Torsion damper, hydraulic torque converter and dual mass flywheel

Abstract

The invention relates to a torsion damper, a hydraulic torque converter and a dual mass flywheel. The torsion damper includes: a flange; the retainer is coaxially aligned with the flange and can rotate around the axis relative to the flange from an initial position to a first relative position and a second relative position; at least one outer spring mounted on the holder; and at least one inner spring mounted on the flange and located radially inward of the outer spring, the torsion damper being configured such that the outer spring is compressed and the inner spring is not compressed during rotation of the retainer from an initial position to a first relative position relative to the flange, and the inner spring is not compressed during rotation of the retainer from an initial position to a second relative position relative to the flange. The outer spring and the inner spring are compressed in the process that the retainer rotates from the first relative position to the second relative position relative to the flange. According to the torsion damper, the hydraulic torque converter and the dual-mass flywheel, the mass and the size of the inner spring are small, and therefore the cost is low.

Description

Technical Field

[0001] The invention relates to a torsional vibration damper, a hydraulic torque converter and a dual-mass flywheel. Background Art

[0002] When transmitting torque, a torque converter in a vehicle requires a torsional vibration damper to enhance NVH (Noise, Vibration, Harshness) performance, thereby improving passenger comfort. The spring stiffness and damping capacity of the torsional vibration damper are key parameters. Depending on the spring stiffness, there are primary and secondary spring stiffnesses. Different spring stiffnesses and damping capacities can be achieved by adjusting the drive mechanism, the geometry of the torsional vibration damper spring, the geometry of the spring seat, the number of springs, and the spring assembly type (single spring, tandem spring, nested spring).

[0003] In order to realize the two-stage spring rate, the torsional vibration damper generally requires a long spring with a relatively low spring rate and a short spring with a relatively high spring rate.

[0004] Figure 1 A perspective view showing an assembly of a long spring and a short spring of a torsional vibration damper of the prior art is shown. Figure 2 Shown including Figure 1 Cross-sectional view of a torsional vibration damper with a long spring and a short spring, Figure 3 Show Figure 2 Schematic diagram of the flange of the torsional vibration damper, and Figure 4 Show Figure 2 Schematic diagram of the holder of the torsional vibration damper, and Figure 5 Show Figure 2 Damping curve of the torsional vibration damper. Figure 6 FIG. 2 shows a cross-sectional view of another prior art torsional vibration damper. Figures 1 to 5 As shown, the torsional vibration damper includes a flange 1', a retaining member 2', a long spring 3' and a short spring 4'. The long spring 3' and the short spring 4' are assembled in the same receiving portion. Figure 6 As shown, the long spring 3 ′ and the short spring 4 ′ are located in different receptacles.

[0005] In these two prior arts, when the torsional vibration damper is working, in the first stage, both the long spring 3' and the short spring 4' are compressed until the long spring 3' is crushed to death. In this article, the term "crushed to death" means that the spring is compressed to the extent that it can no longer be elastically deformed further. In the second stage, the short spring 4' is further compressed, and the long spring 3' is always crushed to death. Under actual working conditions, the second stage is not often used. In addition, the second stage is shorter, usually 1 to 3 degrees, while the first stage is about 15 to 30 degrees, which is 10 to 20 times that of the second stage. The short spring 4' is a key component of the secondary spring stiffness. For Figures 1 to 5 In the prior art shown, the short spring 4' takes up a large space, but its function is rarely used, which compresses the design space of the long spring 3'. Moreover, for both prior arts, the bearing capacity of the short spring 4' needs to be set relatively high, resulting in relatively high volume, mass and cost.

[0006] Furthermore, in the prior art, the torsional vibration damper includes a retainer 2' for holding the spring. This retainer 2' is a stamped part, which is very expensive to manufacture. Once the geometry of the retainer 2' is fixed, the spring geometry and key parameters, such as the outer diameter and window angle, are also fixed. This fixed package makes it difficult to meet more stringent requirements. Manufacturing a new stamping die to meet these new requirements is costly and requires a long production cycle. Summary of the Invention

[0007] The object of the present invention is to provide a torsional vibration damper with a relatively small mass and volume of the inner spring.

[0008] According to one aspect of the present invention, there is provided a torsional vibration damper, comprising:

[0009] flange;

[0010] a retainer coaxially aligned with the flange and rotatable about the axis relative to the flange in a first circumferential direction from an initial position to a first relative position and a second relative position;

[0011] at least one outer spring mounted on the retainer; and

[0012] At least one inner spring mounted on the flange and located radially inwardly of the outer spring, wherein

[0013] The torsional vibration damper is configured such that, during a process in which the retaining member rotates relative to the flange from an initial position to a first relative position, the outer spring is compressed and the inner spring is not compressed; and during a process in which the retaining member rotates relative to the flange from the first relative position to a second relative position, both the outer spring and the inner spring are compressed.

[0014] According to an embodiment of the present invention, the retaining member comprises at least two outer protrusions spaced apart along the circumferential direction, the outer spring is located between two adjacent outer protrusions, and the flange comprises at least one stop portion.

[0015] In the initial position, the two ends of the outer spring respectively abut against two adjacent outer protrusions.

[0016] During the process of the retaining member rotating from the initial position to the second relative position relative to the flange, one end of the outer spring abuts against one of the two adjacent outer protrusions, and the other end of the outer spring abuts against the stopper.

[0017] According to an embodiment of the present invention, the flange includes at least one receiving portion, and at least one inner spring is received in the at least one receiving portion in a one-to-one correspondence.

[0018] The retaining member includes at least one inner protrusion. When the retaining member rotates from a first relative position to a second relative position relative to the flange, one end of the inner spring abuts against the inner protrusion, and the other end of the inner spring abuts against the inner side wall of the accommodating portion.

[0019] According to an embodiment of the present invention, each accommodation portion has a limiting portion that restricts the inner spring from being displaced in a first axial direction directed from the flange to the retaining member.

[0020] According to an embodiment of the present invention, the limiting portion includes two protrusions, which extend from the radial inner wall and the radial outer wall of the accommodating portion respectively, and there is an avoidance gap between the two protrusions extending along the movement path of the inner convex portion.

[0021] According to an embodiment of the invention, the two tabs are inclined with respect to the axial direction.

[0022] According to an embodiment of the present invention, the retaining member is rotatable relative to the flange from an initial position to a third relative position along a second circumferential direction opposite to the first circumferential direction, and

[0023] The torsional vibration damper is configured such that, during the rotation from the initial position to the third relative position, the outer spring is compressed and the inner spring is uncompressed.

[0024] According to an embodiment of the present invention, the spring rate of the outer spring is smaller than the spring rate of the inner spring.

[0025] Another aspect of the present invention provides a hydraulic torque converter comprising:

[0026] The torsional vibration damper according to the above embodiment includes a retainer and a flange;

[0027] a piston fixedly connected coaxially with the retaining member;

[0028] The turbine is fixedly connected coaxially with the flange.

[0029] Yet another aspect of the present invention provides a dual mass flywheel comprising the torsional vibration damper according to the above embodiment.

[0030] In the prior art, the inner spring is compressed in both stages. In the torsional vibration damper according to an embodiment of the present invention, the inner spring is compressed only during the transition from the first relative position to the second relative position (i.e., the second stage). Therefore, compared to the prior art, the inner spring of the torsional vibration damper of the present invention requires less compressive force to achieve the same damping curve. Consequently, the mass and volume of the inner spring are relatively small, resulting in lower costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 A perspective view showing the assembly of a long spring and a short spring of a torsional vibration damper in the prior art is shown.

[0032] Figure 2 Shown including Figure 1 Cross-sectional view of a torsional vibration damper with a long spring and a short spring.

[0033] Figure 3 Show Figure 2 Schematic diagram of the flange of the torsional vibration damper.

[0034] Figure 4 Show Figure 2 Schematic diagram of the retaining element of the torsional vibration damper.

[0035] Figure 5 Show Figure 2 Damping curve of the torsional vibration damper.

[0036] Figure 6 A cross-sectional view of another prior art torsional vibration damper is shown.

[0037] Figure 7 A cross-sectional view illustrating a torque converter according to an embodiment of the present invention.

[0038] Figure 8A A schematic diagram showing a torsional vibration damper in an initial position according to an embodiment of the present invention is shown. Figure 8B A schematic diagram shows a torsional vibration damper according to an embodiment of the present invention in a first relative position.

[0039] Figure 9A is a simplified schematic diagram of a torsional vibration damper in the first stage according to an embodiment of the present invention, Figure 9B FIG. 4 is a simplified schematic diagram of a torsional vibration damper according to an embodiment of the present invention in the second stage.

[0040] Figure 10 A target force / compressed length curve according to one example is shown.

[0041] Figure 11 A schematic diagram of a flange of a torsional vibration damper according to an embodiment of the present invention is shown.

[0042] Figure 12 A schematic diagram shows a holder of a torsional vibration damper according to an embodiment of the present invention.

[0043] Figure 13 A schematic diagram illustrating the assembly of a turbine and a flange according to an embodiment of the present invention is shown. DETAILED DESCRIPTION

[0044] The following detailed description and accompanying drawings are used to illustrate the principles of the present invention. The present invention is not limited to the preferred embodiments described. The scope of protection of the present invention is defined by the claims.

[0045] Unless otherwise specified, the terms “axial”, “radial” and “circumferential” herein refer to the axial, radial and circumferential directions of the torsional vibration damper, respectively.

[0046] Figure 7 A cross-sectional view showing a torque converter according to an embodiment of the present invention, Figure 8A A schematic diagram showing a torsional vibration damper according to an embodiment of the present invention at an initial position is shown, and Figure 8B A schematic diagram shows a torsional vibration damper according to an embodiment of the present invention in a first relative position.

[0047] like Figures 7 to 8B As shown, the torsional vibration damper includes a flange 1, a retaining member 2, at least one outer spring 3 and at least one inner spring 4. The retaining member 2 is coaxially aligned with the flange 1 and can rotate from an initial position to a first relative position and a second relative position around the axis in a first circumferential direction relative to the flange 1. The outer spring 3 is mounted on the retaining member 2, and the inner spring 4 is mounted on the flange 1 and is located radially inward of the outer spring 3. The torsional vibration damper is constructed so that during the process of the retaining member 2 rotating from the initial position to the first relative position relative to the flange 1 (hereinafter referred to as the first stage), the outer spring 3 is always compressed and the inner spring 4 is not compressed. During the process of the retaining member 2 rotating from the first relative position to the second relative position relative to the flange 1 (hereinafter referred to as the second stage), both the outer spring 3 and the inner spring 4 are compressed. The description of the rotation process in this article does not include the starting position and the ending position of the process, but only includes the position between the starting position and the ending position.

[0048] Figure 9A is a simplified schematic diagram of a torsional vibration damper in the first stage according to an embodiment of the present invention, Figure 9B FIG is a simplified schematic diagram of a torsional vibration damper according to an embodiment of the present invention in the second stage. Figure 9A As shown, only the outer spring 3 is compressed, and the inner spring 4 is not compressed. Figure 9B As shown, both the outer spring 3 and the inner spring 4 are compressed.

[0049] Next, the torsional vibration damper according to the embodiment of the present invention will be compared with a torsional vibration damper according to a comparative example of the prior art. Figure 10The target force / compression length curve according to an example is shown. According to the torsional vibration damper of the embodiment of the present invention, in the range of target force from 0 to 100N, the compression force is provided entirely by the outer spring 3. In the range of target force from 100 to 150N, 10N of compression force is provided by the outer spring 3 and 40N of compression force is provided by the inner spring 4. That is, in order to achieve Figure 10 In the damping curve shown, the outer spring 3 is designed to be crushed at 110N, and the inner spring 4 is designed to be crushed at at least 40N. According to a comparative example of the prior art, in the target force range of 0 to 100N, the compressive force is provided by both the outer spring 3 and the inner spring 4. When the target force reaches the turning point of 100N, the outer spring 3 is exactly crushed. In the target force range of 100N to 150N, the compressive force is entirely provided by the inner spring 4. In other words, the inner spring 4 is designed to be crushed at 150N. The volume and mass of the inner spring 4 crushed at 40N are relatively smaller than those crushed at 150N. Therefore, the torsional vibration damper of the embodiment of the present invention is lower in cost. The above description uses a force range of 0 to 150N, with a turning point of 100N. However, those skilled in the art will understand that the above damping curve is merely an example, and the present invention can also achieve the advantages of a smaller mass and volume of the inner spring 4 for other damping curves.

[0050] As can be seen from the above, compared with the prior art, in order to achieve the same damping curve, the compression force required to be provided by the inner spring 4 of the torsional vibration damper of the present invention is relatively small, so the mass and volume of the inner spring 4 are relatively small, resulting in a lower cost of the vibration damper.

[0051] For example, the spring stiffness of the outer spring 3 can be less than that of the inner spring 4. However, those skilled in the art can also select the spring stiffness of the outer and inner springs 3 and 4 based on the desired damping curve. For example, the spring stiffness of the outer spring 3 can be equal to or greater than that of the inner spring 4. The outer and inner springs 3 and 4 can each be a coil spring, which is formed by spirally winding spring wire. The cross-section of the spring wire forming the outer and inner springs 3 and 4 can be circular or oval. Circular spring wire is less expensive than oval spring wire, thus reducing spring costs. If the spring stiffness requirement is higher, oval spring wire can be used for the outer and inner springs 3 and 4 to achieve a lower primary spring stiffness. The outer and inner springs 3 and 4 can be arc-shaped, meaning their central axes extend along a predetermined arc. In another example, the inner spring 4 can be linear, meaning its central axis extends along a predetermined straight line, thereby reducing costs. For example, the arc length of the outer spring 3 can be greater than that of the inner spring 4. For example, the outer spring 3 and the inner spring 4 may be made of metal.

[0052] The number of outer springs 3 and inner springs 4 can each be multiple, for example, three. However, the number of each is not limited to this and can be selected as needed. In the case of multiple inner springs 4, the multiple inner springs 4 are evenly spaced along the circumference, and each inner spring 4 has the same structure. In the case of multiple outer springs 3, the multiple outer springs 3 are evenly spaced along the circumference, and each outer spring 3 has the same structure. For example, the outer diameter of the inner spring 4 can be 6 mm. However, it should be understood that the size of the inner spring 4 and outer spring 3 can be selected as needed. The number of inner springs 4 and outer springs 3 can be the same or different, and can be selected as needed.

[0053] The retainer 2 includes at least two circumferentially spaced protrusions 21. The outer spring 3 is positioned between two adjacent protrusions 21. The flange 1 includes at least one stop 13. In the initial position, the ends of the outer spring 3 respectively abut against the two adjacent protrusions 21. During rotation of the retainer 2 relative to the flange 1 from the initial position to the second relative position, one end of the outer spring 3 abuts against one of the two adjacent protrusions 21, and the other end of the outer spring 3 abuts against the stop 13. The at least two protrusions 21 are evenly spaced along the circumference. For example, there are three protrusions 21. The number of stops 13 is the same as the number of outer springs 3.

[0054] Figure 11 FIG. 1 is a schematic diagram showing a flange 1 of a torsional vibration damper according to an embodiment of the present invention. Figure 11 As shown, the flange 1 further comprises a body portion 11, which is configured as a disc-shaped plate-like member. The stopper portion 13 is provided radially outside the body portion 11 and is formed as an arc-shaped protrusion extending in the circumferential direction.

[0055] Figure 12 Schematic diagram of the holder 2 of the torsional vibration damper according to an embodiment of the present invention is shown. Figure 12 As shown, the retainer 2 includes an annular portion 24. The outer protrusion 21 is provided on the annular portion 24 and can be formed by stamping and bending the annular portion 24. The outer protrusion 21 is formed as an arc-shaped protrusion extending in the circumferential direction. The circumferential length of the outer protrusion 21 is substantially the same as the circumferential length of the stopper 13.

[0056] The flange 1 further includes at least one receiving portion 11a, in which at least one inner spring 4 is received in a one-to-one correspondence. The retaining member 2 further includes at least one inner protrusion 22. During rotation of the retaining member 2 relative to the flange 1 from a first relative position to a second relative position, one end of the inner spring 4 abuts against the inner protrusion 22, while the other end of the inner spring 4 abuts against the inner sidewall of the receiving portion 11a.

[0057] In the case of a plurality of inner convex portions 22, the plurality of inner convex portions 22 are particularly evenly spaced along the circumferential direction. For example, the number of the inner convex portions 22 is three. The number of the inner convex portions 22 is the same as the number of the inner springs 4. Figure 12 The inner convex portion 22 is provided on the radially inner side of the annular portion 24 of the retainer 2 and is formed as an arc-shaped protrusion extending in the circumferential direction.

[0058] Each accommodating portion 11a further includes a limiting portion 12 that constrains the inner spring 4 from displacement in the first axial direction from the flange 1 toward the retaining member 2. In one example, the limiting portion 12 comprises two tabs extending from the radially inner and outer walls of the accommodating portion 11a, respectively. A clearance gap 11b is formed between the two tabs, extending along the movement path of the inner protrusion 22 to allow for clearance. The two tabs are inclined relative to the axial direction. In other words, the accommodating portion 11a provides wrapping, limiting, and compression functions for the inner spring 4.

[0059] Compared with the prior art, the stamping parts of the present invention can also meet the technical requirements by opening small holes. Minor modifications to existing stamping dies can also meet the technical requirements. In other words, the present invention makes relatively small changes to the stamping parts. Based on limited conditions, minor changes are made to the existing stamping dies to leave space for the inner spring, thereby improving the existing two-stage shock absorber design, which costs less than manufacturing a new stamping die. Furthermore, the assembly process of the torsional vibration damper of the present invention does not change much, so the workload of the assembly line will not change much. The torsional vibration damper according to the embodiment of the present invention can be used for current large-scale production. In addition, the installation position of the present invention is flexible and can be arranged in a small space.

[0060] The main body 1111 is also provided with an opening 11c. This opening 11c is located on the same circumference as the inner spring 4 and the inner protrusion 22 of the retainer 2, avoiding the inner protrusion 22. The opening 11c extends along an arc. If there are multiple inner springs 4, the opening 11c is preferably centrally located between two adjacent inner springs 4.

[0061] Refer again Figure 12 The annular portion 24 is provided with a flange on its radially outer side for restraining the outer spring 3 radially outwardly. The annular portion 24 is provided with at least one inscribed portion 23 configured to restrain the outer spring 3 radially inwardly. The inscribed portion 23 is centrally located between two adjacent outer protrusions 21 and is formed as an arcuate tab. The inscribed portion 23 is formed by stamping and bending the annular portion 24.

[0062] When assembling the torsional vibration damper, first, the inner spring 4 is placed in the receiving portion 11a of the retaining member 2, and the outer spring 3 is placed between two adjacent outer protrusions 21. In the initial state, the outer spring 3 has a preload and can therefore be securely installed between the two outer protrusions 21. Then, the flange 1 is snapped onto the retaining member 2 with the inner spring 4 and outer spring 3 installed.

[0063] The outer spring 3 and inner spring 4 are used to transmit torque between the retainer 2 and the flange 1. The inner spring 4 can be removed, allowing the inner protrusion 22 to rotate unimpeded during rotation of the retainer 2 relative to the flange 1 in the first circumferential direction. Therefore, the torsional vibration damper of the present invention can be applied to a wider range of situations, for example, it can be adapted to the current design, in which the inner spring is removed and the outer spring is designed as a long spring and a short spring in series.

[0064] The retainer 2 can rotate to a third relative position relative to the flange 1 in a second circumferential direction opposite to the first circumferential direction. The torsional vibration damper is configured such that during rotation from the initial position to the third relative position, the outer spring 3 is compressed and the inner spring 4 is uncompressed.

[0065] Figure 8A The figure shows the initial position of the retaining element 2 relative to the flange 1, which is defined as 0 degrees. During the rotation of the retaining element 2 relative to the flange 1 from 0 degrees to an angle θ1 in the first circumferential direction, only the outer spring 3 is compressed. There is a circumferential distance between the inner spring 4 and the inner protrusion 22, so the inner spring 4 is not compressed. This is the first stage. For example, θ1 is 33.8 degrees. During the rotation of the retaining element 2 relative to the flange 1 in the first circumferential direction beyond θ1 and further by θ2, the inner protrusion 22 contacts and gradually compresses the inner spring 4, and both the outer spring 3 and the inner spring 4 are compressed. This is the second stage. For example, θ2 is 9 degrees. The long spring is then crushed, so that neither spring can be compressed any further. These two stages correspond to the driving conditions of the torsional vibration damper.

[0066] The torsional vibration damper also has a sliding working condition, in which the retaining member 2 rotates clockwise relative to the flange 1. In the prior art, the characteristics of the torsional vibration damper are the same in the two working conditions. Figure 4 As shown, in the initial position, the inner projection 22' is circumferentially centered on the outer spring, resulting in the same spring compression length and angle. However, the torsional vibration damper according to the present invention has different spring stiffness and total capacity in driving and coasting conditions. Driving is the most common operating condition, and the position of the inner projection is modified to ensure a secondary spring stiffness and total capacity. In coasting conditions, only primary damping is present, and the total capacity is approximately a fraction of the total capacity in driving conditions, for example, 68%, which is sufficient for coasting conditions.

[0067] The torsional vibration damper according to the embodiment of the present invention can be applied to a hydraulic torque converter and a dual mass flywheel. Figure 7 According to an embodiment of the present invention, the torque converter includes a torsional vibration damper, a turbine 6 and a piston 5. The turbine 6 is coaxially fixedly connected to the flange 1 by fasteners such as rivets. The piston 5 is coaxially fixedly connected to the retaining member 2 by fasteners such as rivets. The output shaft 7 passes through the turbine 6, the flange 1, the retaining member 2 and the piston 5 in sequence. The output shaft 7 can be welded to the flange 1. The output shaft 7 can be connected to the gearbox. When the piston 5 rotates, the retaining member 2 rotates accordingly, and the compression force of the inner spring 4 and the outer spring 3 drives the flange 1 to rotate. The turbine 6 and the output shaft 7 rotate together driven by the flange 1. The output shaft 7 transmits the torque to the gearbox.

[0068] Figure 13 FIG. 1 shows a schematic diagram of the assembly of a turbine and a flange according to an embodiment of the present invention. Figure 13 As shown, the turbine 6 includes a housing 61 and blades. The housing 61 is provided with blade slots 61a to accommodate the blades. There are multiple blade slots 61a, for example three, and the multiple blade slots 61a are located on different circumferences. After the turbine 6 and flange 1 are assembled, one side of the inner spring 4 along the second axial direction contacts the housing 61. The other side of the inner spring 4 along the first axial direction is restrained by two stoppers 12, preventing the inner spring 4 from popping out. The circumference of the inner spring 4 differs from the circumference of the blade slots 61a of the turbine 6. Therefore, the inner spring 4 can contact the smooth surface of the housing 61 to prevent interference with the blade slots 61a.

[0069] As mentioned above, although the exemplary embodiments of the present invention have been described with reference to the accompanying drawings, the present invention is not limited to the above specific embodiments, and the scope of protection of the present invention should be defined by the claims and their equivalents.

[0070] Reference Signs List

[0071] 1. 1': flange; 11. Main body; 11a: accommodating portion; 11b: avoidance gap; 11c: opening; 12: limiting portion; 13: stopper; 2. 2': retaining member; 21: outer convex portion; 22. 22': inner convex portion; 23: inner connecting portion; 24: annular portion; 3: outer spring; 3': long spring; 4: inner spring; 4': short spring; 5: piston; 6: turbine; 61: housing; 61a: blade groove; 7: output shaft.

Claims

1. A torsional vibration damper comprising: flange (1); a retaining member (2) coaxially aligned with the flange (1) and rotatable relative to the flange (1) about an axis in a first circumferential direction from an initial position to a first relative position and a second relative position; at least one outer spring (3) mounted on the retaining member (2); as well as At least one inner spring (4) mounted on the flange (1) and located radially inward of the outer spring (3), wherein: The torsional vibration damper is constructed such that, during the process of the retaining member (2) rotating from the initial position to the first relative position relative to the flange (1), the outer spring (3) is compressed and the inner spring (4) is not compressed; and during the process of the retaining member (2) rotating from the first relative position to the second relative position relative to the flange (1), both the outer spring (3) and the inner spring (4) are compressed.

2. The torsional vibration damper according to claim 1, wherein: The retaining member (2) comprises at least two outer protrusions (21) spaced apart along the circumferential direction, the outer spring (3) is located between two adjacent outer protrusions (21), and the flange (1) comprises at least one stopper (13). In the initial position, the two ends of the outer spring (3) respectively abut against the two adjacent outer protrusions (21). During the process of the retaining member (2) rotating from the initial position to the second relative position relative to the flange (1), one end of the outer spring (3) abuts against one of the two adjacent outer protrusions (21), and the other end of the outer spring (3) abuts against the stopper (13).

3. The torsional vibration damper according to claim 1, wherein: The flange (1) comprises at least one accommodating portion (11a), and the at least one inner spring (4) is accommodated in the at least one accommodating portion (11a) in a one-to-one correspondence. The retaining member (2) includes at least one inner convex portion (22). When the retaining member (2) rotates from the first relative position to the second relative position relative to the flange (1), one end of the inner spring (4) abuts against the inner convex portion (22), and the other end of the inner spring (4) abuts against the inner side wall of the accommodating portion (11a).

4. The torsional vibration damper according to claim 3, wherein: Each of the accommodating portions (11a) has a limiting portion (12), and the limiting portion (12) restricts the inner spring (4) from being displaced in a first axial direction directed from the flange (1) toward the retaining member (2).

5. The torsional vibration damper according to claim 4, wherein: The limiting portion (12) includes two protrusions, which extend from the radial inner wall and the radial outer wall of the accommodating portion (11a) respectively, and there is an avoidance gap (11b) between the two protrusions extending along the movement path of the inner convex portion (22).

6. The torsional vibration damper according to claim 5, wherein: The two tabs are inclined relative to the axial direction.

7. The torsional vibration damper according to claim 1, wherein: The retaining member (2) is rotatable relative to the flange from the initial position to a third relative position along a second circumferential direction opposite to the first circumferential direction, and The torsional vibration damper is configured such that, during the rotation from the initial position to the third relative position, the outer spring (3) is compressed and the inner spring (4) is not compressed.

8. The torsional vibration damper according to any one of claims 1 to 7, wherein: The spring stiffness of the outer spring (3) is smaller than the spring stiffness of the inner spring (4).

9. A torque converter comprising: The torsional vibration damper according to any one of claims 1 to 8, comprising a retaining member (2) and a flange (1); A piston (5) fixedly connected coaxially with the retaining member (2); A turbine (6) is coaxially and fixedly connected to the flange (1).

10. A dual mass flywheel comprising a torsional vibration damper according to any one of claims 1 to 8.

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