is tightened is shown. Detailed Implementation

[0037] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings.

[0038] Unless otherwise defined, the technical or scientific terms used herein shall have the ordinary meaning understood by one of ordinary skill in the art to which this disclosure pertains. The use of terms such as “a,” “an,” or “the” in this patent application specification and claims does not indicate a limitation of quantity, but rather indicates the presence of at least one. Terms such as “comprising” or “including” mean that the element or object preceding the word encompasses the element or object listed following the word and its equivalents, without excluding other elements or objects. Although expressions such as “first” and “second” are used to describe the various elements of this disclosure, they are only used to distinguish one component from another and are not used to define the order or importance of the respective components. Without departing from the scope of this disclosure, “first element” may be written as “second element,” and similarly, “second element” may be written as “first element.” Terms such as “upper,” “lower,” “left,” and “right” are used only to indicate relative positional relationships, which may change accordingly when the absolute position of the described object changes. The directions “axial,” “radial,” and “circumferential” are defined relative to the rotation axis X of the dual-mass flywheel. The axial direction is the direction in which the rotation axis X extends, the radial direction is the direction perpendicular to the rotation axis X, and the circumferential direction is the circumferential direction around the rotation axis X.

[0039] Figure 1 This is an exploded view of a dual-mass flywheel 100 according to an embodiment of the present disclosure. Figure 2 yes Figure 1 The cross-sectional view of the dual-mass flywheel 100 shown.

[0040] A dual-mass flywheel 100 forms part of a transmission system that transmits torque between the vehicle's engine and gearbox. The dual-mass flywheel 100 includes a primary mass assembly 100a and a secondary mass assembly 100b, both arranged and rotatable about a rotation axis X. The primary mass assembly 100a and secondary mass assembly 100b can be connected to the engine and gearbox, respectively, serving as the input and output sides of the dual-mass flywheel 100. A spring assembly 100c is arranged between the primary mass assembly 100a and the secondary mass assembly 100b, and may include, for example, two sets of arc-shaped helical compression springs. The primary mass assembly 100a and secondary mass assembly 100b are resistant to relative rotation of the spring assembly 100c. Relative rotation between the primary mass assembly 100a and secondary mass assembly 100b can occur when torque fluctuations occur in the vehicle's engine. The spring assembly 100c can absorb and mitigate these torque fluctuations through compression and elongation.

[0041] refer to Figure 2The primary mass assembly 100a includes a primary flywheel 101 and a cover plate 102, and the secondary mass assembly 100b is arranged axially between the primary flywheel 101 and the cover plate 102. A spring assembly 100c may be at least partially accommodated in a receiving groove formed on the primary flywheel 101. The cover plate 102 is fastened to the primary flywheel 101 to maintain the assembled configuration of the dual-mass flywheel 100. Exemplarily, the cover plate 102 may be fastened to the primary flywheel 101 by welding.

[0042] Continue to refer to Figure 1 and Figure 2 The secondary mass component 100b includes a torque limiter 10. Specifically, in Figure 1 In the illustrated embodiment, the secondary mass component 100b is entirely comprised of a torque limiter 10. The torque limiter 10 has a predetermined maximum torque, and even when the torque generated by the engine exceeds this maximum torque, the torque output by the torque limiter 10 to downstream components (e.g., gearboxes) will not exceed this maximum torque.

[0043] like Figure 2 As shown, the torque limiter 10 includes two axially stacked support disks 20 and an intermediate disk 30 axially arranged between the two support disks 20. At least one of the support disks 20 has an elastic deformation region d. When the two support disks 20 are fastened together, the elastic deformation region d undergoes elastic deformation, clamping the intermediate disk 30 between the two support disks 20. That is, the elastic deformation of the elastic deformation region d causes the support disk 20 to generate an axial force biasing the intermediate disk 30. This axial force can enhance the friction generated between the support disks 20 and the intermediate disk 30, enabling the transmission of a certain torque between them through friction.

[0044] refer to Figure 3 Each support disc 20 includes a fastening ring 21, a clamping ring 22, and a connecting portion 23. Two support discs 20 are fastened together at the fastening ring 21, for example, by riveting or welding them together at the fastening ring 21. The clamping ring 22 is spaced a distance from the fastening ring 21 in the axial and / or radial directions and is configured to clamp the intermediate disc 30. The connecting portion 23 is configured to connect the clamping ring 22 and the fastening ring 21.

[0045] Figure 4A and Figure 4B A schematic diagram is shown before and after the two support discs 20 are tightened to better illustrate the elastic deformation zone d. Figure 4A and Figure 4B In the embodiment shown, the elastic deformation zone d of the support disk 20 is formed by the fastening ring 21 and the clamping ring 22.

[0046] Before assembling and forming the torque limiter 10, such as Figure 4AAs shown, the fastening ring 21 and the clamping ring 22 have an inclination angle α relative to the radial direction. That is, in the cross-sectional view, the extending directions of the fastening ring 21 and the clamping ring 22 are not entirely radial, but have a certain axial component. Thus, the fastening ring 21 and the clamping ring 22 have a structure similar to that of a disc spring.

[0047] When assembling the torque limiter 10, such as Figure 4B As shown, the fastening rings 21 of the two support discs 20 are fastened together, and their clamping rings 22 are also pressed against each other. The fastening rings 21 and clamping rings 22 in the formed elastic deformation zone d undergo elastic deformation, and their relative radial inclination angle α decreases. The elastic force generated by this elastic deformation in the elastic deformation zone d constitutes the axial force applied by the clamping rings 22 to the intermediate disc 30. Furthermore, this decrease in inclination angle α also helps to increase the contact area between the clamping rings 22 and the intermediate disc 30, thereby increasing the stability of the frictional action between them and extending the service life of the torque limiter 10. Figure 4B In the preferred embodiment shown, in the assembly configuration of the torque limiter 10, the fastening ring 21 and the clamping ring 22 extend approximately in the radial direction. That is, their tilt angle α is reduced to approximately zero. The clamping ring 22 is able to press its entire plane against the intermediate disk 30, thereby maximizing the contact area between them.

[0048] exist Figure 4A and Figure 4B In the illustrated embodiment, the fastening rings 21 and clamping rings 22 of both support discs 20 have an inclination angle α. In other embodiments not shown in the figures, only one support disc 20 may have a fastening ring 21 and / or clamping ring 22 with an inclination angle α; only both support discs 20 may have clamping rings 22 with an inclination angle α; or only both support discs 20 may have fastening rings 21 with an inclination angle α. The inclination angles α of the fastening rings 21 and clamping rings 22 of the same support disc 20 may be equal or unequal, and the inclination angles α of the fastening rings 21 and / or clamping rings 22 of different support discs 20 may be equal or unequal. Adjusting the size of the inclination angle α adjusts the maximum torque of the torque limiter 10.

[0049] Another conceivable technical solution is that the elastic deformation zone d of the support disk 20 is formed by the connecting portion 23 that connects the fastening ring 21 and the clamping ring 22. That is, when the torque limiter 10 is assembled, the connecting portion 23 undergoes elastic deformation, generating an axial force applied to the intermediate disk 30 by the clamping ring 22.

[0050] Further reference Figures 2-4BThe fastening ring 21 of the support plate 20 is located radially outside the clamping ring 22 and the intermediate plate 30, and the fastening ring 21 of one support plate 20 (specifically the support plate 20 on the axially lower side) has a radially outwardly extending extension 24. This extension 24 extends to contact the end of the spring assembly 100c.

[0051] Thus, the spring assembly 100c acts on the extension 24, causing the torque limiter 10 to receive the torque of the primary mass assembly 100a of the dual-mass flywheel 100 via the support disk 20. The support disk 20 constitutes at least a part of the drive assembly of the torque limiter 10. The support disk 20 further drives the intermediate disk 30 through friction, causing the intermediate disk 30 to constitute at least a part of the output assembly of the torque limiter 10.

[0052] exist Figures 1-2 In the illustrated embodiment, the intermediate disk 30 is riveted to the output hub 60 of the dual-mass flywheel 100, which includes a central connection portion 61 (e.g., a spline portion) that can be further connected to the output shaft of a downstream component (e.g., a gearbox) to output torque to the downstream component.

[0053] Preferably, the extension 24 extends generally in the radial direction, and the end of the spring assembly 100c contacts the extension 24 approximately at its axial midpoint. This helps ensure the stability of torque transmission between the spring assembly 100c and the support plate 40. It should be noted that providing elastic deformation zones d formed by inclined fastening rings 21 and / or clamping rings 22 on both support plates 20 (rather than, for example, providing elastic deformation zones only on the axially upper support plate 20) advantageously ensures that the extension direction of the extension 24 is generally in the radial direction.

[0054] Continue to refer to Figures 2-4B Friction linings 40 are arranged adjacent to the intermediate disk 30 on both axial sides. The friction linings 40 are riveted to the intermediate disk 30, so they rotate together with the intermediate disk 30 and generate friction between them and the support disk 20. The friction linings 40 enhance and stabilize the friction between the support disk 20 and the intermediate disk 30.

[0055] In other embodiments not shown in the accompanying drawings, friction linings 40 may be arranged only on one side of the axial sides of the intermediate disk 30, or the friction linings 40 may be circumferentially locked to a support disk 20 located on the same axial side of the intermediate disk 30 opposite to the friction linings 40 (e.g., by means of locking pins and locking grooves that cooperate with each other). Another conceivable technical solution is to not provide friction linings at all, but to transmit torque through direct friction between the support disk 20 and the intermediate disk 30. The surfaces of both can be treated to some extent. For example, regardless of whether friction linings are provided, the surface of the support disk 20 can be subjected to shot peening and phosphating to enhance and stabilize the friction between the support disk 20 and the intermediate disk 30 or the friction linings 40.

[0056] In a preferred embodiment according to this disclosure, the friction lining 40 of the torque limiter 10 is a dry friction lining. Compared to wet friction linings, dry friction linings, which meet the performance (e.g., strength and stability of frictional action) and lifespan requirements of the torque limiter 10, are less expensive, thus reducing the component costs of the dual-mass flywheel 100.

[0057] Another difference between dry and wet friction linings is that the performance of dry friction linings deteriorates significantly after contact with lubricating oil. Therefore, it is necessary to isolate the friction lining 40 of the torque limiter 10 from the lubricating oil disposed inside the dual-mass flywheel 100, such as the lubricating oil disposed at the location of the spring assembly 100c, for example, to lubricate the spring assembly 100c during compression and extension.

[0058] Therefore, such as Figures 3-4B As shown, the torque limiter 10 also includes a sealing gasket 50 clamped between the fastening rings 21 of the support disc 20. When the two support discs 20 are fastened by riveting, the sealing gasket 50 increases the seal between the two fastening rings 21, enhancing its isolation effect against lubricating oil. The support discs 20, fastened by welding, provide sufficient sealing, eliminating the need for a dedicated seal.

[0059] As described above, the torque limiter 10 is arranged in the axial direction between the primary flywheel 101 and the cover plate 102, and its axial position is supported by the first friction ring 103 and the second friction ring 107.

[0060] like Figure 3 As shown, the first friction ring 103 is arranged between the cover plate 102 and a support plate 20 near the cover plate 102. The second friction ring 107 is arranged between the primary flywheel 101 and the support plate 20 near the primary flywheel 101. Thus, the first friction ring 103 and the second friction ring 107 respectively support the torque limiter 10 on both axial sides.

[0061] The dual-mass flywheel 100 also includes an elastic element 110 arranged between the first friction ring 103 and the cover plate 102, which axially biases the first friction ring 103 toward the support plate 20. This biasing force is then transmitted by the torque limiter 10 to the second friction ring 107, biasing the second friction ring 107 toward the primary flywheel 101. Exemplarily, this elastic element 110 is formed of a disc spring.

[0062] With the aid of the elastic element 110, the first friction ring 103 and the second friction ring 107 are pressed tightly against the torque limiter 10 with a certain axial force. Preferably, the first friction ring 103 forms a sealing contact between the cover plate 102 and the corresponding support plate 20, and / or the second friction ring 107 forms a sealing contact between the primary flywheel 101 and the corresponding support plate 20. In particular, when both the first friction ring 103 and the second friction ring 107 form a sealing contact, and the fastening rings 21 of the two support plates 20 are fastened together with a reliable sealing effect, the friction lining 40 of the torque limiter 10 will be completely isolated from the radially outer portion of the dual-mass flywheel 100 (e.g., the spring assembly 100c), completely avoiding the decrease in frictional performance caused by contact with lubricating oil.

[0063] The first friction ring 103 includes a plurality of axially extending protrusions 104, and the cover plate 102 includes a plurality of centering holes 106. Each protrusion 104 is inserted into a corresponding centering hole 106, thereby centering the first friction ring 103 with the cover plate 102. In particular, the protrusions 104 are also provided with elastic snaps 105, which can engage with the centering holes 106, so that the first friction ring 103 is pre-assembled on the cover plate 102. This pre-assembly reduces the assembly difficulty of the dual-mass flywheel 100.

[0064] Furthermore, the cooperation between the protrusion 104 and the centering hole 106 allows the first friction ring 103 to be approximately locked to the cover plate 102 in the circumferential direction. That is, the first friction ring 103 rotates synchronously with the cover plate 102. Therefore, when the secondary mass assembly 100b (i.e., torque limiter 10) of the dual-mass flywheel 100 rotates relative to the primary mass assembly 100a, the first friction ring 103 will rotate relative to the support disk 20, resulting in friction between them. This friction hysteresis lags the torque transmission of the dual-mass flywheel 100, adjusting the dynamic response characteristics of the dual-mass flywheel 100 and attenuating torque fluctuations. In other words, the first friction ring 103 acts as a torque transmission hysteresis element.

[0065] Similarly, the second friction ring 107 can rub against the primary flywheel 101 and / or the support disc 20, delaying torque transmission of the dual-mass flywheel 100 and attenuating torque fluctuations. In other words, the second friction ring 107 acts as a torque transmission delaying element.

[0066] exist Figures 2-4B In the illustrated embodiment, the support plate 20 located on the axially lower side has a relatively large thickness and includes an extension 24, while the support plate 20 located on the axially upper side has a relatively small thickness and does not include an extension 24. Alternatively, the two support plates 20 of the torque limiter 10 may also have identical constructions, for example, they may both have the same thickness, and the extension 24 may be provided on both support plates 20.

[0067] In the dual-mass flywheel 100 according to this disclosure, the support plate 20 of the torque limiter 10 has multiple functions, including holding, supporting, rotating drive, and pressing (i.e., axially pressing the intermediate plate 30). By employing the aforementioned support plate 20, the torque limiter 10 according to this disclosure can eliminate the need for dedicated disc springs and pressure plates, thereby reducing component costs and assembly steps.

[0068] In addition to serving as a torque output hub, the output hub 60 of the dual-mass flywheel 100 also functions as a centering hub for the support disc 20 and the entire torque limiter 10.

[0069] like Figure 2 and Figure 3 As shown, a clamping ring 22 of a support disc 20 is fitted onto the output hub 60, with the inner diameter of the clamping ring 22 matching the outer diameter of the output hub 60. For example, the inner diameter of the clamping ring 22 is approximately equal to or slightly larger than the outer diameter of the output hub 60. This centers the clamping ring 22 and the output hub 60, and correspondingly, the support disc 20 and the output hub 60. This further centers the torque limiter 10 and the output hub 60.

[0070] Further reference Figure 2 and Figure 3 The dual-mass flywheel 100 also includes a pressure washer 111 fastened to the primary flywheel 101, the pressure washer 111 including an axially extending centering ring 112. A central connecting portion 61 of the output hub 60 extends axially. The centering ring 112 is fitted onto the central connecting portion 61, and the inner diameter of the centering ring 112 matches the outer diameter of the central connecting portion 61. For example, the inner diameter of the centering ring 112 is approximately equal to or slightly larger than the outer diameter of the central connecting portion 61. Thus, the output hub 60 is centered with the primary flywheel 101 by means of the pressure washer 111. Furthermore, the torque limiter 10 is integrally centered with the primary flywheel 101 by being centered with the output hub 60.

[0071] According to another aspect of this disclosure, a vehicle is proposed that includes a dual-mass flywheel 100 as described above.

[0072] Certain features, structures, or characteristics in one or more embodiments of this disclosure may be appropriately combined.

[0073] The foregoing description is illustrative of the present disclosure and should not be construed as limiting it. While several exemplary embodiments of the present disclosure have been described, those skilled in the art will readily understand 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 foregoing description is illustrative of the present disclosure and should not be construed as limiting it to the specific embodiments disclosed, and modifications to the disclosed embodiments and other embodiments are intended to be included within the scope of this disclosure.

Claims

1. A dual-mass flywheel (100) comprising a primary mass assembly (100a), a secondary mass assembly (100b), and a spring assembly (100c) disposed between the primary mass assembly (100a) and the secondary mass assembly (100b), the primary mass assembly (100a) and the secondary mass assembly (100b) rotating about a rotation axis (X) and capable of resisting rotation of the spring assembly (100c) relative to each other, characterized in that, The secondary mass component (100b) includes a torque limiter (10), the torque limiter (10) comprising: Two support disks (20) stacked axially; The intermediate disk (30) is axially arranged between the two support disks (20); At least one of the two support disks (20) has an elastic deformation zone (d), and the two support disks (20) are fastened together so that the elastic deformation zone (d) undergoes elastic deformation, thereby clamping the intermediate disk (30) between the two support disks (20).

2. The dual-mass flywheel (100) according to claim 1, characterized in that, The support plate (20) includes: A fastening ring (21) is configured to fasten the two support discs (20) together; A clamping ring (22) is configured to clamp the intermediate disk (30), and the clamping ring (22) and the fastening ring (21) are separated by a certain distance in the axial direction and / or radial direction; A connecting part (23) is configured to connect the clamping ring (22) and the fastening ring (21). The elastic deformation zone (d) is formed by at least one of the fastening ring (21), the clamping ring (22), or the connecting part (23).

3. The dual-mass flywheel (100) according to claim 2, characterized in that, The clamping ring (22) and / or the fastening ring (21) have an inclination angle (α) formed relative to the radial direction to form the elastic deformation zone (d).

4. The dual-mass flywheel (100) according to claim 3, characterized in that, Both the clamping ring (22) and the fastening ring (21) have the tilt angle (α), and the tilt angle (α) of the clamping ring (22) and the fastening ring (21) may be equal or unequal.

5. The dual-mass flywheel (100) according to claim 3, characterized in that, The clamping rings (22) of both support discs (20) have the stated tilt angle (α), and the tilt angles (α) of the clamping rings (22) of the two support discs (20) are equal or unequal; and / or The fastening rings (21) of both support discs (20) have the tilt angle (α), and the tilt angle (α) of the fastening rings (21) of the two support discs (20) may be equal or unequal.

6. The dual-mass flywheel (100) according to any one of claims 3 to 5, characterized in that, When the two support discs (20) are fastened together, the clamping ring (22) and / or the fastening ring (21) undergo elastic deformation, causing the tilt angle (α) to decrease.

7. The dual-mass flywheel (100) according to any one of claims 1 to 6, characterized in that... The torque limiter (10) also includes a friction lining (40) arranged on at least one of the axial sides adjacent to the intermediate disk (30).

8. The dual-mass flywheel (100) according to claim 7, characterized in that, The friction lining (40) is a dry friction lining (40).

9. The dual-mass flywheel (100) according to claim 7, characterized in that, The friction pad (40) is riveted to the intermediate disk (30), or The friction pad (40) is circumferentially locked to a support plate (20) located on the same axial side as the intermediate plate (30) opposite to the friction pad (40).

10. The dual-mass flywheel (100) according to any one of claims 2 to 5, characterized in that, The fastening ring (21) is located radially outside the clamping ring (22) and the intermediate disk (30), and the fastening ring (21) of at least one support disk (20) has a radially outwardly extending extension (24), the end of the spring assembly (100c) contacts the extension (24) and transmits torque, such that the support disk (20) constitutes at least a part of the drive assembly of the torque limiter (10), and The intermediate disk (30) constitutes at least a portion of the output assembly of the torque limiter (10).

11. The dual-mass flywheel (100) according to claim 10, characterized in that, The end of the spring assembly (100c) contacts the extension (24) at approximately its axial midpoint.

12. The dual-mass flywheel (100) according to any one of claims 2 to 5, characterized in that, The two support discs (20) are fastened together by riveting at the fastening ring (21), wherein the torque limiter (10) also includes a sealing gasket (50) clamped between the fastening rings (21).

13. The dual-mass flywheel (100) according to any one of claims 2 to 5, characterized in that, The two support discs (20) are fastened together by welding at the fastening ring (21).

14. The dual-mass flywheel (100) according to any one of claims 1 to 5, characterized in that, The primary mass assembly (100a) includes a primary flywheel (101) and a cover plate (102) fastened to the primary flywheel (101), and the torque limiter (10) is arranged axially between the primary flywheel (101) and the cover plate (102). The dual-mass flywheel (100) further includes a first friction ring (103) disposed between the cover plate (102) and a support disk (20) near the cover plate (102), and the first friction ring (103) is centered with the cover plate (102) or the support disk (20).

15. The dual-mass flywheel (100) according to claim 14, characterized in that, The first friction ring (103) includes a plurality of axially extending protrusions (104), and the cover plate (102) includes a plurality of centering holes (106). Each of the protrusions (104) is inserted into a corresponding centering hole (106), so that the first friction ring (103) and the cover plate (102) are centered.

16. The dual-mass flywheel (100) according to claim 15, characterized in that, The protrusion (104) is provided with an elastic buckle (105), which cooperates with the centering hole (106) so that the first friction ring (103) is pre-assembled on the cover plate (102).

17. The dual-mass flywheel (100) according to claim 14, characterized in that, The dual-mass flywheel (100) also includes an elastic element (110) disposed between the first friction ring (103) and the cover plate (102), the elastic element (110) biasing the first friction ring (103) axially toward the support plate (20).

18. The dual-mass flywheel (100) according to claim 14, characterized in that, The dual-mass flywheel (100) further includes a second friction ring (107) disposed between the primary flywheel (101) and a support disk (20) near the primary flywheel (101), the second friction ring (107) being centered with the primary flywheel (101) or the support disk (20).

19. The dual-mass flywheel (100) according to claim 18, characterized in that, The second friction ring (107) includes a plurality of axially extending protrusions (108), and the primary flywheel (101) is provided with a centering groove (109). The protrusions (108) are inserted into the centering groove (109) so that the second friction ring (107) is centered with the primary flywheel (101).

20. The dual-mass flywheel (100) according to claim 18 or 19, characterized in that, The first friction ring (103) forms a sealing contact between the cover plate (102) and the corresponding support plate (20); and / or The second friction ring (107) forms a sealed contact between the primary flywheel (101) and the corresponding support plate (20).

21. The dual-mass flywheel (100) according to any one of claims 2 to 5, characterized in that, The secondary mass assembly (100b) also includes an output hub (60) for outputting torque, the output hub (60) being configured to be fastened to the intermediate disk (30). In this configuration, the clamping ring (22) of at least one of the two support discs (20) is fitted onto the output hub (60), thereby aligning the clamping ring (22) with the output hub (60).

22. The dual-mass flywheel (100) according to claim 21, characterized in that, The output hub (60) includes an axially extending central connecting portion (61). The dual-mass flywheel (100) also includes a pressure pad (111) fastened to the primary flywheel (101), the pressure pad (111) including a centering ring (112) extending axially and fitted onto the central connection (61) so that the torque limiter (10) is centered with the primary flywheel (101).

23. A vehicle comprising a dual-mass flywheel (100) according to any one of claims 1 to 22.

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