JP7069863B2 - Damper device - Google Patents

Description

The technique disclosed in the present invention relates to a damper device that absorbs fluctuations in torque transmitted between a first rotating body and a second rotating body.

In a vehicle or the like, a damper device for absorbing the vibration of the power transmitted from the drive source to the transmission is provided on the power transmission path between the drive source of the engine or the like and the transmission. The damper device is generally incorporated in a clutch device (clutch disk).

The general configuration of the damper device is to insert a coil spring between the first rotating body (for example, a disc plate) and the second rotating body (for example, a clutch hub) that can rotate relative to each other, and the elasticity of the coil spring. The deformation is used to absorb and attenuate the vibration in the torsional direction caused by the fluctuation of torque.

In such a damper device, as generally disclosed in Patent Document 1, a pair of seat members are arranged inside a window portion provided on a disc plate so as to support a coil spring (elastic member). A clutch hub (hub flange) is provided so as to engage with the pair of seat members. As a result, the driving force from the driving source such as the engine is sequentially transmitted to the disc plate, the seat member, the coil spring, the clutch hub, and the input shaft of the transmission. On the other hand, the relative rotation between the disc plate and the clutch hub is stopped when the tips of the protrusions (reference numeral 48 in Patent Document 1) provided on each of the pair of seat members come into contact with each other. Therefore, in this case, the seat member is provided with a stopper function for stopping the relative rotation.

Further, in Patent Document 1, as another embodiment, a coil spring supported by a pair of seat members and a pair of seat members arranged in the coil spring are provided in a part of the window portion provided on the disc plate. A float body that can move in the circumferential direction and is elastically deformable is provided, and a stopper torque generating member is provided in place of a coil spring and a seat member in the other windows, so that the disc plate and the clutch hub are relative to each other. A damper device for stopping the rotation is also disclosed.

It should be noted that Patent Document 2 and Patent Document 3 also disclose that a torsion damper is provided between a pair of seat members in the coil spring. Thereby, a damper device having a partially increased torsional rigidity in the torsional characteristics of the disc plate and the clutch hub is disclosed.

Japanese Unexamined Patent Publication No. 2001-304341 Japanese Unexamined Patent Publication No. 7-293578 Japanese Unexamined Patent Publication No. 2014-181785

By the way, in general, in vehicles, there is a demand for miniaturization of the engine (so-called downsizing) for the purpose of improving fuel efficiency while maintaining the same power performance, but the miniaturization of the engine is aimed at while maintaining the power performance. Then, the vibration of the power transmitted from the engine naturally becomes large (for example, while the number of cylinders of the engine can be reduced, the vibration of the power becomes large because the same power is output with a small number of cylinders). .. Therefore, in order to realize the miniaturization of the engine, a low-rigidity damper device is required in order to absorb such vibration.

In order to realize a low-rigidity damper device, for example, a configuration in which the rigidity of the coil spring is lowered to increase the torsion angle can be adopted, but in this case, as the torsion angle gradually increases, the centrifugal force of the damper device itself also increases. Together, the coil spring compresses and deforms in the rotational direction (circumferential direction) and the radial direction. In such a damper device with low rigidity, as described in Patent Document 1, the protrusions provided on each of the pair of seat members function as stoppers, and the tips of the protrusions are brought into contact with each other to make a disk. When stopping the relative rotation between the plate and the clutch hub, it is necessary to design so that the protruding portion does not interfere with the inner peripheral portion of the coil spring. In order to meet this design requirement, it is necessary to provide a large clearance between the protrusion and the inner peripheral portion of the coil spring as compared with the conventional damper device (damper device without low rigidity). As a result, the tip of the protruding portion needs to have a shape having a small outer diameter extending in the radial direction thereof.

10 to 12 are diagrams schematically showing such design requirements. FIG. 10 is a schematic side view showing a general arrangement state of a pair of seat members and coil springs in a conventional damper device when the twist angle is 0 °. FIG. 11 is a schematic side view showing a state in which the tips of the protruding portions of the pair of seat members are in contact with each other to exert the stopper function in the conventional damper device having not been reduced in rigidity. FIG. 12 is a schematic side view showing a state in which the tips of the protruding portions of the pair of seat members are in contact with each other to exert the stopper function in the conventional low-rigidity damper device. Comparing FIGS. 11 and 12, since the damper device according to FIG. 12 has a larger allowable twist angle, the coil spring 5 according to FIG. 12 is greatly compressed and deformed. On the other hand, the tip portions 4a and 4b of the protrusions 4A and 4B according to FIG. 12 are set to allow a large compressive deformation of the coil spring 5, and the outer diameter r2 extending in the radial direction thereof is the protrusion of FIG. It is designed to be smaller (r2 <r1) than the outer diameter r1 of the tip portions 4a and 4b of the portions 4A and 4B. With this configuration, the radial outer clearance α3 and the radial inner clearance α4 between the tip portions 4a and 4b in FIG. 12 and the inner peripheral portion of the coil spring 5 are both the radial outer clearance α1 and the radial inner clearance in FIG. It is formed larger than the clearance α2, and interference between the protrusions 4A and 4B and the coil spring 5 is avoided (α1 <α3, α2 <α4).

However, as shown in FIG. 12, when the tips of the protruding portions of the pair of seat members are brought into contact with each other to provide the stopper function, the smaller the contact area between the tips, the lower the strength as the stopper function. There is a contradictory issue of getting rid of it. Further, in the future, as the demand for lower rigidity of the damper device becomes stronger, such a problem becomes more important.

On the other hand, Patent Document 1 is configured such that a part of the window portion provided on the disc plate is composed of a pair of seat members, a coil spring, and a float body, and the other window portions are provided with a stopper torque generating member. In the damper device disclosed in another embodiment, elastic members such as coil springs are not arranged in other windows due to the fact that low rigidity is not originally taken into consideration, and the torsional characteristics themselves are not provided. The setting is limited and it is not suitable for low-rigidity damper devices. In addition, since the elastic resin member is used as the stopper torque generating member, there is a problem that the stopper torque is not stable due to variations in the material characteristics of the elastic resin material, deterioration, and the like.

Since the torsion dampers described in Patent Documents 2 and 3 also use elastic materials that can be elastically deformed, variations in the material properties of the elastic materials and the same as in another embodiment of Patent Document 1 described above may occur. , The stopper torque of the torsion damper is not stable due to deterioration.

Therefore, various embodiments are provided to provide a low-rigidity damper device having a stopper function higher than that of the prior art while preventing interference between a seat member or the like and a coil spring.

The damper device according to one embodiment is accommodated between the first rotating body, the second rotating body that rotates relative to the first rotating body, and the first rotating body and the second rotating body, and is described as described above. The first rotating body and the elastic mechanism portion for elastically connecting the second rotating body in the rotation direction are provided, and the elastic mechanism portion transmits power between the first rotating body and the second rotating body. A seat member that abuts at least one of the first rotating body and the second rotating body, a coil spring whose both ends are supported by a pair of the seat members, and a coil spring are housed in the coil spring. A floating stopper that stops the relative rotation between the first rotating body and the second rotating body by moving in the rotation direction and the radial direction in the coil spring and sandwiching both ends between the pair of seat members. , Which have.

According to this configuration, the floating stopper housed in the coil spring can move not only in the rotational direction but also in the radial direction in the coil spring without being fixed or connected to any member. Therefore, it can move in the coil spring without interfering with the coil spring according to the centrifugal force of the damper device itself or the compression deformation of the coil spring. As a result, the thickness of the floating stopper (outer diameter extending in the radial direction) may be set to such that it can move in the radial direction in the coil spring, and is sufficient to reliably exert the stopper torque. It is possible to have a thickness. In other words, by using the floating stopper, the pair of seat members has a protruding portion having a tapered tip extending deep inside the coil spring as disclosed in the above-mentioned Patent Document 1. Since it is not necessary to provide it, it is possible to reliably exert the stopper torque.

Further, in the damper device according to one aspect, it is preferable that at least a part of the floating stopper is formed of an inelastic body.

With this configuration, the floating stopper can reliably exert a stable stopper torque without being affected by variations in material characteristics, deterioration, and the like.

Further, in the damper device according to one aspect, it is preferable that a part of the floating stopper is formed of at least an elastic body elastically deformed in the rotational direction, and the other part is formed of the inelastic body.

With this configuration, by combining the coil spring and the elastic body in the floating stopper, the variation of the torsional characteristics of the damper device can be increased (while enhancing the function of absorbing torque fluctuations). It is possible to reliably exert the stopper torque based on the inelastic body in the floating stopper.

Further, in the damper device according to one aspect, it is preferable that the floating stopper has a predetermined clearance with the inner peripheral portion of the coil spring and is housed in the coil spring.

With this configuration, the floating stopper can move in the radial direction in the coil spring without interfering with the coil spring. More specifically, in the initial state (state in which the twist angle is 0 °), the floating stopper is in contact with the inner peripheral portion on the radial inner side of the coil spring and between the inner peripheral portion on the radial outer side of the coil spring. When arranged so as to have a predetermined clearance, the floating stopper has a diameter of the coil spring according to the centrifugal force of the damper device and the compression deformation of the coil spring as the twist angle increases thereafter. It moves in the radial direction toward the inner peripheral portion on the outer side of the direction. In this way, the floating stopper itself moves in the radial direction, so that the position of the clearance between the floating stopper and the inner peripheral portion of the coil spring is appropriately moved according to the magnitude of the twist angle. , Interference with the coil spring can be avoided.

Further, in the damper device according to one aspect, the coil spring is wound outside the first coil spring that houses the floating stopper and the first coil spring, and houses the first coil spring inside. It is preferable to have a second coil spring.

With this configuration, the damper device can be further reduced in rigidity, so that the torque fluctuation absorption performance of the damper device can be further improved.

Further, in the damper device according to one aspect, the seat member abuts on the coil spring to support the coil spring, and the coil when the first rotating body and the second rotating body rotate relative to each other. The floating stopper when the seat surface that compresses the spring, the transmission surface that abuts on the first rotating body and the second rotating body and transmits power, and the first rotating body and the second rotating body rotate relative to each other. It is preferable to have a holding surface that abuts on and holds the coil spring, and a regulating surface that restricts the radial movement of the coil spring.

With this configuration, the torque input to the first rotating body can be transmitted to the second rotating body through the seat member and the coil spring. Further, since the seat member can come into contact with the floating stopper on the sandwiching surface while preventing interference between the seat member and the coil spring through the restricting surface, the floating stopper is sandwiched as a pair of the seat members. By doing so, it becomes possible to reliably exert the stopper torque of the floating stopper.

Further, in the damper device according to one aspect, the restricting surface is a first restricting surface that restricts the radial movement of the first coil spring and the radial movement of the second coil spring. It is preferable to have a second regulatory aspect to regulate.

With this configuration, both springs can be separated by a predetermined distance so that the first coil spring and the second coil spring do not interfere with each other. This makes it possible to further reduce the rigidity of the damper device and reliably improve the torque fluctuation absorption performance of the damper device.

Further, in the damper device according to one aspect, the first regulating surface is formed on a protruding portion having a top portion as the holding surface, and the protruding portion projects toward the inside of the first coil spring. It is preferable to form in.

With this configuration, the first regulating surface can surely regulate the movement of the first coil spring in the radial direction.

According to various embodiments, it is possible to provide a low-rigidity damper device having a stopper function higher than that of the prior art while preventing interference between a seat member or the like and a coil spring.

It is a schematic top view which shows typically the structure of the clutch disk which incorporated the damper device which concerns on one Embodiment. It is a schematic cross-sectional view schematically showing the structure of the clutch disk shown in FIG. 1 when viewed from the line AA. It is a schematic diagram which shows the operation of the clutch disk shown in FIG. 1 and FIG. It is a schematic side view which is the damper device which concerns on one Embodiment, and shows the seat member, the 1st coil spring, and the 2nd coil spring schematically. It is a schematic side view which shows the state which is the elastic mechanism part which concerns on one Embodiment, and the stopper torque is exerted by a floating stopper. FIG. 5 is a schematic side view schematically showing a state in which a stopper torque is exerted by a floating stopper having a form different from that of the floating stopper of FIG. 5, which is an elastic mechanism portion according to another embodiment. It is a figure which shows the torsional characteristic of the damper device which concerns on another embodiment. It is a schematic diagram explaining the operation performed between the engaging portion formed in the clutch hub and the corresponding seat. It is a schematic diagram which shows the relationship between each engaging member (each convex portion) and the corresponding sheet in the clutch disk which incorporated the damper device. It is a schematic side view which shows the general arrangement state of a pair of seat members and a coil spring in the case of a twist angle 0 ° in a conventional damper device. FIG. 3 is a schematic side view showing a state in which the tips of the protruding portions of a pair of seat members are in contact with each other to exert a stopper function in a conventional damper device that has not been reduced in rigidity. FIG. 3 is a schematic side view showing a state in which the tips of the protruding portions of a pair of seat members are in contact with each other to exert a stopper function in a conventional low-rigidity damper device.

Hereinafter, various embodiments of the present invention will be described with reference to the accompanying drawings. The same reference numerals are given to the common constituent requirements in the drawings. It should also be noted that the components represented in one drawing may be omitted in another drawing for convenience of explanation. Furthermore, it should be noted that the attached drawings are not always drawn to the correct scale.

1. 1. Configuration of Clutch Disc Incorporating a Damper Device An outline of the overall configuration of a clutch disk in which a damper device is incorporated according to an embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a schematic top view schematically showing a configuration of a clutch disk in which a damper device according to an embodiment is incorporated. FIG. 2 is a schematic cross-sectional view schematically showing the configuration of the clutch disk shown in FIG. 1 when viewed from the line AA.

The clutch disk 10 in which the damper device according to the present embodiment is incorporated is a component constituting the clutch device, and is sandwiched between a flywheel (not shown) and a pressure plate (not shown) to form an engine, a motor, or the like. The driving force from the driving source is transmitted to the transmission. Since the structure for sandwiching the clutch disc 10 between the flywheel and the pressure plate is known, detailed description thereof will be omitted.

The clutch disc 10 absorbs and attenuates torque vibration in the twisting direction by incorporating the damper device according to the present embodiment. As shown in FIGS. 1 and 2, the clutch disc 10 mainly includes a disc plate 100 as a first rotating body, a clutch hub 200 as a second rotating body, a thrust member 300, and a seat member 400. , Coil spring 500, facing 600, and floating stopper 1000.

1-1. Clutch hub 200
The clutch hub 200 is formed of, for example, a metal material and has a shape extending substantially annularly as a whole. The clutch hub 200 can be spline-coupled by inserting an input shaft of a transmission (not shown) into a through hole 204 formed in a substantially annular hub 202. Further, the clutch hub 200 has a substantially annular flange 206 extending radially from the hub 202. As for the clutch hub 200, it is possible to adopt a configuration in which the hub 202 and the flange 206 are integrated, or a configuration in which the hub 202 and the flange 206 are separated and a minute spring is arranged between them. ..

The flange 206 is formed with at least one notch along the circumferential direction on its outer periphery. In the present embodiment, as an example, the flange 206 is formed with four notches 206a, 206b, 206c, and 206d on the outer periphery thereof at intervals along the circumferential direction. As shown in FIG. 1, conceptually, when the clutch disc 10 is viewed from the upper surface and divided into four regions I, II, III, and IV each having a fan shape, the flange 206 is divided into regions I to IV. Correspondingly, the first notch 206a, the second notch 206b, the third notch 206c, and the fourth notch 206d are formed, respectively.

By forming such a notch, the flange 206 is associated with the region I and has an engaging portion on one end side (engaging portion on the first one end side) 208a ₁ and the other end side facing the engaging portion 208a 1. The engaging portion (the engaging portion on the other end side of the first end) 208a ₂ and the engaging portion on one end side (the engaging portion on the second one end side) 208b ₁ in association with the region II. It has an engaging portion on the other end side facing this (engaging portion on the second other end side) 208b ₂ . Similarly, although not shown in FIG. 1, the flange 206 corresponds to the region III and has an engaging portion on one end side (engaging portion on the third one end side) 208c ₁ and the other end facing the engaging portion 208c 1. It has an engaging portion on the side (engaging portion on the third other end side) 208c ₂ , and is associated with the region IV, and the engaging portion on one end side (engaging portion on the fourth integrated side) 208d ₁ . And an engaging portion on the other end side facing the same (engaging portion on the fourth other end side) 208d ₂ .

The engaging portions 208a ₁ , 208b ₁ , 208c ₁ , and 208d ₁ on each one end side can both have the same configuration, and the engaging portions 208a ₂ , 208b ₂ , 208c ₂ , and 208d on the other end side, respectively. ₂ can both have the same configuration. The engaging portions 208a ₁ , 208b ₁ , 208c ₁ , and 208d ₁ on each one end side may have a symmetrical configuration with the engaging portions 208a ₂ , 208b ₂ , 208c ₂ , and 208d ₂ on the other end side, respectively. can. The specific shapes of the engaging portion on one end side and the engaging portion on the other end side will be described later.

1-2. Disc plate 100
The disc plate 100 is formed of, for example, a metal material, and is provided on both sides of the clutch hub 200 so as to be coaxial with and relative to the clutch hub 200. The disc plate 100 includes a first disc plate 100A and a second disc plate 100B provided on both sides of the clutch hub 200 in the axial direction. The first disc plate 100A and the second disc plate 100B are housed with a seat member 400, a coil spring 500, a floating stopper 1000 and a clutch hub 200 (flange 206) sandwiched between them, and their outer circumferences thereof. It may be combined by a plurality of rivets R or the like in the vicinity.

The first disc plate 100A and the second disc plate 100B cooperate with each other to accommodate the seat member 400, the coil spring 500, and the floating stopper 1000 in association with each of the regions I to IV (FIG. In the example shown in 1, the disc plate 100 has an axially bulging shape so as to form four accommodation regions). Each accommodating area extends substantially linearly or substantially arcuately along the circumferential direction of the disc plate 100 to accommodate the coil springs 500 extending along the circumferential direction of the disc plate 100.

More specifically with reference to FIGS. 1 and 2, the first disc plate 100A and the second disc plate 100B correspond to the regions I to IV, respectively, and the first accommodating region 102a extending along the circumferential direction. , A second accommodating area 102b, a third accommodating area 102c, and a fourth accommodating area 102d. As shown in FIG. 1, the first accommodation area 102a is the above-mentioned first notch 206a, the second accommodation area 102b is the above-mentioned second notch 206b, and the third accommodation area 102c is the above-mentioned third cut. The notch 206c and the fourth accommodation region 102d are formed so as to correspond to the above-mentioned fourth notch 206d, respectively.

Focusing on the region I, the first disc plate 100A and the second disc plate 100B have one end surface (first end surface) 104a ₁ and the other end surface (first) facing the first end surface (first end surface) 104a 1 as a side wall surrounding the first accommodation area 102a. The other end surface of) 104a ₂ and the like. These first end surfaces 104a ₁ and 104a ₂ extend along the axial direction of the disc plate 100, for example.

However, the first end surface 104a ₁ and the second end surface 104a 1 formed by the first disk plate 100A so that the engaging portion 208a ₁ on the first end side can enter the inside of the first accommodation area 102a. A gap G (not shown) for receiving the engaging portion 208a ₁ on the first end side is formed between the first end surface 104a ₁ formed by the disc plate 100B. Further, the first other end surface 104a ₂ and the first end surface 104a 2 formed by the first disk plate 100A so that the engaging portion 208a ₂ on the other end side of the first end can enter the inside of the first accommodation area 102a. A gap G (not shown) for receiving the engaging portion 208a ₂ on the first other end side is similarly formed between the first other end surface 104a ₂ formed by the two disc plates 100B.

Similar to the region I, the first disc plate 100A and the second disc plate 100B face each other with the second one end surface 104b ₁ as shown in FIG. 1, even if they are associated with the regions II to IV. It has a second end surface 104b ₂ and a third end surface 104c ₁ (not shown) and a third end surface 104c ₂ facing it, and a fourth end surface 104d (not shown). It has ₁ and a fourth other end surface 104d ₂ facing the same. The second end surface 104b ₁ to the fourth end surface 104d ₁ also have a first one in order to receive the engagement portion 208b ₁ on the second end side to the engagement portion 208d ₁ on the fourth end side, respectively. The above-mentioned gap G (not shown) is similarly formed on the one end surface 104a ₁ , and the second other end surface 104b ₂ to the fourth other end surface 104d ₂ also have the engaging portion 208b ₂ on the second other end side, respectively. In order to receive the engaging portion 208d ₂ on the other end side of the fourth end, the above-mentioned gap G (not shown) is similarly formed for the first other end surface 104a ₂ .

Further, as an option, the first disc plate 100A and the second disc plate 100B have a first opening 106a, a first opening 106a, in order to partially expose each of the first accommodation area 102a to the fourth accommodation area 102d to the outside. It can have two openings 106b, a third opening 106c, and a fourth opening 106d.

1-3. Thrust member 300
The thrust member 300 is a washer-shaped member made of, for example, resin, which is provided between the contact surface between the clutch hub 200 and the disc plate 100. The thrust member 300 includes a first thrust member 300A provided between the clutch hub 200 and the first disc plate 100A, and a second thrust member 300B provided between the clutch hub 200 and the second disc plate 100B. , Can be included.

1-4. Seat member 400
In the embodiment shown in FIG. 1, as an example, four accommodating areas, that is, first accommodating areas 102a to fourth accommodating areas 102d are formed on the disk plate 100, and therefore, each of these four accommodating areas is formed. Contains the coil spring 500. In FIG. 1, as an example, as a coil spring 500, a first coil spring 500A and a second coil spring 500B wound outside the first coil spring are accommodated (to the extent of low rigidity required for a damper device). (Depending on whether the coil spring 500 is single or double), both ends of the first coil spring 500A and the second coil spring 500B are supported by a pair of seat members 400.

More specifically, focusing on the region I, the first accommodation region 102a and the first notch 206a have a seat on one end side (the first) that supports one end of the first coil spring 500A (and the second coil spring 500B). The sheet on one end side of 1) 400a ₁ and the sheet on the other end side supporting the other end of the first coil spring 500A (and the second coil spring 500B) 400a ₂ on the other end side are both. The first coil spring 500A (and the second coil spring 500B) is arranged so as to sandwich the first coil spring 500A (and the second coil spring 500B).

Next, the details of the seat member 400 will be described with reference to FIGS. 3 to 5. FIG. 3 is a schematic view showing the operation of the clutch disc shown in FIGS. 1 and 2. FIG. 4 is a schematic side view schematically showing a seat member, a first coil spring, and a second coil spring in the damper device according to the embodiment. FIG. 5 is a schematic side view schematically showing a state in which the stopper torque is exerted by the floating stopper in the elastic mechanism portion according to the embodiment. The seat 400a ₁ on the first one end side and the seat 400a ₂ on the other end side of the first end are formed of, for example, a resin material, and the seat surface 410 supporting one end of the first coil spring 500A (and the second coil spring 500B). A base portion 402 including the base portion 402 and a substantially trapezoidal or substantially truncated cone-shaped protrusion 404 coupled to the base portion 402 can be mainly included. The protruding portion 404 protrudes toward the inside of the first coil spring 500A. However, unlike the prior art disclosed in Patent Document 1 described above, the protrusion 404 according to the embodiment does not need to extend deep inside the first coil spring 500A, and the first coil spring 500A will be described later. It suffices as long as it protrudes to the extent that the regulation surface 414 can be formed.

As shown in FIGS. 3 and 5, the sheet 400a ₁ on the first end side and the sheet 400a ₂ on the other end side of the first end act as a pair of seat members 400, and the disc plate 100 and the clutch hub 200 are relative to each other. When rotated, the first coil spring 500A (and the second coil spring 500B) is compressed, and finally, it is formed so as to be in surface contact (contact) with the side surface 1010 of the floating stopper 1000. That is, in order to realize such surface contact, a holding surface 412 is formed on the top of each of the protruding portions 404 of the sheet 400a ₁ on the first one end side and the sheet 400a ₂ on the first other end side.

Further, as shown in FIG. 4, in the vicinity of the joint portion 404a with the base portion 402 in each of the protruding portions 404 of the sheet 400a ₁ on the first one end side and the sheet 400a ₂ on the first other end side, the first In order to regulate that the first coil spring 500A receives centrifugal force and moves outward in the radial direction of the clutch disc 10 (or the disc plate 100) by abutting on the outer periphery of one end of the one coil spring 500A. The first regulatory surface 414 is formed. The first regulating surface 414 extends in a direction substantially perpendicular to the extending direction of the first coil spring 500A in order to surely restrict the lateral movement of the first coil spring 500A in the radial direction, and the length thereof is the first. One coil spring 500A preferably has about 1 to 2 turns, and more preferably about 1.5 turns. This makes it possible to prevent interference between the seat member 400 (the seat 400a ₁ on the first one end side and the seat 400a ₂ on the first other end side) and the first coil spring 500A.

When the coil spring 500 adopts a double coil spring structure including a first coil spring 500A and a second coil spring 500B as in one embodiment, the base 402 has a second coil spring 500B as a clutch disk 10. A substantially annular holding portion 406 may be included to form a second regulatory surface 415 for restricting the radial outward movement of (or the disc plate 100). The second regulating surface 415 extends in a direction substantially perpendicular to the extending direction of the second coil spring 500B in order to surely restrict the lateral movement of the second coil spring 500B in the radial direction, and the length thereof is the first. The number of two coil springs 500B is preferably about 1 to 2 turns, and more preferably about 1.5 turns.

As shown in FIG. 4, the distance between the outer circumference of the first coil spring 500A under centrifugal force and the inner circumference of the second coil spring 500B in the same state (specifically, for example). The size of the protrusion 404 and / or the holding portion 406 can be determined so that the radial outer spacing G1 and the radial inner spacing G2) are greater than or equal to a predetermined value. For example, when various sizes are adopted for each of the projecting portion 404 and the holding portion 406, the first coil spring 500A and the second coil spring 500B may be the clutch disc 10 (or the disc plate 100) depending on the magnitude of the centrifugal force. ), We collected experimental values on how much it moves outward in the radial direction (how much the distance between both coil springs is), and based on such experimental values, in a state where centrifugal force is applied. The size of the protrusion 404 and / or the holding portion 406 may be set so that the distance between the coil springs can be maintained above a predetermined value. As a result, for example, the first coil spring 500A subjected to the centrifugal force moves radially outward and comes into contact with and interferes with the second coil spring 500B, thereby reliably suppressing a situation in which sliding between the two occurs. be able to.

Further, the base portion 402 has a transmission surface 416 that abuts on the disc plate 100 and the clutch hub 200 to transmit the driving force on the side opposite to the protruding portion 404, and has a recess 408 on the transmission surface 416. be able to.

The seat 400a ₁ on the first end side is urged by the coil spring 500 (first coil spring 500A and / or the second coil spring 500B) in a direction away from the seat 400a ₂ on the first other end side. Is supported by the first end surface 104a ₁ of the disc plate 100. In this state, the concave portion 408 of the sheet 400a ₁ on the first one end side engages with the engaging portion (convex portion) 208a ₁ on the first one end side.

The seat 400a ₂ on the other end side of the first end is urged by the coil spring 500 (first coil spring 500A and / or the second coil spring 500B) in a direction away from the seat 400a ₁ on the first one end side. Therefore, it is supported by the first other end surface 104a ₂ of the disc plate 100. In this state, the concave portion 408 of the sheet 400a ₂ on the other end side of the first end engages with the engaging portion (convex portion) 208a ₂ on the other end side of the first end. The details of the operation of the seat 400a ₁ on the first one end side and the seat 400a ₂ on the other end side of the first end caused by the relative rotation of the disc plate 100 and the clutch hub 200 will be described later.

As described above, attention has been paid to the region I, but also for the region II, referring to FIG. 1, one end of the first coil spring 500A (and the second coil spring 500B) is provided in the second accommodating region 102b and the second notch 206b. One end side sheet to support (second one end side sheet) 400b ₁ , and the other end side sheet to support the other end of the first coil spring 500A (and the second coil spring 500B) (second other end side) (Sheet) 400b ₂ is arranged so as to sandwich the first coil spring 500A (and the second coil spring 500B) between the two.

The sheet 400b ₁ on the second one end side and the sheet 400b ₂ on the second other end side have the same configuration as the above-mentioned sheet 400a ₁ on the first one end side (the first other end side is the sheet 400a ₂ ). Can be.

The sheet 400c ₁ on the third one end side and the sheet 400c ₂ on the third other end side provided in association with the region III, and the sheet 400d ₁ and the third on the fourth end side provided in association with the region IV. Since the same applies to the sheet 400d ₂ on the other end side of No. 4, the detailed description thereof will be omitted.

1-5. Coil spring 500
In the embodiment shown in FIGS. 1, 2, 4, and 5, the coil spring 500 is wound outside the first coil spring 500A and the first coil spring 500A as described above (first coil spring). It is composed of a second coil spring 500B (which internally accommodates 500A). As a result, it exhibits a double coil spring structure of the inner first coil spring 500A and the outer second coil spring 500B, and has a configuration pursuing low rigidity as a damper device. As described above, a single coil spring structure in which the second coil spring 500B is omitted may be adopted depending on the low rigidity performance required for the damper device.

As the first coil spring 500A and the second coil spring 500B, commonly used metal ones can be used, and it is preferable to use an elliptical coil having an elliptical shape as the cross section thereof, as shown in FIG. .. Further, the first coil spring 500A and the second coil spring 500B are wound in opposite directions (for example, the first coil spring 500A is wound clockwise so that they do not bite each other, and the second coil spring 500A is second. It is preferable to wind the coil spring 500B counterclockwise). For the same reason, the winding pitch (so-called line-to-line pitch) of the first coil spring 500A (inner coil spring) is set smaller than that of the second coil spring 500B (outer coil spring). Is preferable. The load sharing between the first coil spring 500A and the second coil spring 500B may be appropriately set by a person skilled in the art, but the load load of the second coil spring 500B is larger than that of the first coil spring 500A. Is preferable.

The configuration in which the first coil spring 500A and the second coil spring 500B are supported by the seat member 400 is as described above. In short, both coil springs are supported at both ends by the seat surface 410 of the seat member 400 (the seat 400a ₁ on the first one end side and the seat 400a ₂ on the first other end side), and the disc plate 100 and the clutch hub. As the seat member 400 moves in the circumferential direction in response to the relative rotation with the 200, both coil springs are compressed and deformed while being pushed by the seat surface 410.

The first coil spring 500A houses a floating stopper 1000, which will be described later, inside the first coil spring 500A.

1-6. Facing 600
The facing 600 can include an annular first facing 600A and a second facing 600B, each of which is made of a wear resistant material. The first facing 600A and the second facing 600B are attached to the disc plate 100 by a known method so that their inner circumferences extend along the outer circumference of the disc plate 100. These first facing 600A and second facing 600B are sandwiched between a flywheel (not shown) and a pressure plate (not shown) as described above.

1-7-1. Floating stopper 1000
As described above, in the embodiment shown in FIG. 1, the floating stopper 1000 is housed inside the first coil spring 500A. The floating stopper 1000 is made of a lightweight and highly wear-resistant material so that the first coil spring 500A can be easily moved in the first coil spring 500A while exhibiting a stable stopper torque without damaging the first coil spring 500A. It is preferably formed, and an inelastic body such as a hard resin or a glass fiber can be used.

The floating stopper 1000 is arranged in the first coil spring 500A so as to be able to freely move in the rotational direction and the radial direction of the disc plate 100 (or the clutch hub 200). Specifically, as shown in FIG. 1, the floating stopper 1000 is not fixed to any member and has a predetermined clearance CL between the floating stopper 1000 and the inner peripheral portion of the first coil spring 500A. Moreover, at a twist angle of 0 ° (state shown in FIG. 1), the first coil spring is in a state where it does not abut on the respective holding surfaces 412 of the sheet 400a ₁ on the first one end side and the sheet 400a ₂ on the first other end side. It is placed in 500A. After that, when the disc plate 100 and the clutch hub 200 rotate relative to each other and the twist angle becomes large, finally, as shown in FIG. 5, the sheet 400a ₁ on the first one end side and the first other end side By being sandwiched between the sandwiching surfaces 412 of the seat 400a ₂ , the stopper torque is exerted to stop the relative rotation.

The shape of the floating stopper 1000 is not particularly limited, but it is preferably, for example, substantially cylindrical or substantially prismatic as a whole so as not to be fitted between the winding pitches of the first coil spring 500A. Further, in the floating stopper 1000, as shown in FIG. 5, the side surface 1010 having an area larger than the area of the holding surface 412 in the seat member 400 so that the stopper torque can be stably exerted over a long period of time. It is preferable to have.

On the other hand, the thickness of the floating stopper 1000 (the outer diameter extending in the radial direction of the clutch disc 10 or the disc plate 100) is set to be smaller than the inner diameter of the first coil spring 500A. As a result, a predetermined clearance CL can be provided between the inner peripheral portion of the first coil spring 500A, so that the floating stopper 1000 can freely move in the radial direction in the first coil spring 500A. It becomes. The details of the operation of the floating stopper 1000 caused by the relative rotation of the disc plate 100 and the clutch hub 200 will be described later.

The length of the floating stopper 1000 (the length extending in parallel with the extending direction of the first coil spring 500A) can be appropriately set according to the required size of the twist angle and the rigidity of the first coil spring 500A. Needless to say, the length is set smaller than the length of the first coil spring 500A.

The floating stopper 1000 may be arranged in all of the above-mentioned regions I to IV, or may be arranged only in two places, for example, region I and region III, depending on the stopper torque exerted by the floating stopper 1000. Further, the floating stopper 1000 according to one embodiment is arranged at two locations of region I and region III, and the floating stopper 1000 according to another embodiment (modification example) described later is provided at two locations of region II and region IV. It may be configured to provide.

Among the clutch discs 10 having the above configuration, the seat member 400, the coil spring 500, the floating stopper 1000, the disc plate 100 (of which the configuration related to the seat member 400 and the coil spring 500), and the clutch hub 200 (of which). Of these, the configuration related to the seat member 400 and the coil spring 500) can be regarded as a damper device. Further, among those that can be regarded as a damper device, the seat member 400, the coil spring 500, and the floating stopper 1000 can be regarded as an elastic mechanism portion.

1-7-2. Modification example of the floating stopper 1000 By the way, as described above, the floating stopper 1000 is required to be lightweight so that it can be easily moved in the first coil spring 500A. Therefore, in another embodiment of the floating stopper 1000, as shown in FIG. 6A, the floating stopper 1000 may be provided with a groove portion 1100 extending in the thickness direction or the length direction. This makes it possible to reduce the weight of the floating stopper 1000. For convenience of drawing, it should be added that the floating stopper 1000 of one embodiment shown in FIG. 2 indicates the other embodiment to which the groove portion 1100 is attached.

Further, in the floating stopper 1000, as shown in FIGS. 6 (b) and 6 (c), it may be a combined body of an inelastic body and an elastic body. More specifically, in the floating stopper 1000 in FIG. 6B, an elastic body 1250 having an elastic force such as rubber and inelastic bodies 1200a and 1200b are coupled to each other. The inelastic body 1200a has a shape that covers one side surface of the elastic body 1250 in a substantially U shape in cross section, and the inelastic body 1200b has a shape that similarly covers the other side surface of the elastic body 1250 in a substantially U shape in cross section. As a result, both are configured to sandwich the elastic body 1250. In the inelastic body 1200a and the inelastic body 1200b, when the twist angle is equal to or less than a predetermined value (including the case of 0 °), the end portion 1201 of the inelastic body 1200a and the end portion 1202 of the inelastic body 1200b are in contact with each other. It is formed so as not to. After that, when the twist angle becomes large, the inelastic body 1200a and the inelastic body 1200b elastically deform the elastic body 1250, and finally the end portions 1201 and the end portions 1202 come into contact with each other to exert a stopper torque.

In the floating stopper 1000 in FIG. 6C, the substantially convex inelastic bodies 1300a and 1300b are configured to sandwich the elastic body 1350 between them. Similar to the floating stopper 1000 according to FIG. 6B, in the floating stopper 1000 according to FIG. 6C, the inelastic body 1300a and the inelastic body 1300b have a twist angle of a predetermined value or less (0 °). The end portion 1301 of the inelastic body 1300a and the end portion 1302 of the inelastic body 1300b are formed so as not to come into contact with each other. After that, when the twist angle becomes large, the inelastic body 1300a and the inelastic body 1300b elastically deform the elastic body 1350, and finally the end portions 1301 and the end portions 1302 come into contact with each other to exert a stopper torque.

By the way, in the floating stopper 1000 according to another embodiment as shown in FIGS. 6 (b) and 6 (c), the coil spring 500 (first) while reliably exerting a stable stopper torque by the inelastic body. In addition to the torque fluctuation absorption by the coil spring 500A and the double coil spring structure including the second coil spring 500B), the torque fluctuation is also absorbed by the elastic body (elastic body 1250 or elastic body 1350) of the floating stopper 1000. Therefore, it is possible to increase the variation of the torsional characteristics of the damper device as a whole (strengthen the damping function of torque fluctuation).

The floating stopper 1000 according to another embodiment shown in FIGS. 6 (b) and 6 (c) is, for example, arranged in the regions II and IV of the above-mentioned regions I to IV, and in the regions I and III. It can be mixed with the floating stopper 1000 according to the embodiment which does not include an elastic body and used in the damper device.

Next, the floating stopper 1000 according to another embodiment shown in FIGS. 6 (b) and 6 (c) is arranged in the region II and the region IV, and one embodiment or another is shown in FIG. 5 or FIG. 6 (a). FIG. 7 shows the torsional characteristics of the damper device in which the floating stopper 1000 according to the embodiment is arranged in the region I and the region III. The dotted line in FIG. 7 shows the torsional characteristics of a conventional damper device that is not low-rigidity (for example, the damper device according to Patent Document 1 and provided with a float body having an elastic function), and the solid line is a diagram. 6 (b) and FIG. 6 (c) show the torsional characteristics of the low-rigidity damper device including the floating stopper 1000 according to another embodiment. As shown in FIG. 7, since the embodiment according to the present application has a lower rigidity than the conventional one, it is possible to absorb the torque fluctuation at a large twist angle. Further, in the region of torque W1, the torque fluctuation is absorbed by the coil spring 500 (including the double coil spring structure including the first coil spring 500A and the second coil spring 500B), and in the region of torque W2, the coil spring. In addition to the torque fluctuation absorption by the 500, the torque fluctuation can be absorbed by the elastic body (elastic body 1250 or elastic body 1350) of the floating stopper 1000.

2. 2. Operation of Clutch Disc Incorporating a Damper Device The operation of the clutch disc 10 having the above configuration will be described with reference to FIGS. 1 to 3.

FIG. 3A shows a state in which the driving force is not transmitted to the clutch disc 10 from a drive source such as an engine, that is, a state in which the torque transmitted to the clutch disc 10 is 0. As shown in FIG. 3A, the seat 400a ₁ on the first end side provided in association with the region I is urged by the coil spring 500 (the first coil spring 500A and the second coil spring 500B). As a result, the base portion 402 is supported by the one end surface 104a ₁ of the disc plate 100, and the concave portion 408 formed in the base portion 402 engages with the engaging portion (convex portion) 208a ₁ on the first one end side. do. As described above, the engaging portion (convex portion) 208a ₁ on the first one end side is provided between the one end surface 104a ₁ of the first disc plate 100A and the one end surface 104a ₁ of the second disc plate 100B. It is possible to enter the inside of the first accommodation region 102a through the gap G (not shown) and engage with the recess 408.

Similarly, the seat 400a ₂ on the other end side of the first end, which is provided in association with the region I, is also urged by the coil spring 500 (the first coil spring 500A and the second coil spring 500B) to form a base thereof. The 402 is supported by the other end surface 104a ₂ of the disc plate 100, and the concave portion 408 formed in the base portion 402 engages with the first other end side engaging portion (convex portion) 208a ₂ .

The floating stopper 1000 is arranged inside the first coil spring 500A in a state of being separated from the holding surface 412 of the seat 400a ₁ on the first one end side and the holding surface 412 of the seat 400a ₂ on the first other end side. Will be done. In this case, the floating stopper 1000 has an inner peripheral portion of the first coil spring 500A and a predetermined clearance CL in the radial direction (toward the outer side in the radial direction).
The above operation regarding the region I also applies to the regions II to IV. Hereinafter, the operation described with respect to the region I also applies to the regions II to IV in the same manner. Therefore, only the region I will be described, and the detailed description of the regions II to IV will be omitted.

Next, a state in which the torque transmitted to the clutch disc 10 is positive (for example, a state during acceleration in a vehicle) is shown in FIG. 3 (b). As shown in FIG. 3B, the disc plate 100 rotates counterclockwise on paper relative to the clutch hub 200. As a result, the base portion 402 of the first other end side seat 400a ₂ is pressed toward the first one end side seat 400a ₁ by the first other end surface 104a ₂ , so that the first coil spring 500A And, against the second coil spring 500B, the engagement portion (convex portion) 208a ₂ on the other end side of the first end is separated from the seat 400a ₁ on the first end side. Since the clutch hub 200 is relatively stationary, the seat 400a ₁ on the first end side supported by the engaging portion (convex portion) 208a ₁ on the first end side also does not slide. Therefore, the first coil spring 500A and the second coil spring 500B are compressionally deformed, and the one end surface 104a ₁ of the disc plate 100 cancels the support for the seat 400a ₁ (base 402) on the first one end side. , Separated from the sheet 400a ₁ on the first end side. After that, the first coil spring 500A and the second coil spring 500B extend to return to the original state, so that the seat 400a ₁ (base 402) on the first one end side urged by both springs becomes the first. The engaging portion (convex portion) 208a ₁ on one end side of 1 is pressed in the counterclockwise direction on the paper surface. As a result, the clutch hub 200 rotates counterclockwise, and by extension, the input shaft of the transmission (not shown) rotates.

In this case, by sliding the sheet 400a ₂ on the other end side so as to approach the sheet 400a ₁ on the first one end side, the holding surface 412 on the sheet 400a ₂ on the first other end side floats. It abuts on the side surface 1010 of the stopper 1000. After that, when the relative rotation further progresses and the twist angle becomes large, the floating stopper 1000 is pushed by the holding surface 412 on the seat 400a ₂ on the other end side of the first end, so as to be pushed in the circumferential direction in the first coil spring 500A. After moving, as shown in FIG. 5 and the like, the sheet 400a ₁ on the first end side also comes into contact with the holding surface 412 on the sheet 400a 1, and the sheet 400a ₁ on the first end side and the other end of the first end. It is sandwiched between the seats 400a ₂ on the side and exerts a stopper torque.

As the relative rotation between the disc plate 100 and the clutch hub 200 progresses as described above, a centrifugal force is applied to the floating stopper 1000, and as a result, the floating stopper 1000 is provided in FIG. 3A. In the clearance CL, it moves outward in the radial direction. The floating stopper 1000 in FIG. 3B moves from the state of FIG. 3A to the outside in the radial direction, thereby allowing a clearance inward in the radial direction between the floating stopper 1000 and the inner peripheral portion of the first coil spring 500A. CLa is formed, and a clearance CLb is formed on the outer side in the radial direction. The sum of CLa and CLb is CL (CLa + CLb = CL). In this way, the floating stopper 1000 can be moved radially outward by the action of centrifugal force (in some cases, the action of elastic deformation of the first coil spring 500A), so that when the first coil spring 500A is elastically deformed. , The floating stopper 1000 and the first coil spring 500A do not interfere with each other. That is, by moving the floating stopper 1000 itself in the radial direction in a timely manner, the position of the clearance CL between the floating stopper 1000 and the inner peripheral portion of the first coil spring 500A is moved or dispersed in a timely manner according to the size of the twist angle. By distributing (CL is dispersed in CLa and CLb), it is possible to avoid interference between the floating stopper 1000 and the first coil spring 500A.

As described above, the thickness of the floating stopper 1000 is set to be smaller than the inner diameter of the first coil spring 500A. More specifically, since the first coil spring 500A is also affected by centrifugal force or the like and elastically deforms in a curved shape rather than linearly, the thickness of the floating stopper 1000 is due to the elastic deformation of the first coil spring 500A. The thickness that does not interfere with the first coil spring 500A can be set in consideration of such a curvature (particularly, the maximum curvature when the twist angle is the largest). Therefore, in other words, it is preferable that the thickness of the floating stopper 1000 is the maximum thickness that can be moved in the radial direction in the first coil spring 500A and that takes into consideration the elastic deformation direction of the first coil spring 500A. .. This makes it possible to reliably exert the stopper torque.

Next, a state in which the torque transmitted to the clutch disc 10 is negative (for example, a state during deceleration in a vehicle) is shown in FIG. 3 (c). As shown in FIG. 3C, the disc plate 100 rotates clockwise on the paper relative to the clutch hub 200. As a result, the base portion 402 of the seat 400a ₁ on the first end side is pressed toward the seat 400a ₂ on the other end side by the first end surface 104a ₁ , so that the first coil spring 500A is used. And, against the second coil spring 500B, it separates from the engaging portion (convex portion) 208a ₁ on the first one end side and approaches the seat 400a ₂ on the first other end side. Since the clutch hub 200 rotates counterclockwise with respect to the disc plate 100, the seat 400a ₂ on the first other end side supported by the engaging portion (convex portion) 208a ₂ on the first other end side. Does not slide. Therefore, the first coil spring 500A and the second coil spring 500B are compressionally deformed, and the other end surface 104a ₂ of the disc plate 100 cancels the support for the seat 400a ₂ (base 402) on the first other end side. It is separated from the sheet 400a ₂ on the other end side of the first. After that, the first coil spring 500A and the second coil spring 500B extend to return to the original state, so that the first other end side seat 400a ₂ (base 402) urged by both springs is released. The engaging portion (convex portion) 208a ₂ on the other end side of the first end is pressed in the clockwise direction on the paper surface. As a result, the clutch hub 200 that rotates counterclockwise decelerates, and eventually the input shaft of the transmission (not shown) decelerates.

In this case, by sliding the sheet 400a ₁ on the first end side closer to the sheet 400a ₂ on the other end side, the holding surface 412 on the sheet 400a ₁ on the first end side becomes a floating stopper. It abuts on the side surface 1010 of 1000. After that, when the relative rotation further progresses and the twist angle becomes large, the floating stopper 1000 moves in the circumferential direction in the first coil spring 500A so as to be pushed by the holding surface 412 in the seat 400a ₁ on the first one end side. Finally, as shown in FIG. 5 and the like, the sheet 400a ₁ on the first one end side also comes into contact with the holding surface 412 on the sheet 400a 1, and the sheet 400a ₁ on the first one end side and the other end side of the first end. It is sandwiched between the seats 400a ₂ and exerts a stopper torque. Since the movement of the floating stopper 1000 and the clearance CL are the same as those described above based on FIG. 3 (b), the description thereof will be omitted here. However, the clearance CLc in FIG. 3C corresponds to the clearance CLa in FIG. 3B, and the clearance CLd in FIG. 3C corresponds to the clearance CLb in FIG. 3B.

As described above, the driving force from the drive source such as the engine is the disc plate 100, the seat on one end side (for example, the seat 400a ₁ on the one end side), and each in both acceleration and deceleration states. Sequentially with respect to the seat on the other end side (for example, the seat 400a ₂ on the other end side), the coil spring 500 (first coil spring 500A and the second coil spring 500B), the clutch hub 200, and the input shaft of the transmission (not shown). Be transmitted.

3. 3. Operations taken between the engaging portion of the clutch hub 200 and the corresponding seat FIGS. 8 (a) to 8 (c) show the space between the engaging portion formed in the clutch hub 200 and the corresponding seat. It is a schematic diagram explaining the operation performed in.

As shown in FIG. 8A, each engaging portion (convex portion) formed on the flange 206 of the clutch hub 200 (in FIGS. 8A to 8C, the convex portion 208a ₁ is exemplified. However, the same applies to the other protrusions.) Can be formed to have the shape described below.

The seat 400a ₁ on the first end side provided corresponding to the convex portion 208a ₁ has a coil spring 500 (first coil spring 500A and a first coil spring 500A) arranged between the seat 400a ₂ on the other end side of the first end. When the 2-coil spring 500B) receives a centrifugal force toward the radial outer side of the clutch disc 10, it is rotated counterclockwise on the paper surface with the center O as the central axis. Here, the center O is the convex portion 208a ₁ (or the convex portion 208a 1) on the one end side that comes into contact with the convex portion 208a 1 on the one end side as the rotation center when the sheet 400a ₁ on the first one end side receives centrifugal force and rotates with respect to the convex portion 208a ₁ on the one end side. It is the outer edge of the convex portion 208a ₂ to the convex portion 208a ₄ ).

Here, the line connecting the center O and the rotation center of the clutch disc 10 (clutch hub 200 or disc plate 100) is referred to as a “boundary line L”.

In the present embodiment, the convex portion 208a ₁ extends to the side where the first other end side sheet 400a ₂ (opposing the first one end side sheet 400a ₁ ) exists with respect to the boundary line L. That is, it is configured to extend to both sides along the circumferential direction of the clutch disk 10 with respect to the boundary line L. In other words, the first contact point between the convex portion 208a ₁ and the side wall 408A (the side wall along the arc concentric with the rotation center of the clutch disk 10) surrounding the concave portion 408 of the sheet 400a ₁ on the first end side. The convex portion 208a ₁ is formed so that C1 exists on the side where the sheet 400a ₂ on the other end side of the first end side exists with respect to the boundary line L (corresponding to the normal line with respect to the arc passing through the center O). As a result, even if the sheet 400a ₁ on the first end side receives centrifugal force and tries to rotate counterclockwise on the paper surface around the center O, a part of FIGS. 8 (b) and 8 (b). As shown in FIG. 8 (c), which is an enlarged view of the above, the convex portion 208a ₁ abuts on the side wall 408A surrounding the concave portion 408 of the sheet 400a ₁ on the first one end side at the first contact point C1 and bites into the side wall 408A. Therefore, the sheet 400a ₁ on the first end side cannot rotate any more. As a result, the base portion 402 (particularly the holding portion 406) of the sheet 400a ₁ on the first end side can be rotated in the radial direction of the clutch disk 10. By protruding to the outside, it is possible to suppress a situation in which the disc plate 100 (the side wall surrounding the first accommodating area 102a in the disc plate 100) is in contact with the disc plate 100 and is worn.

On the other hand, tentatively, the convex portion 208a ₁ does not extend to the side where the first other end side sheet 400a ₂ (opposing the first one end side sheet 400a ₁ ) exists with respect to the boundary line L. In the case, that is, when the boundary line L extends only to the side opposite to the sheet 400a ₂ on the other end side of the first end, the convex portion 208a ₁ extends to the concave portion 408 of the sheet 400a ₁ on the first one end side. Since it does not bite into the side wall 408A surrounding the first one end side, the sheet 400a ₁ on the first one end side can be further rotated. As a result, the base portion 402 (particularly the holding portion 406) of the sheet 400a ₁ on the first one end side protrudes radially outward of the clutch disk 10, whereby the side wall surrounding the first accommodating area 102a in the disc plate 100 (in the side wall). There is a possibility that it will come into contact with and wear.

As described above, in the clutch disc 10 in which the damper device according to the present embodiment is incorporated, the convex portion 208a ₁ (or the convex portion 208a ₂ ) is along the circumferential direction of the clutch disc 10 with respect to the boundary line L. It is formed so as to exist on both sides. As a result, the convex portion 208a ₁ bites into the side wall 408A surrounding the concave portion 408 formed in the corresponding sheet 400a ₁ on the one end side (or the sheet 400a ₂ on the other end side of the first end). It is possible to prevent the corresponding sheet 400a ₁ on the one end side (or the sheet 400a ₂ on the other end side) from rotating further due to centrifugal force.

9 (a) and 9 (b) are schematic views showing the relationship between each engaging member (each convex portion) and the corresponding sheet in the clutch disc incorporating the damper device according to another embodiment. ..

As shown in FIG. 9A, the sheet 400a ₁ on the first one end side can have a corner portion 408B at the opening of the recess 408. The corner portion 408B is the second with respect to the engaging portion (convex portion) 208a ₁ on the one end side when the sheet 400a ₁ on the first end side tries to rotate counterclockwise on the paper surface around the center O. At the contact point C2 of the above, it functions to abut and regulate the rotation of the sheet 400a ₁ on the first one end side.

As shown in FIG. 9B, the gap δ between the convex portion 208a ₁ and the concave portion 408 is used, and the convex portion 208a ₁ and the concave portion when the sheet 400a ₁ on the first one end side rotates around the center O. Assuming that the amount of interference with 408 is θ, such a corner portion 408B can be formed so that the relationship of the amount of interference θ> the gap δ is satisfied.

The corner portion 408B described above is not only used for the sheet 400a1 on the _first one end side, but is also used for the other sheet on the one end side and / or the other sheet on the other end side. be able to.

Thus, according to the embodiments illustrated in FIGS. 9 (a) and 9 (b), each convex portion has a first contact point C1 and a second contact point C2 with respect to the concave portion 408 of the corresponding sheet. By contacting at the two points, the corresponding sheet is held and fixed between the two points. Thereby, each convex portion can more effectively regulate the rotation of the corresponding sheet.

As described above, various embodiments have been exemplified, but the above embodiments are merely examples and are not intended to limit the scope of the invention. The above embodiment can be implemented in various other embodiments, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. In addition, each configuration, shape, size, length, width, thickness, height, number, and the like can be appropriately changed for implementation.

10 Clutch disc 100 Disc plate (1st rotating body)
100A 1st disc plate 100B 2nd disc plate 200 Clutch hub (2nd rotating body)
400 Sheet member 400a ₁ , 400a ₂ A pair of sheet members (seat on the first end side, sheet on the other end side of the first)
404 Protruding part 410 Seat surface 412 Holding surface 414 1st regulation surface 415 2nd regulation surface 416 Transmission surface 500 Coil spring 500A 1st coil spring 500B 2nd coil spring 1000 Floating stopper 1100 Groove part 1200a, 1200b, 1300a, 1300b Inelastic body 1250, 1350 Elastic body 400, 500, 1000 Elastic mechanism CL, CLa, CLb, CLc, CLd Clearance

Claims (8)

The first rotating body and
A second rotating body that rotates relative to the first rotating body, and
An elastic mechanism portion accommodated between the first rotating body and the second rotating body and elastically connecting the first rotating body and the second rotating body in the rotational direction.
Equipped with
The elastic mechanism is
A sheet member that comes into contact with at least one of the first rotating body and the second rotating body when power is transmitted between the first rotating body and the second rotating body.
A coil spring whose both ends are supported by the pair of seat members,
It is housed in the coil spring, moves in the rotational direction and the radial direction in the coil spring, and has both ends sandwiched between the pair of seat members so that the first rotating body and the second rotating body are relative to each other. A floating stopper that stops rotation,
Have,
A damper device in which at least a part of the floating stopper is formed of an inelastic body . The damper device according to claim 1 , wherein a part of the floating stopper is formed of at least an elastic body elastically deformed in the rotational direction, and the other part is formed of the inelastic body. The damper device according to claim 1 or 2 , wherein the floating stopper has a predetermined clearance between the floating stopper and the inner peripheral portion of the coil spring and is housed in the coil spring. The seat member has a seat surface that abuts on the coil spring to support the coil spring and compresses the coil spring when the first rotating body and the second rotating body rotate relative to each other, and the first one. A transmission surface that abuts on the rotating body and the second rotating body to transmit power, a holding surface that abuts on the floating stopper and holds the first rotating body and the second rotating body when the first rotating body and the second rotating body rotate relative to each other. The damper device according to any one of claims 1 to 3, further comprising a regulatory surface that regulates the radial movement of the coil spring. The first rotating body and
A second rotating body that rotates relative to the first rotating body, and
An elastic mechanism portion accommodated between the first rotating body and the second rotating body and elastically connecting the first rotating body and the second rotating body in the rotational direction.
Equipped with
The elastic mechanism is
A sheet member that comes into contact with at least one of the first rotating body and the second rotating body when power is transmitted between the first rotating body and the second rotating body.
A coil spring whose both ends are supported by the pair of seat members,
It is housed in the coil spring, moves in the rotational direction and the radial direction in the coil spring, and has both ends sandwiched between the pair of seat members so that the first rotating body and the second rotating body are relative to each other. A floating stopper that stops rotation,
Have,
The coil spring has a first coil spring that houses the floating stopper inside, and a second coil spring that is wound outside the first coil spring and houses the first coil spring inside. Coil spring device. The seat member has a seat surface that abuts on the coil spring to support the coil spring and compresses the coil spring when the first rotating body and the second rotating body rotate relative to each other, and the first one. A transmission surface that abuts on the rotating body and the second rotating body to transmit power, a holding surface that abuts on the floating stopper and holds the first rotating body and the second rotating body when the first rotating body and the second rotating body rotate relative to each other. The damper device according to claim 5 , further comprising a regulatory surface that regulates the radial movement of the coil spring. The claim has a first regulatory surface that regulates the radial movement of the first coil spring and a second regulatory surface that regulates the radial movement of the second coil spring. Item 6. The damper device according to Item 6. The damper device according to claim 7, wherein the first regulating surface is formed on a protruding portion having a top portion as the holding surface, and the protruding portion projects toward the inside of the first coil spring.

Images