Spring seat and damping device

Abstract

The present application relates to a spring seat and a vibration damper. In a vibration damper provided with a spring seat, a hole constituting a stop mechanism is formed longer in the circumferential direction. A spring seat (30) is provided in a vibration damper (1) having an input-side plate (21), a hub flange (22), and a plurality of coil springs (27). The spring seat (30) has an end face support portion (301) and an outer peripheral support portion (302). The end face support portion (301) has a recessed portion (301a) recessed toward the coil springs (27) in the central portion in the radial direction, supports the end faces of the coil springs (27), and is supported by a pressing surface (21c) of the input-side plate (21) and a pressing surface (22d) of the hub flange (22). The outer peripheral support portion (302) supports a portion of the radially outer side portions of the coil springs (27).

Description

Technical Field

[0001] The invention relates to a spring seat and a vibration damping device. Background Art

[0002] For example, in a hybrid vehicle including an engine and an electric motor, a vibration damper device having a torque limiting function as disclosed in Patent Document 1 is used to prevent excessive torque from being transmitted from the output side to the engine side during engine startup.

[0003] The vibration damping device disclosed in Patent Document 1 includes a vibration damping unit comprising a side plate as an input rotating body, a hub plate as an output rotating body, and multiple coil springs. A torque limiter is provided on the outer periphery of the vibration damping unit. The torque limiter and the vibration damping unit are connected by rivets. Furthermore, the torque limiter plate is fixed to the flywheel by bolts.

[0004] Here, the coil spring of the vibration damper is placed in the window portion of the side plate. Therefore, when the side plate and hub plate rotate relative to each other, the coil spring is compressed in the rotational direction between the two plates. Centrifugal force acts on the coil spring, and when the coil spring is compressed, it moves radially outward. As a result, the coil spring slides relative to the window portion, generating frictional resistance between the coil spring and the side plate. This frictional resistance reduces the vibration damper's ability to attenuate rotational fluctuations.

[0005] Therefore, spring seats are installed at both ends of the coil spring. The end face of the coil spring and a part of the radially outer side are supported by the spring seats to prevent the coil spring from sliding relative to the window portion.

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 2011-226572

[0007] In a vibration damping device, a limiter mechanism is generally provided to limit the relative rotation (torsion angle) between the input and output rotors within a predetermined angular range. The limiter mechanism comprises, for example, a limiter pin provided on the input rotor and an arc-shaped limiter hole formed in the output rotor.

[0008] In order to improve the rotational fluctuation performance of the vibration damping device, it is preferable to increase the torsion angle between the input rotating body and the output rotating body (ie, widen the angle). To achieve this wide angle, the length of the stopper hole of the output rotating body must be ensured to be long.

[0009] But, as mentioned above, under the situation that the two ends of coil spring are provided with spring seat, this spring seat and limiter are mostly configured at the position that overlaps in radial direction with hole. Therefore, if spring seat is set, then limiter can't be formed long with hole, hinder wide-angle. Summary of the Invention

[0010] The technical problem of the present invention is to enable a hole constituting a stopper mechanism to be formed long in the circumferential direction in a vibration damping device provided with a spring seat.

[0011] (1) The spring seat according to the present invention is provided in a vibration damping device to support at least one end face of at least one elastic member among a plurality of elastic members. The vibration damping device comprises a first rotating body, a second rotating body, and a plurality of elastic members. The first rotating body comprises a plurality of first accommodating portions, each of which has a first pressing surface at both end faces in the circumferential direction. The second rotating body is capable of rotating relative to the first rotating body and comprises a plurality of second accommodating portions, each of which has a second pressing surface at both end faces in the circumferential direction. The plurality of elastic members are accommodated in the first accommodating portions and the second accommodating portions, and elastically connect the first rotating body and the second rotating body in the rotational direction.

[0012] The spring seat includes an end face support portion and an outer peripheral support portion. The end face support portion includes a recessed portion in its radially central portion, which is recessed toward the elastic member. The end face support portion supports the end face of the elastic member and is supported by the first pressing surface and the second pressing surface. The outer peripheral support portion supports a portion of the radially outer portion of the elastic member.

[0013] Here, the elastic component is supported on the respective pressing surfaces of the first and second accommodating portions via a spring seat. A recess is formed in the end surface support portion of the spring seat. Therefore, a protrusion can be formed on the second pressing surface of the second accommodating portion so as to fit into the recess. Therefore, when a limiting mechanism for limiting the relative rotation of the first and second rotating bodies is formed by an arc-shaped limiting hole and a component passing through the hole, the end of the limiting hole can be formed to have a longer protrusion toward the second pressing surface. As a result, the torsion angle between the first and second rotating bodies can be widened.

[0014] (2) Preferably, the recess has a hole extending in the circumferential direction. By forming the hole in the recess, the recess can be formed deeper. As a result, the protrusion of the second pressing surface can be made more prominent, for example, the stopper hole can be further lengthened.

[0015] (3) Preferably, the first rotating body includes a first plate and a second plate that are spaced apart in the axial direction. In this case, the second rotating body is arranged between the first plate and the second plate in the axial direction.

[0016] (4) The vibration damping device according to the present invention comprises a first rotating body, a second rotating body, a plurality of elastic components, a limiting mechanism and a spring seat. The first rotating body has a plurality of first accommodating portions, each of which has a first pressing surface at both end faces in the circumferential direction. The second rotating body is capable of rotating relative to the first rotating body and has a plurality of second accommodating portions, each of which has a second pressing surface at both end faces in the circumferential direction. A plurality of elastic components are accommodated in the first accommodating portions and the second accommodating portions, and elastically connect the first rotating body and the second rotating body in the rotational direction. The limiting mechanism comprises a limiting component and a limiting hole. The limiting component is provided on the first rotating body. The limiting hole is formed in the second rotating body and extends in the circumferential direction, and the limiting component passes through the limiting hole. The spring seat supports at least one end face of at least one elastic component among the plurality of elastic components, and has a specific structure as described above.

[0017] (5) Preferably, the second rotating body has a protrusion protruding in the circumferential direction on at least one second pressing surface of the second accommodating portion, and the protrusion is embedded in the recess of the spring seat. In this case, one end portion of the limiting hole in the circumferential direction extends toward the protrusion.

[0018] Effects of the Invention

[0019] In the present invention as described above, in a vibration damper device provided with a spring seat, the stopper hole constituting the stopper mechanism can be formed long in the circumferential direction, thereby achieving excellent rotational fluctuation damping performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 4 is a cross-sectional view of a vibration damping device with a torque limiter according to one embodiment of the present invention.

[0021] Figure 2 for Figure 1 Front view of the vibration damping unit of the vibration damping device.

[0022] Figure 3 This is the main view of the flange.

[0023] Figure 4 This is a side view of the spring seat.

[0024] Figure 5 for Figure 4 VV line cross-sectional view.

[0025] Figure 6 It is a torsional characteristic line diagram.

[0026] Description of Reference Numerals

[0027] 21: Input side plate (first rotating body); 211: First plate; 212: Second plate; 21a: First window portion (first accommodating portion); 21c: Pressing surface (first pressing surface); 22: Hub flange (second rotating body); 22a: First window hole (second accommodating portion); 22c: Limiting hole; 22d: Pressing surface (second pressing surface); 22e: Protrusion; 24: Limiting pin; 25: Limiting mechanism; 27: Coil spring (elastic component); 28: Resin component (elastic component); 30: Spring seat; 301: End face support portion; 301a: Recess; 301b: Hole; 302: Peripheral support portion. DETAILED DESCRIPTION

[0028] [Overall composition]

[0029] Figure 1 1 is a cross-sectional view of a vibration damping device 1 with a torque limiter (hereinafter sometimes referred to as a "vibration damping device") according to an embodiment of the present invention. Figure 2 This is a front view of the vibration damping device 1, showing a portion of the components removed or a portion of the components deleted. Figure 1 In the figure, the OO line is the axis of rotation. Figure 1 In FIG, the engine is arranged on the left side of the vibration damping device 1, and the drive unit including the electric motor, the transmission, etc. is arranged on the right side.

[0030] It should be noted that in the following description, the axial direction is the direction in which the rotation axis O of the vibration damping device 1 extends. In addition, the circumferential direction is the circumferential direction of the circle centered on the rotation axis O, and the radial direction is the radial direction of the circle centered on the rotation axis O. It should be noted that the circumferential direction does not need to be completely consistent with the circumferential direction of the circle centered on the rotation axis O. For example, it also includes Figure 2 The left-right direction is based on the window portion and the window hole shown in the upper part of the figure. In addition, the radial direction does not need to be completely consistent with the diameter direction of the circle centered on the rotation axis O. For example, it also includes the direction of the circle centered on the rotation axis O. Figure 2 The concept of the up and down direction is based on the window portion and window hole shown in the upper part.

[0031] The vibration damper device 1 is provided between a flywheel (not shown) and an input shaft of a drive unit, and is used to limit torque transmitted between the engine and the drive unit and to dampen rotational fluctuations.

[0032] [Torque limiting unit 10]

[0033] The torque limiting unit 10 is disposed on the outer periphery of the vibration damping unit 20. The torque limiting unit 10 limits the torque transmitted between the flywheel and the vibration damping unit 20. The torque limiting unit 10 includes a first side plate 11, a second side plate 12, a friction disk 13, a pressure plate 14, and a conical spring 15.

[0034] The first side plate 11 and the second side plate 12 are fixed to each other by multiple rivets. The friction disc 13 includes a core plate 131 and a pair of friction members 132. A pressure plate 14 and a conical spring 15 are positioned between the first side plate 11 and the friction disc 13. The conical spring 15 presses the friction disc 13 against the second side plate 12 via the pressure plate 14.

[0035] Vibration reduction unit 20

[0036] The vibration damper unit 20 includes an input-side plate 21 (an example of a first rotating body), a hub flange 22 (an example of a second rotating body), and a vibration damper portion 23 disposed between the input-side plate 21 and the hub flange 22 .

[0037] <Input side plate 21>

[0038] The input side plate 21 includes a first plate 211 and a second plate 212 (hereinafter, the first and second plates 211, 212 will sometimes be collectively referred to as the "input side plate 21"). The first plate 211 and the second plate 212 are both annular components with a center hole. The first and second plates 211, 212 are fixed to each other in the axial direction at a predetermined distance by four stop pins 24. Therefore, the first and second plates 211, 212 cannot move relative to each other in the axial and rotational directions. In addition, the inner circumference of the core plate 131 of the friction disk 13 is fixed to the first plate 211 by the stop pins 24.

[0039] A pair of first window portions 21a (an example of a first accommodating portion) and a pair of second window portions 21b are formed on the first plate 211 and the second plate 212, respectively. The pair of first window portions 21a are arranged opposite to each other with the rotation axis O interposed therebetween. Figure 2 , the first window portion 21a and the second window portion 21b of the second plate 212 are shown, and the first window portion and the second window portion of the first plate 211 are also constructed in the same manner. A pair of first window portions 21a are formed by cutting and standing up the plates 211 and 212, and have pressing surfaces 21c (an example of a first pressing surface) at both end faces in the circumferential direction, and have support portions at the outer periphery and the inner periphery, respectively. In addition, a pair of second window portions 21b are spaced 90° apart from the first window portions and are arranged relative to each other across the rotation axis O. The pair of second window portions 21b are rectangular openings that pass through in the axial direction, and have pressing surfaces 21d at both end faces in the circumferential direction.

[0040] <Hub flange 22>

[0041] The hub flange 22 is a component of a device for transmitting torque from the input side plate 21 to the output side. The hub flange 22 has a hub 221 and a flange 222. Figure 2 As shown, the hub 221 and the flange 222 are integrated by a plurality of teeth and a plurality of recesses engaged with the teeth.

[0042] The hub 221 is a cylindrical member, and is disposed in the center holes of the first plate 211 and the second plate 212. A spline hole is formed in the inner circumference of the hub 221, and an output-side component can be spline-engaged with the spline hole.

[0043] like Figure 2 and Figure 3 As shown, the flange 222 is formed into a disk shape and is arranged axially between the first plate 211 and the second plate 212. The flange 222 has a center hole, a pair of first window holes 22a (an example of a second accommodating portion), a pair of second window holes 22b, and four stopper holes 22c.

[0044] The first window holes 22a are arranged opposite each other across the rotation axis O and are formed at positions corresponding to the first window portions 21a of the first plate 211 and the second plate 212. The first window holes 22a have pressing surfaces 22d (an example of a first pressing surface) at both circumferential end surfaces. Furthermore, each pressing surface 22d has a protrusion 22e at its radial center portion that bulges toward the opposing pressing surface 22d.

[0045] The second window hole 22b is spaced 90° apart from the first window hole 22a, and is positioned opposite each other across the rotation axis O. Specifically, the second window hole 22b is formed at a position corresponding to the second window portion 21b of the first plate 211 and the second plate 212. The second window hole 22b is formed in an arc shape, with the pitch radius (the radius of the center of the radial width of the hole) located radially inward of the radial center of the first window hole 22a. The second window hole 22b has pressing surfaces 22f on both circumferential end surfaces. The distance between the two pressing surfaces 22f is set to be longer than the distance between the two pressing surfaces 21d of the second window portion 21b of the input-side plate 21.

[0046] The stopper hole 22c is an elongated hole extending in an arcuate pattern on either side of the first window hole 22a in the circumferential direction. The end of the stopper hole 22c facing away from the first window hole 22a extends radially outward from the second window hole 22b. Furthermore, the end of the stopper hole 22c facing the first window hole 22a extends toward the protrusion 22e of the first window hole 22a. Specifically, the end of the stopper hole 22c facing the first window hole 22a reaches a straight line L. Here, straight line L connects the outer and inner circumferential end surfaces of the first window hole 22a, where the protrusion 22e is not formed.

[0047] With this configuration, the end of the stopper hole 22c on the first window hole 22a side can be extended further than in a case where the protrusion 22e is not formed in the first window hole 22a. As a result, the angle formed by the rotation axis O and the pair of stopper pins 24 across the first window hole 22a can be made closer to 90 degrees. It should be noted that the four stopper holes 22c have the same pitch radius. In other words, the four stopper holes 22c are formed on the same circumference.

[0048] Furthermore, the stopper pin 24 axially extends through the stopper hole 22c. Therefore, the input side plate 21 and the hub flange 22 are capable of relative rotation within the range within which the stopper pin 24 can move within the stopper hole 22c. In other words, the stopper pin 24 and the stopper hole 22c form a stopper mechanism 25, which prevents relative rotation between the input side plate 21 and the hub flange 22 by abutting the stopper pin 24 against the end surface of the stopper hole 22c.

[0049] <Vibration damping unit 23>

[0050] The vibration damping part 23 is a mechanism for elastically connecting the input side plate 21 and the hub flange 22 in the rotation direction. Figure 1 and Figure 2 As shown, the present invention comprises two coil springs 27, two resin members 28, a pair of spring seats 30 supporting the end faces of the coil springs 27, and a hysteresis generating mechanism 31 (see FIG. Figure 1 ).

[0051] The coil spring 27 is accommodated in the first window hole 22a of the flange 222, and the resin member 28 is accommodated in the second window hole 22b of the flange 222. The coil spring 27 and the resin member 28 are supported in the axial and radial directions by the windows 21a and 21b of the first and second plates 211 and 212, respectively.

[0052] It should be noted that the resin member 28 is circumferentially disposed within the second window portion 21b of the input-side plate 21 without any gap. On the other hand, the resin member 28 is shorter than the circumferential width of the second window opening 22b of the flange 222. In other words, when the input-side plate 21 and the hub flange 22 are in a neutral position, with no relative rotation (the torsion angle is "0"), gaps are formed between the ends of the resin member 28 and the pressing surfaces 22f of the second window opening 22b of the flange 222 (details regarding these gaps will be described later).

[0053] The spring seats 30 are arranged at both circumferential ends of the first window hole 22a of the flange 222. The spring seats 30 support the end surface of the coil spring 27 and a portion of the outer periphery of the coil spring 27 (both circumferential ends).

[0054] like Figure 4 and Figure 5As shown, the spring seat 30 has an end surface support portion 301 and an outer peripheral support portion 302. It should be noted that, Figure 4 is a side view of the spring seat 30 (viewed from one side in the circumferential direction), Figure 5 for Figure 4 VV line cross-sectional view.

[0055] The end surface support portion 301 supports the end surface of the coil spring 27, and the end surface support portion 301 is supported by the pressing surface 21c of the first window portion 21a of the input side plate 21 and the pressing surface 22d of the first window hole 22a of the flange 222. Figure 5 As shown, the surface of the end surface support portion 301, which is supported by the pressing surface 22d of the first window 22a, has a recessed portion 301a that is arcuately recessed toward the coil spring 27. Furthermore, a hole 301b is formed in the center of this recess 301a, i.e., the radial center and the axial center, extending circumferentially therethrough. The protrusion 22e of the first window 22a of the flange 222 is fitted into this recess 301a.

[0056] As described above, the coil spring 27 is accommodated in the first window portions 21 a of the first and second plates 211 and 212 and the first window hole 22 a of the flange 222 with no gap in the circumferential direction via the spring seat 30 .

[0057] The outer peripheral support portion 302 is formed to extend circumferentially from the outer peripheral end portion of the end surface support portion 301. The outer peripheral support portion 302 is positioned between the outer peripheral portions of the two ends of the coil spring 27 and the inner peripheral surfaces of the first window portion 21a and the first window hole 22a. Therefore, even if the coil spring 27 moves outward due to centrifugal force or while compressed, contact between the coil spring 27 and the first window portion 21a and the first window hole 22a is avoided.

[0058] The hysteresis generating mechanism 31 is arranged between the first plate 211 and the second plate 212 and the hub flange 22 in the axial direction. Figure 1 As shown, the hysteresis generating mechanism 31 includes a first bushing 41 , a second bushing 42 , a third bushing 43 and a conical spring 44 .

[0059] The first and second bushings 41, 42 are arranged on the outer circumferential surface of the hub 221, axially between the inner circumferential end of the first plate 211 and the flange 222. The second bushing 42 is non-rotatably engaged with the hub 221 and in frictional contact with the first bushing 41. The third bushing 43 is arranged axially between the inner circumferential end of the second plate 212 and the flange 222. The third bushing 43 is non-rotatably engaged with the second plate 212 and in frictional contact with the flange 222. A conical spring 44 is compressed and arranged between the third bushing 43 and the second plate 212.

[0060] With the above-described configuration, when the first plate 211 and the second plate 212 rotate relative to the hub flange 22 , a hysteresis torque is generated.

[0061] [action]

[0062] The torque transmitted from the engine to the flywheel is input to the vibration damping unit 20 via the torque limiting unit 10. In the vibration damping unit 20, the torque is input to the input-side plate 21 to which the friction disk 13 of the torque limiting unit 10 is fixed. This torque is then transmitted to the hub flange 22 via the coil spring 27 and the resin member 28. The power is then transmitted from the hub flange 22 to the output-side motor, generator, transmission, and the like.

[0063] In addition, for example, when the engine is started, due to the large inertia of the output side, excessive torque may be transmitted from the output side to the engine. In such a case, the torque limiting unit 10 limits the torque transmitted to the engine side to a predetermined value or less.

[0064] <Positive-side torsional characteristics>

[0065] The torsional characteristics on the positive side of the vibration damping unit 20 , that is, the characteristics when torque is input from the engine (input of positive torque) will be described.

[0066] When the input has positive torque, Figure 2 The input side plate 21 rotates in the R1 direction. Therefore, the two coil springs 27 are compressed between the spring seat 30 supported by the pressing surface 21c on the R2 side of the first window portion 21a of the input side plate 21 and the spring seat 30 supported by the pressing surface 22d on the R1 side of the first window hole 22a of the flange 222.

[0067] It should be noted that if Figure 2 As shown, the resin member 28 is supported without gap by the second window portion 21b of the input-side plate 21 when in neutral. However, a circumferential gap of θ1 exists on both the R1 and R2 sides of the second window hole 22b of the flange 222. Furthermore, a circumferential gap of θ2 exists between the stopper pin 24 and each stopper hole 22c on both the R1 and R2 sides. The relationship between these circumferential gaps (hereinafter referred to as "gap") is set as follows.

[0068] θ1﹤θ2

[0069] By setting the gap as described above, the resin member 28 is not compressed until the torsion angle between the input side plate 21 and the hub flange 22 (hereinafter referred to as the "twist angle") reaches θ1. Then, when the torsion angle exceeds θ1, the resin member 28 is compressed between the R2-side pressing surface 21d of the second window portion 21b of the input side plate 21 and the R1-side pressing surface 22f of the second window hole 22b of the flange 222. Therefore, as Figure 6 As shown, before the torsion angle reaches θ1, the torsion characteristic on the positive side is characteristic C1. When the torsion angle exceeds θ1, the torsion characteristic on the positive side becomes characteristic C2.

[0070] When the torsion angle reaches θ2, the stopper pin 24 abuts against the end surface of the stopper hole 22 c on the R1 side, and relative rotation between the input side plate 21 and the hub flange 22 is prohibited.

[0071] Negative-side torsional characteristics

[0072] The torsional characteristics on the negative side of the vibration damping unit 20 , that is, the characteristics when torque is input in the reverse direction from the drive unit side (input of negative torque) will be described.

[0073] When the input has negative torque, Figure 2 In the embodiment of the present invention, the hub flange 22 rotates in the R1 direction relative to the input-side plate 21. Therefore, the two coil springs 27 are compressed between the spring seat 30 attached to the R2-side pressing surface 22d of the first window hole 22a of the hub flange 22 and the spring seat 30 attached to the R1-side pressing surface 21c of the first window portion 21a of the input-side plate 21.

[0074] The action of the resin member 28 is the same as that when a positive torque is input. That is, it is not compressed until the torsion angle reaches -θ1. When the torsion angle is below -θ1, Figure 6 As shown, the torsional characteristic C1 with low rigidity is obtained. In addition, when the torsional angle reaches -θ1, the resin member 28 begins to be compressed between the R2 side pressing surface 22f of the second window hole 22b of the hub flange 22 and the R1 side pressing surface 21d of the second window portion 21b of the input side plate 21. Therefore, when the torsional angle exceeds -θ1, as shown in FIG. Figure 6 It is shown that the torsional characteristic C2 with high rigidity is achieved.

[0075] When the torsion angle reaches −θ2, the stopper pin 24 abuts against the R2-side end surface of the stopper hole 22 c, and relative rotation between the input-side plate 21 and the hub flange 22 is prohibited.

[0076] In this embodiment, a recess 301a is formed in the spring seat 30, and the protrusion 22e of the first window 22a formed in the flange 222 fits into this recess 301a. Consequently, the end of the stopper hole 22c extends toward the protrusion 22e. Consequently, the circumferential length of the stopper hole 22c can be increased. Specifically, compared to a case where the spring seat 30 lacks the recess 301a and the end surface of the window is formed from a single plane (a case where there is no protrusion), the torsion angle between the input-side plate 21 and the hub flange 22 can be increased (i.e., widened).

[0077] Furthermore, for the same reason, the ends of the stopper holes 22c on either side of the first window hole 22a of the flange 222 can be brought closer together. As a result, the angle formed by the rotation axis O and the stopper pins 24 on either side of the first window hole 22a can be made closer to 90 degrees, thereby suppressing unevenness in the strength of the input-side plate 21 and the hub flange 22.

[0078] [Other embodiments]

[0079] The present invention is not limited to the above-described embodiments, and various changes and modifications can be made without departing from the scope of the present invention.

[0080] (a) In the above embodiment, the hub flange 22 is composed of two components, the hub 221 and the flange 222 , but may be composed of a single component.

[0081] (b) In the aforementioned embodiment, spring seats are provided at both ends of the coil spring, but a spring seat may be provided only at one end of the coil spring. Alternatively, the spring seat of the present invention may be provided at one end of the coil spring, while another conventionally known spring seat may be provided at the other end.

[0082] (c) The configuration of the elastic member is not limited to two coil springs and two resin members. For example, all the elastic members may be coil springs, and the number of coil springs is not limited.

[0083] (d) In the above embodiment, the present invention is applied to the vibration damping device with a torque limiter, but it is also applicable to other vibration damping devices.

[0084] (e) Torsional characteristics are not limited to Figure 6 Features shown.

Claims

1. A vibration damping device comprising: The first rotating body has a plurality of first accommodating portions, each of the first accommodating portions having first pressing surfaces at both end surfaces in the circumferential direction; a second rotating body capable of rotating relative to the first rotating body and having a plurality of second accommodating portions, wherein the second accommodating portions have second pressing surfaces at both end surfaces in the circumferential direction; a plurality of elastic members, each of which is accommodated in the first accommodation portion and the second accommodation portion and elastically connects the first rotating body and the second rotating body in a rotational direction; a limiting mechanism comprising a limiting member and a limiting hole, wherein the limiting member is provided on the first rotating body, the limiting hole is formed in the second rotating body and extends in the circumferential direction, and the limiting member passes through the limiting hole; as well as a spring seat supporting at least one end surface of at least one elastic member among the plurality of elastic members; The spring seat has: an end face support portion having a recessed portion in a radially central portion thereof that is recessed toward the elastic member, the end face support portion supporting the end face of the elastic member and being supported by the first pressing face and the second pressing face; and an outer peripheral support portion supporting a portion of a radially outer portion of the elastic member, The second rotating body has a protrusion protruding in the circumferential direction on at least one second pressing surface of the second accommodating portion, and the protrusion is embedded in the recess of the spring seat. One end portion of the stopper hole in the circumferential direction extends toward the protruding portion. One end portion of the stopper hole reaches a predetermined straight line connecting an outer peripheral end surface and an inner peripheral end surface of the second accommodating portion where the protrusion is not formed.

2. The vibration damping device according to claim 1, wherein: The recess has a hole penetrating in the circumferential direction.

3. The vibration damping device according to claim 1 or 2, wherein: The first rotating body includes a first plate and a second plate which are spaced apart in the axial direction. The second rotating body is arranged between the first plate and the second plate in the axial direction.

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