Damping device

Abstract

A damper device enables a longer formation of a hole for a stopper in a circumferential direction, which constitutes a stopper mechanism. The damper device (1) is provided with an input side plate (21), a hub flange (22), a plurality of coil springs (27), and a stopper mechanism (25). The stopper mechanism (25) has a plurality of holes for stoppers (22c) and a plurality of stopper pins (24). The hole for the stopper (22c) is formed in a manner extending in the circumferential direction on both sides of a first window hole (22a) of the hub flange (22). The stopper pin (24) is fixed to the input side plate (21) and is movable in the circumferential direction within the hole for the stopper (22c). The hub flange (22) has a protruding portion (22e) protruding in the circumferential direction on a pressing surface (22d) of the first window hole (22a), and an end portion of the hole for the stopper (22c) near the first window hole (22a) extends toward the protruding portion (22e).

Description

TECHNICAL FIELD

[0001] The present application relates to a vibration damper. BACKGROUND

[0002] In order to transmit power generated in an engine to a transmission side and to attenuate rotational variation, a power transmission device having a vibration damper is mounted on a vehicle.

[0003] Such a vibration damper has an input rotation body, an output rotation body, and a plurality of coil springs. The coil springs are arranged in window portions of the input rotation body and window holes of the output rotation body, and elastically link the input rotation body and the output rotation body in a rotational direction.

[0004] In addition, as shown in Patent Document 1, in order to restrict mutual relative rotation of the input rotation body and the output rotation body, a stopper mechanism is provided in the vibration damper. The stopper mechanism has a plurality of stopper pins and notches. The stopper pins are fixed to the input rotation body, and pass through the notches formed in the output rotation body.

[0005] In Patent Document 1, as the notches that constitute the stopper mechanism, notches that open toward the outer circumferential side are formed, and as other constitution, a constitution in which a hole for stopper is formed in a circular arc shape and the stopper pin passes through the hole for stopper is provided.

[0006] Patent Document 1: Japanese Patent Application Publication No. 2004-197781

[0007] Here, in order to make the rotational variation performance of the vibration damper good, it is preferable to widen (i.e., widen the angle) the torsion angle of the output rotation body with respect to the input rotation body. In order to achieve this widening, it is necessary to ensure that the length of the notches or the hole for stopper of the output rotation body in the circumferential direction is long.

[0008] However, in the output rotation body, the notches including the hole for stopper and the window holes are often arranged at positions that overlap in the radial direction, and thus the hole for stopper cannot be formed long. SUMMARY

[0009] The technical problem of the present application is to enable the hole for stopper that constitutes the stopper mechanism to be formed long in the circumferential direction in the vibration damper.

[0010] (1) The vibration damping device of the present application includes a first rotating body, a second rotating body, a plurality of elastic members, and a stopper mechanism. The first rotating body has a plurality of first accommodating portions. The second rotating body is configured to be able to rotate in opposition to the first rotating body and has a plurality of second accommodating portions, each of which has a pressing surface at both ends in a circumferential direction. The plurality of elastic members are accommodated in the first accommodating portions and the second accommodating portions and elastically link the first rotating body and the second rotating body in a rotational direction. The stopper mechanism has a plurality of first notches and a plurality of second notches and a plurality of stopper members. The plurality of first notches and the plurality of second notches are formed in a manner of extending in the circumferential direction at both sides of the second accommodating portions in the circumferential direction. The plurality of stopper members are fixed to the first rotating body and are able to move in the circumferential direction in the first notches and the second notches.

[0011] In addition, the second rotating body has a protruding portion protruding in the circumferential direction at one of the pressing surfaces of the second accommodating portions, and the first notches are holes, and an end portion of the first notches close to the second accommodating portions extends toward the protruding portion.

[0012] Here, the protruding portion is formed at one of the pressing surfaces of the second accommodating portions. Therefore, the end portion of the first notches (holes) of the stopper mechanism in the circumferential direction can be formed longer toward the protruding portion. As a result, the torsion angle of the first rotating body and the second rotating body can be wide-angled.

[0013] (2) Preferably, the second rotating body has a protruding portion protruding in the circumferential direction at the other of the pressing surfaces of the second accommodating portions. In this case, the second notches are holes, and an end portion of the second notches close to the second accommodating portions extends toward the protruding portion.

[0014] (3) Preferably, the second notches are holes, and an end portion of the second notches close to the second accommodating portions communicates with the second accommodating portions. In this case, the second notches of the stopper mechanism can be formed longer in the circumferential direction, and the torsion angle can be wide-angled.

[0015] (4) Preferably, the first notches are formed in a circular arc shape at a first pitch radius, and the second notches are holes formed in a circular arc shape at a second pitch radius closer to an inner circumferential side than the first pitch radius.

[0016] Here, the first notches and the second notches that are holes are formed at positions offset in a radial direction. Therefore, two notches adjacent in the circumferential direction can be brought close to each other, and the strength of each of the first rotating body and the second rotating body can be made uniform.

[0017] (5) Preferably, the damper device further has a spring seat. The spring seat is supported by the pressing surface of the second housing portion formed with the protrusion, and supports the end surface of the elastic member. The spring seat has an end surface supporting portion and an outer peripheral supporting portion. The end surface supporting portion has a recessed portion recessed toward the elastic member side in the central portion in the radial direction, and the protrusion is fitted into the recessed portion. In addition, the outer peripheral supporting portion supports a portion of the outer side portion of the elastic member in the radial direction.

[0018] Here, even in the case where the spring seat is provided to the second housing portion, the notch of the stopper mechanism can be formed longer in the circumferential direction as described above.

[0019] Effects of the Invention

[0020] With the present application as described above, in the damper device, the stopper hole constituting the stopper mechanism can be formed longer in the circumferential direction. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 is a sectional view of a damper device with a torque limiter according to the first embodiment of the present application.

[0022] Figure 2 is a front view of a damper unit of the damper device of Figure 1

[0023] Figure 3 is a front view of a flange of the damper device of Figure 1

[0024] Figure 4 is a side view of a spring seat of the damper device of Figure 1

[0025] Figure 5 is a V-V line sectional view of the damper device of Figure 4

[0026] Figure 6 is a torsion characteristic line diagram.

[0027] Figure 7 is a diagram corresponding to Figure 2 of the second embodiment of the present application.

[0028] Figure 8 is a diagram corresponding to Figure 3 of the second embodiment of the present application.

[0029] Explanation of Reference Numerals

[0030] ​​​​21: input-side plate (first rotating body); 21a: first window portion (first accommodating portion); 21c: pressing surface; 22: hub flange (second rotating body); 22a, 51a: first window hole (second accommodating portion); 22c: stopper hole (first and second notches); 22d: pressing surface; 22e: protruding portion; 24: stopper pin; 25: stopper mechanism; 27: coil spring (elastic member); 28: resin member (elastic member); 30: spring seat; 301: end surface support portion; 301a: recessed portion; 302: outer peripheral support portion; 50: flange; 52a: first stopper hole (first notch); 52b: second stopper hole (second notch). DETAILED DESCRIPTION

[0031] First Embodiment

[0032] [Overall Configuration]

[0033] Figure 1 is a cross-sectional view of a vibration-damping device 1 with a torque limiter according to the first embodiment of the present application (hereinafter, sometimes simply referred to as "vibration-damping device"). In addition, FIG. 2 is a front view of the vibration-damping device 1, shown with a part of the components detached, or with a part of the components deleted. In Figure 2 is a front view of the vibration-damping device 1, shown with a part of the components detached, or with a part of the components deleted. In Figure 1 , the O-O line is the rotation axis. In Figure 1 , an engine is disposed on the left side of the vibration-damping device 1, and a drive unit including a motor, a transmission, and the like is disposed on the right side.

[0034] Note 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 a circle centered on the rotation axis O, and the radial direction is the radial direction of the circle centered on the rotation axis O. Note that the circumferential direction need not necessarily be exactly the same as the circumferential direction of the circle centered on the rotation axis O, and, for example, it is a concept that also includes the left-right direction with reference to the window portion and the window hole shown in the upper portion of Figure 2 . In addition, the radial direction need not necessarily be exactly the same as the diameter direction of the circle centered on the rotation axis O, and, for example, it is a concept that also includes the up-down direction with reference to the window portion and the window hole shown in the upper portion of Figure 2

[0035] The vibration-damping device 1 is provided between a not-shown flywheel and an input shaft of the drive unit, and is a device for limiting the torque transmitted between the engine and the drive unit and for attenuating the rotation variation. The vibration-damping device 1 has a torque limiter unit 10 and a vibration-damping unit 20.

[0036] [Torque Limiter Unit 10]

[0037] ​The torque limiting unit 10 is arranged on the outer periphery side of the damping unit 20. The torque limiting unit 10 limits the torque transmitted between the flywheel and the damping unit 20. The torque limiting unit 10 has a first side plate 11 and a second side plate 12, a friction plate 13, a pressure plate 14, and a coned spring 15.

[0038] The first side plate 11 and the second side plate 12 are fixed to each other by a plurality of rivets. The friction plate 13 has a core plate 131 and a pair of friction members 132. The pressure plate 14 and the coned spring 15 are arranged between the first side plate 11 and the friction plate 13. The coned spring 15 presses the friction plate 13 to the second side plate 12 via the pressure plate 14.

[0039] [Damper unit 20]

[0040] The damping unit 20 includes an input side plate 21 (one example of the first rotary body), a hub collar 22 (one example of the second rotary body), and a damping portion 23 arranged between the input side plate 21 and the hub collar 22.

[0041] < Input side plate 21 >

[0042] The input side plate 21 has a first plate 211 and a second plate 212 (hereinafter, the first plate 211 and the second plate 212 are also referred to as "input side plate 21" collectively). Both the first plate 211 and the second plate 212 are annular members having a central hole. The first plate 211 and the second plate 212 are fixed to each other at a predetermined interval in the axial direction by four stop pins 24. Therefore, the first plate 211 and the second plate 212 cannot move relatively in the axial direction and the rotational direction. In addition, on the first plate 211, the inner peripheral portion of the core plate 131 of the friction plate 13 is fixed by the stop pin 24.

[0043] A pair of first window portions 21a (one example of the first accommodation 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 each other across the rotational axis O. The pair of second window portions 21b are arranged opposite each other across the rotational axis O at an interval of 180°. Figure 2 In the drawing, 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 similarly configured. The pair of first window portions 21a are formed by cutting each plate 211, 212 and standing up, have a pressing surface 21c at both end surfaces in the circumferential direction, and have a support portion at the outer peripheral edge and the inner peripheral edge, respectively. In addition, the pair of second window portions 21b are arranged opposite each other across the rotational axis O at an interval of 90° from the first window portion. The pair of second window portions 21b are rectangular openings that penetrate in the axial direction, and have a pressing surface 21d at both end surfaces in the circumferential direction.

[0044] < Hub collar 22 >

[0045] 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. As shown in Figure 2 the hub 221 and the flange 222 are integrated by a plurality of teeth and a plurality of recesses engaged with the teeth.

[0046] The hub 221 is a cylindrical component disposed in the central hole of the first plate 211 and the second plate 212. A spline hole is formed in the inner peripheral portion of the hub 221, and the component of the output side can be spline-fitted to the spline hole.

[0047] As shown in Figure 2 and Figure 3 the flange 222 is formed in a circular plate shape and is disposed between the axial directions of the first plate 211 and the second plate 212. The flange 222 has a central hole, a pair of first window holes 22a (one example of a second accommodation portion), a pair of second window holes 22b, and four stopper holes 22c (one example of a first notch and a second notch).

[0048] The first window holes 22a are disposed 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 at both ends in the circumferential direction. Further, each pressing surface 22d has a protruding portion 22e protruding in a manner bulging toward the opposite pressing surface 22d at the central portion in the radial direction.

[0049] The second window holes 22b are disposed opposite each other across the rotation axis O at an interval of 90° from the first window holes 22a. That is, the second window holes 22b are formed at positions corresponding to the second window portions 21b of the first plate 211 and the second plate 212. The second window holes 22b are formed in a circular arc shape, and the pitch radius (radius of the central position of the radial width of the hole) of the second window holes 22b is located more radially inward than the radial center position of the first window holes 22a. The second window holes 22b have pressing surfaces 22f at both ends in the circumferential direction, and 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 portions 21b of the input side plate 21.

[0050] The stopper holes 22c are long holes extending in a circular arc shape on both sides in the circumferential direction of the first window holes 22a. The end portion of the stopper holes 22c on the side away from the first window holes 22a extends to the radially outer side of the second window holes 22b. In addition, the end portion of the stopper holes 22c on the side close to the first window holes 22a extends toward the protruding portion 22e of the first window holes 22a. Specifically, the end portion of the stopper holes 22c on the side of the first window holes 22a reaches the straight line L. Here, the straight line L is a straight line connecting the end surface on the outer peripheral side and the end surface on the inner peripheral side of the first window holes 22a on which the protruding portion 22e is not formed.

[0051] In such a configuration, the end portion of the first window hole 22a on the side of the stopper hole 22c can be formed to extend longer than in the case where the protruding portion 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 close to 90 degrees. Note that the pitch radii of the four stopper holes 22c are the same. That is, the four stopper holes 22c are formed on the same circumference.

[0052] Further, the stopper pin 24 penetrates the stopper hole 22c in the axial direction. Therefore, the input-side plate 21 and the hub flange 22 can relatively rotate within a range in which the stopper pin 24 is movable within the stopper hole 22c. In other words, the stopper mechanism 25 is configured by the stopper pin 24 and the stopper hole 22c, and the mutual relative rotation of the input-side plate 21 and the hub flange 22 is prohibited by the stopper pin 24 abutting against the end face of the stopper hole 22c.

[0053] <Damping portion 23>

[0054] The damping portion 23 is a mechanism for elastically linking the input-side plate 21 and the hub flange 22 in the rotational direction, and is configured as shown in Figs. 1 and 2, for example. Figure 1 Figure 2 As shown in Figs. 1 and 2, the damping portion 23 has two coil springs 27 and two resin members 28, a pair of spring seats 30 that support the end faces of the coil springs 27, and a hysteresis generation mechanism 31 (see Fig. 3). Figure 1

[0055] The coil springs 27 are accommodated in the first window holes 22a of the flange 222, and the resin members 28 are accommodated in the second window holes 22b of the flange 222. Further, the coil springs 27 and the resin members 28 are supported in the axial and radial directions by the window portions 21a, 21b of the first and second plates 211, 212.

[0056] Note that the resin members 28 are disposed in the second window portions 21b of the input-side plate 21 without a gap in the circumferential direction. On the other hand, the resin members 28 are shorter than the width of the second window holes 22b of the flange 222 in the circumferential direction. That is, at the neutral time when the input-side plate 21 and the hub flange 22 are not relatively rotated (the torsion angle is "0"), a gap is formed between the both end portions of the resin members 28 and the pressing faces 22f of the second window holes 22b of the flange 222 (the details of the gap will be described later).

[0057] The spring seats 30 are disposed at both ends in the circumferential direction of the first window holes 22a of the flange 222. The spring seats 30 support the end faces of the coil springs 27, and also support a part (both ends in the circumferential direction) of the outer peripheral portions of the coil springs 27.

[0058] As shown in Figs. 1 and 2, the damping portion 23 has two coil springs 27 and two resin members 28, a pair of spring seats 30 that support the end faces of the coil springs 27, and a hysteresis generation mechanism 31 (see Fig. 3). Figure 4 Figure 5 ​​​As shown, the spring seat 30 has an end face supporting portion 301 and an outer peripheral supporting portion 302. Note that, Figure 4 is a side view of the spring seat 30 (a view from the side in the circumferential direction), Figure 5 is a Figure 4 V-V line cross-sectional view.

[0059] The end face supporting portion 301 supports the end face of the coil spring 27, and is supported by the pressing face 21c of the first window portion 21a of the input side plate 21 and the pressing face 22d of the first window hole 22a of the flange 222. As shown in Figure 5 , a recessed portion 301a recessed in a circular arc shape toward the coil spring 27 side is formed in the face of the end face supporting portion 301 that is supported by the pressing face 22d of the first window hole 22a. Further, a hole 301b that penetrates in the circumferential direction is provided in the central portion in the radial direction and in the axial direction of this recessed portion 301a. Thus, the protruding portion 22e of the first window hole 22a of the flange 222 is fitted into this recessed portion 301a.

[0060] As described above, the coil spring 27 is housed in the first window portion 21a of the first plate 211 and the first window hole 22a of the flange 222 without a gap in the circumferential direction by means of the spring seat 30.

[0061] The outer peripheral supporting portion 302 is formed extending from the outer peripheral end portion of the end face supporting portion 301 in the circumferential direction. This outer peripheral supporting portion 302 is disposed between the outer peripheral portions of both end portions of the coil spring 27 and the inner peripheral faces of the first window portion 21a and the first window hole 22a. Therefore, even if the coil spring 27 moves to the outer peripheral side due to centrifugal force or in a compressed state, it is possible to avoid contact of the coil spring 27 with the first window portion 21a and the first window hole 22a.

[0062] The hysteresis generation mechanism 31 is disposed between the first plate 211 and the second plate 212 and the axial direction of the hub flange 22. As shown in Figure 1 , the hysteresis generation mechanism 31 has a first bushing 41, a second bushing 42, a third bushing 43, and a coned spring 44.

[0063] The first bushing 41 and the second bushing 42 are disposed between the inner peripheral end portion of the first plate 211 and the axial direction of the flange 222 on the outer peripheral face of the hub 221. The second bushing 42 is engaged with the hub 221 in a manner that does not rotate relatively, and is in frictional contact with the first bushing 41. The third bushing 43 is disposed between the inner peripheral end portion of the second plate 212 and the axial direction of the flange 222. The third bushing 43 is engaged with the second plate 212 in a manner that does not rotate relatively, and is in frictional contact with the flange 222. The coned spring 44 is disposed between the third bushing 43 and the second plate 212 in a compressed state.

[0064] With the above configuration, when the first plate 211 and the second plate 212 are rotated relative to the hub flange 22, a hysteresis torque is generated.

[0065] [Action]

[0066] The torque transmitted from the engine to the flywheel is input to the damping unit 20 via the torque limiting unit 10. In the damping unit 20, the torque is input to the input-side plate 21 in which the torque limiting unit 10 is fixed, and the torque is transmitted to the hub flange 22 via the coil springs 27 and the resin member 28. Then, the power is transmitted from the hub flange 22 to the output-side motor, generator, transmission, and the like.

[0067] In addition, for example, at the time of engine start, since the inertia amount of the output side is large, an excessive torque is sometimes transmitted from the output side to the engine. In such a case, the torque transmitted to the engine side is limited to a predetermined value or less by the torque limiting unit 10.

[0068] <Positive-side torsional characteristic>

[0069] The positive-side torsional characteristic in the damping unit 20, that is, the characteristic at the time of input of the torque from the engine (input of the positive-side torque) is described.

[0070] When the positive-side torque is input, the input-side plate 21 is rotated in the Rl direction in the Figure 2 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 Rl side of the first window hole 22a of the flange 222.

[0071] Note that, as shown in Figure 2 the resin member 28 is supported without a gap by the second window portion 21b of the input-side plate 21 at the neutral position, but there are circumferential direction gaps of θl on the Rl side and the R2 side in the second window hole 22b of the flange 222. In addition, there are circumferential direction gaps of θ2 on the Rl side and the R2 side between the stopper pin 24 and each stopper hole 22c. Here, the relationship of each circumferential direction gap (hereinafter, simply referred to as "gap") is set as follows.

[0072] θl < θ2

[0073] By setting the gap as above, the resin member 28 is not compressed until the twist angle of the input-side plate 21 and the hub flange 22 (hereinafter referred to as "twist angle", the twist angle of the input-side plate 21 and the hub flange 22) reaches θ1. Then, if the twist 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 shown in FIG. 6, before the twist angle reaches θ1, the positive-side twist characteristic is the characteristic C1, and if the twist angle exceeds θ1, the positive-side twist characteristic becomes the characteristic C2. Figure 6

[0074] In addition, if the twist angle reaches θ2, the limit pin 24 abuts against the R1-side end surface of the limit hole 22c, and the mutual relative rotation of the input-side plate 21 and the hub flange 22 is prohibited.

[0075] <Negative-side twist characteristic>

[0076] The negative-side twist characteristic in the damper unit 20, that is, the characteristic when a torque is inputted from the drive unit side in the reverse direction (input of negative-side torque) is described.

[0077] When a negative-side torque is inputted, in Figure 2 , the hub flange 22 rotates in the R1 direction with respect to the input-side plate 21. Therefore, the two coil springs 27 are compressed between the spring seat 30 installed to the R2-side pressing surface 22d of the first window hole 22a of the hub flange 22 and the spring seat 30 installed to the R1-side pressing surface 21c of the first window portion 21a of the input-side plate 21.

[0078] As for the action of the resin member 28, it is the same as in the case where a positive-side torque is inputted. That is, before the twist angle reaches -θ1, it is not compressed, and when the twist angle is -θ1 or less, as shown in FIG. 8, the twist characteristic C1 of low rigidity is obtained. In addition, if the twist angle reaches -θ1, the resin member 28 starts 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, if the twist angle exceeds -θ1, as shown in FIG. 9, the twist characteristic C2 of high rigidity is obtained. Figure 6 Figure 6

[0079] If the twist angle reaches -θ2, the limit pin 24 abuts against the R2-side end surface of the limit hole 22c, and the mutual relative rotation of the input-side plate 21 and the hub flange 22 is prohibited.

[0080] ​​​In such an embodiment, the spring seat 30 is formed with a recess 301a into which the protruding portion 22e of the first window hole 22a formed in the flange 222 is fitted. Thus, the end portion of the stopper hole 22c extends toward the protruding portion 22e. Therefore, the length of the stopper hole 22c in the circumferential direction can be made longer. That is, compared with the case where the spring seat 30 is not formed with the recess 301a and the end surface of the window hole is formed by one flat surface (the case where there is no protruding portion), the torsion angle of the input-side plate 21 and the flange 22 can be increased (i.e., wide-angle).

[0081] In addition, according to the same reason, the end portions of the stopper holes 22c on both sides of the first window hole 22a of the flange 222 can be made close to each other. As a result, the angle formed by the rotation axis O and the stopper pins 24 on both sides of the first window hole 22a can be made close to 90 degrees, and the unevenness of the strength of the input-side plate 21 and the flange 22 can be suppressed.

[0082] - Second Embodiment -

[0083] In Figure 7 and Figure 8 a vibration damping unit 20' and a flange 50 according to a second embodiment of the present application are shown. In the second embodiment, the configuration other than the flange 50 is the same as that of the first embodiment. In addition, in the flange 50, the configuration other than the first window hole and the stopper hole is the same as that of the flange 222 of the first embodiment.

[0084] The flange 50 has a central hole, a pair of first window holes 51a (one example of a second accommodation portion) and a pair of second window holes 51b, and a pair of first stopper holes 52a (one example of a first notch) and a pair of second stopper holes 52b (one example of a second notch). The arrangement of each window hole 51a, 51b is the same as that of the first embodiment.

[0085] The pressing surface 51d on the Rl side of the first window hole 51a has a protruding portion 51e. The protruding portion 51e protrudes in the center portion in the radial direction of the pressing surface 51d in a manner that bulges in the circumferential direction (more specifically, toward the R2 side).

[0086] The pair of first stopper holes 52a are long holes that extend in a circular arc shape on the Rl side in the circumferential direction of the first window hole 51a. The end portion on the Rl side of the first stopper hole 52a extends to the radial direction outside of the second window hole 51b. In addition, the end portion on the R2 side of the first stopper hole 52a extends toward the protruding portion 51e of the first window hole 51a. Specifically, the end portion on the R2 side of the first stopper hole 52a reaches the straight line L. Here, the straight line L is a straight line that connects the pressing surface on the outer circumferential side and the pressing surface on the inner circumferential side of the first window hole 51a on which the protruding portion 51e is not formed.

[0087] A pair of second-limiting holes 52b are long holes extending in a circular arc shape on the R2 side of the first window hole 51a in the circumferential direction. The R2-side end portion of the second-limiting hole 52b extends to the radially outer side of the second window hole 51b, and the Rl-side end portion of the second-limiting hole 52b communicates with the radially intermediate portion of the first window hole 51a.

[0088] In such a configuration, the R2-side end portion of the first-limiting hole 52a can be formed to extend longer than in the case where the protruding portion 51e is not formed in the first window hole 51a. In addition, since the second-limiting hole 52b communicates with the first window hole 51a, the angle formed by the rotation axis O and the pair of limiting pins 24 across the first window hole 51a can be made close to 90 degrees.

[0089] In addition, since the one end portion of the first window hole 51a does not communicate with the first-limiting hole 52a, the strength of the flange 50 can be suppressed from decreasing.

[0090] The torsional characteristics of the second embodiment are the same as those of the first embodiment, and the same effects as those of the first embodiment can be obtained even in such a second embodiment.

[0091] Here, in the second embodiment, the radial positions of the pair of first window holes 51a are the same, but the pitch radius Pl of the first-limiting hole 52a (the radius of the radially central portion of the first-limiting hole 52a) is larger than the pitch radius P2 of the second-limiting hole 52b. That is, the first-limiting hole 52a and the second-limiting hole 52b are formed at positions that are offset in the radial direction.

[0092] Therefore, the R2-side end portion of the first-limiting hole 52a can be made to extend toward the radially central portion of the first window hole 51a (i.e., the protruding portion 51e). In addition, the Rl-side end portion of the second-limiting hole 52b can be made to communicate with the radially central portion of the first window hole 51a.

[0093] In the second embodiment, the spring seat 30 for the Rl-side pressing surface 51d of the first window hole 51a is the same as the spring seat 30 of the first embodiment. In addition, the spring seat for the R2-side pressing surface of the first window hole 51a is a spring seat that is known in the art, and detailed description thereof is omitted here.

[0094] [Other Embodiments]

[0095] The present application is not limited to the above-described embodiments, and various modifications or changes can be made without departing from the scope of the present application.

[0096] (a) In the foregoing embodiments, the hub flange 22 is configured from two components, the hub 221 and the flange 222, but can be configured from one component.

[0097] (b) In the foregoing embodiment, spring seats are provided at both ends of the helical spring, but spring seats may not be provided. Furthermore, spring seats may be provided only at one end of the helical spring.

[0098] (c) In the first embodiment, protrusions 22e are provided on the pressing surfaces 22d at both ends of the first window opening 22a. However, it is also possible to form protrusions on only one pressing surface and make the other pressing surface a flat surface. In this case, the limiting hole extending toward the other pressing surface may also be a notch that opens to the outer periphery.

[0099] (d) The composition of the elastic components is not limited to two helical springs and two resin components. For example, all the elastic components can be helical springs, and the number is not limited.

[0100] (e) In the foregoing embodiments, the present invention was applied to a vibration damping device with a torque limiter, but it can also be applied to other vibration damping devices.

[0101] (f) Torsional properties are not limited to Figure 6 The characteristics shown.

Claims

1. A vibration damping device comprising: a first rotating body having a plurality of first accommodating portions; a second rotating body configured to be relatively rotatable with the first rotating body and having a plurality of second accommodating portions each having a pressing surface at both ends in a circumferential direction; a plurality of elastic members accommodated in the first accommodating portions and the second accommodating portions and elastically connecting the first rotating body and the second rotating body in a rotational direction; and a stopper mechanism having a plurality of first notches and second notches each formed in a manner of extending in the circumferential direction at both sides of the second accommodating portions in the circumferential direction and a plurality of stopper members fixed to the first rotating body and movable in the circumferential direction in the first notches and the second notches, wherein the second rotating body has a protruding portion protruding in the circumferential direction at a pressing surface of the second accommodating portion, wherein the first notches and the second notches are holes, and an end portion of the first notches near the second accommodating portion extends toward the protruding portion.

2. The vibration damping device according to claim 1, wherein the second rotating body has a protruding portion protruding in the circumferential direction at another pressing surface of the second accommodating portion, and an end portion of the second notches near the second accommodating portion extends toward the protruding portion.

3. The vibration damping device according to claim 1, wherein an end portion of the second notches near the second accommodating portion communicates with the second accommodating portion.

4. The vibration damping device according to claim 3, wherein the first notches are formed in a circular arc shape at a first pitch radius, and the second notches are holes formed in a circular arc shape at a second pitch radius more inward than the first pitch radius.

5. The vibration damping device according to any one of claims 1 to 4, further comprising a spring seat supported by the pressing surface of the second accommodating portion in which the protruding portion is formed and supporting an end surface of the elastic member, wherein the spring seat has an end surface supporting portion and an outer peripheral supporting portion, the end surface supporting portion has a recessed portion recessed toward the elastic member side at a central portion in a radial direction and into which the protruding portion is fitted, and the outer peripheral supporting portion supports a part of a radially outer portion of the elastic member. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

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