JP6965566B2 - Torque fluctuation absorber - Google Patents

Description

The present invention relates to a torque fluctuation absorber disposed between a drive source and a transmission.

Conventionally, the rotary vibration damper disclosed in Patent Document 1 below is known. This conventional rotary vibration damper is a hub that connects multiple springs in series, an intermediate plate that transmits the spring force of one spring to the other spring, and a hub that transmits the transmission torque transmitted through the other spring to the output shaft. And have.

International Publication No. 2009/0362727

Generally, in a torque fluctuation absorbing device such as the conventional rotary vibration damper, the axial position of the intermediate plate is determined with reference to the outer flanges arranged apart from each other in the axial direction, and the intermediate plate is used as a reference. The axial position of the flange portion provided on the hub is determined. In this case, the axial position of the intermediate plate is arranged within the allowable tolerance with respect to the outer plate, and the axial position of the flange portion is arranged within the allowable tolerance with reference to the intermediate plate. Therefore, the axial positions of the flange portion and the intermediate plate are determined within the range in which these allowable tolerances are added.

Further, in the torque fluctuation absorbing device, various members such as a spring and a thrust member are provided in order to suppress (attenuate) vibration in the rotational direction. In this case, the flange portion and the intermediate plate are arranged in the axial direction so as to be connected to a spring or the like. In this case, an allowable tolerance is set for the spring or the like. Therefore, the axial positions of the flange portion and the intermediate plate need to be determined so as to be connected to the spring or the like within the allowable tolerance set for the spring or the like. Further, the outer plate is also set with an allowable tolerance so that the spring or the like within the allowable tolerance can be accommodated inside so as not to hinder the operation of the spring or the like.

Therefore, when determining the axial position of the intermediate plate with reference to the outer plate and determining the axial position of the flange portion with reference to the intermediate plate, the allowable tolerances set for each member are added. It is necessary to determine the axial positions of the flange and intermediate plate. In this case, the axial dimension of the torque fluctuation absorber increases, and the torque fluctuation absorber becomes larger.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a torque fluctuation absorbing device capable of realizing miniaturization.

In order to solve the above problem, the invention of the torque fluctuation absorbing device according to claim 1 is a torque fluctuation absorbing device that absorbs the torque fluctuation generated in the torque transmission path from the input side rotating member to the output side rotating member. , A pair of outer shell plates that are connected to a vibration absorbing member in which a plurality of elastic members are connected in series to absorb torque fluctuations and are connected to an input side rotating member and arranged apart from each other in the axial direction of the output side rotating member. A hub member having a boss portion connected to the output side rotating member and a flange portion provided on the boss portion and arranged between a pair of outer shell plates, a flange portion of the hub member, and a pair of outer shells. Arranged between the plates and connected between the series of elastic members constituting the vibration absorbing member, from one of the series of elastic members to the other of the series of elastic members. Rutotomoni comprising a pair of intermediate plates annular transmitting torque, and a control plate annular rotatably connected integrally with the flange portion, is assembled to the outer periphery of the boss portion of the hub member, the flange portion The cylindrical first sliding contact member formed so as to be in sliding contact with the control plate and the first sliding contact member are pressed from the reference outer shell plate, which is one of the pair of outer shell plates, toward the flange portion. At the same time, the annular first pressing member that presses from the reference outer shell plate toward the control plate, the annular second sliding contact member that is in sliding contact with the intermediate plate, and the second sliding contact member are pressed from the reference outer shell plate to the intermediate plate. the second and the pressing member includes a flange portion located an axial position of the flange portion, the first sliding member and the first pressing member with respect to the axial position of the criteria shell plate for pressing the The intermediate plate position, which is the axial position of the intermediate plate, is determined by the second sliding contact member and the second pressing member with reference to the axial position of the reference outer plate.

According to this, the flange position of the flange portion of the hub member is determined with reference to the reference outer plate. The position of the intermediate plate of the intermediate plate is determined with reference to the reference outer plate. That is, in the torque fluctuation absorbing device of the present invention, the flange portion position and the intermediate plate position can be determined independently of each other with reference to the reference outer plate. Therefore, the number of members that determine the flange position can be reduced, and the number of members that determine the intermediate plate position can be reduced, so that the allowable tolerance set for each member and added can be reduced. be able to. As a result, the axial dimension of the torque fluctuation absorber can be reduced, and the torque fluctuation absorber can be miniaturized.

It is a partial notch figure which shows the structure of the torque fluctuation absorption apparatus which concerns on 1st Embodiment of this invention. It is sectional drawing which shows the torque fluctuation absorption apparatus in the section II-II of FIG. It is a figure for demonstrating the hysteresis characteristic. It is a partial notch figure which shows the structure of the torque fluctuation absorption apparatus which concerns on 2nd Embodiment of this invention. It is sectional drawing which shows the torque fluctuation absorption apparatus in the VV cross section of FIG. It is a figure for demonstrating the hysteresis characteristic. It is a partial notch figure which shows the structure of the torque fluctuation absorption apparatus which concerns on 3rd Embodiment of this invention. It is sectional drawing which shows the torque fluctuation absorption apparatus in the cross section of VIII-VIII of FIG. It is a partial notch figure which shows the structure of the torque fluctuation absorption apparatus which concerns on 4th Embodiment of this invention. It is sectional drawing which shows the torque fluctuation absorption apparatus in the XX cross section of FIG. It is sectional drawing which shows the torque fluctuation absorption apparatus which concerns on the 3rd Embodiment and 4th Embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the following embodiments and modifications, the same or equal parts are designated by the same reference numerals in the drawings. Further, each diagram used for explanation is a conceptual diagram, and the shape of each part may not always be exact.

The torque fluctuation absorbing device 1 (hereinafter, also referred to as “the device 1”) according to the present embodiment is applied to, for example, a hybrid vehicle. This device 1 is a device provided on an output shaft (not shown) of an engine (not shown) and absorbs (suppresses) fluctuation torque caused by an engine and an electric motor (not shown).

As shown in FIGS. 1 and 2, the apparatus 1 of the first embodiment has a disc plate 3 and a disc plate as a pair of outer plates connected to a hub member 2 and a flywheel F which is an input side rotating member. 4 and an intermediate plate 5 are provided. The hub member 2, the disc plate 3, the disc plate 4, and the intermediate plate 5 are rotatable around the rotation axis J. In the following description, the direction orthogonal to the rotation axis J is referred to as "the radial direction of the rotation axis J" or the unit "diameter direction", and the direction along the rotation axis J is the "axial direction of the rotation axis J" or simply. The direction of rotation around the rotation axis J is referred to as the "axial direction", and the direction of rotation around the rotation axis J is referred to as the "circumferential direction of the rotation axis J" or simply the "circumferential direction". Further, in the following description, the disc plate 3 is used as the reference outer plate of the pair of outer plates.

The hub member 2 has a boss portion 2a and a flange portion 2b. The boss portion 2a is formed in a cylindrical shape extending in the axial direction of the rotating shaft J, and is spline-engaged with the input shaft S, which is an output-side rotating member of the transmission (not shown), on the inner peripheral side. There is. The flange portion 2b is arranged between the disc plate 3 and the disc plate 4 which are a pair of outer shell plates, and is formed so as to extend in the radial direction of the rotation shaft J on the outer peripheral side of the boss portion 2a. The flange portion 2b forms a window portion for accommodating the coil spring 6, the spring seat 7, the spring seat 8, and the small spring 9 described later in the intermediate portion, and the spring seat 7 and the spring seat 8 They are in contact with each other or can be separated from each other. As shown in FIG. 2, the flange portion 2b is slidably in contact with the thrust member 10 as the first sliding contact member on the surface facing the disc plate 3, and is on the side facing the disc plate 4. It is slidably in contact with the thrust member 11 on the surface.

The disc plate 3 as the reference outer plate is formed in an annular shape, and is arranged axially separated from the flange portion 2b of the hub member 2 (on the right side in FIG. 2). The disc plate 3 has a plurality of uneven portions on the inner peripheral portion 3a, and the detent portion 10a of the thrust member 10 as the first sliding contact member described later is fitted to the uneven portions. As a result, the disc plate 3 cannot rotate relative to the thrust member 10 and can move in the axial direction. The disc plate 3 has one end of a disc spring 12 as a first pressing member arranged between a surface of the hub member 2 facing the flange portion 2b and a thrust member 10, and a side facing the flange portion 2b. It is in contact with the face. The disc plate 3 has a window portion for accommodating the coil spring 6, the spring seat 7, the spring seat 8, and the small spring 9 in the intermediate portion, and the circumferential end surface of the window portion is the spring seat 7. And in contact with or separable from the spring seat 8. The disc plate 3 is fixed on the outer peripheral side of the coil spring 6 together with the support plate 13 described later by, for example, a rivet.

The disc plate 4 is formed in an annular shape, and is arranged axially separated (on the left side in FIG. 2) with respect to the flange portion 2b of the hub member 2. The disc plate 4 is connected to the thrust member 11 at the inner peripheral portion. As a result, the disc plate 4 cannot rotate relative to the thrust member 11 and cannot move in the axial direction. The disc plate 4 has a window portion for accommodating the coil spring 6, the spring seat 7, the spring seat 8, and the small spring 9 in the intermediate portion, and the circumferential end surface of the window portion is the spring seat 7. And in contact with or separable from the spring seat 8. The disc plate 4 is fixed together with the support plate 13 on the outer peripheral side of the coil spring 6 by, for example, a rivet.

The intermediate plate 5 is arranged between the disc plate 3 and the disc plate 4 in the axial direction of the rotation axis J, more specifically, between the flange portion 2b of the hub member 2 and the disc plate 3 and the disc plate 4. ing. The intermediate plate 5 connects a plurality of (two in this embodiment) coil springs 6 in series via a spring seat 7 and a spring seat 8, and connects one coil spring 6 to the other coil spring 6. It transmits torque. The intermediate plate 5 is composed of a first plate 51 and a second plate 52.

The first plate 51 is arranged so as to face the disc plate 3 in the axial direction of the rotation axis J. The first plate 51 is formed in an annular shape, and as shown in FIG. 2, the small diameter portion 10b of the thrust member 10 which is the first sliding contact member described later is inserted through the inner peripheral portion 51a. As a result, the first plate 51 comes into contact with the small diameter portion 10b of the thrust member 10, and is pivotally supported by the small diameter portion 10b of the thrust member 10. As shown in FIG. 2, the first plate 51 is arranged axially separated from the flange portion 2b of the hub member 2 (on the right side in FIG. 2). More specifically, the first plate 51 is arranged so that a gap is formed between the surface of the hub member 2 facing the flange portion 2b and the surface facing the thrust member 10 and the thrust member 10. Has been done. Further, the first plate 51 is formed by a thrust member 14 as a second sliding contact member and a disc spring 15 as a second pressing member arranged between the surface facing the disc plate 3 and the disc plate 3. , The position of the arrangement of the rotation axis J with respect to the disc plate 3 in the axial direction is determined. The thrust member 14 is urged toward the first plate 51 by a disc spring 15.

The second plate 52 is arranged so as to face the disc plate 4 in the axial direction of the rotation axis J. The second plate 52 is formed in an annular shape, and as shown in FIG. 2, the inner peripheral portion is in contact with the thrust member 11. That is, the second plate 52 is pivotally supported by the thrust member 11. As shown in FIG. 2, the second plate 52 is arranged axially separated from the flange portion 2b of the hub member 2 (on the left side in FIG. 2). More specifically, the second plate 52 is arranged so that a gap is formed between the surface of the hub member 2 facing the flange portion 2b and the surface facing the thrust member 11 and the thrust member 11. Has been done. Further, the position of the second plate 52 in the axial direction of the rotation axis J is determined by the thrust member 16 arranged between the surface of the second plate 52 facing the disc plate 4 and the disc plate 4. There is.

As shown in FIG. 2, the first plate 51 and the second plate 52 are integrally connected by a pin member 53. In the pin member 53, the first plate 51 is fixed by caulking at the end on the disc plate 3 side. Further, a second plate 52 is fixed to the pin member 53 at the end on the disc plate 4 side by caulking.

As shown in FIG. 1, the coil spring 6 which is an elastic member includes a disc plate 3, a disc plate 4, a flange portion 2b of a hub member 2, and an intermediate plate 5 (first plate 51 and second plate 52). It is housed in a window formed in. The coil spring 6 comes into contact with the spring seats 7 and the spring seats 8 arranged at both ends. The coil spring 6 contracts when the disc plate 3, the disc plate 4, and the flange portion 2b rotate relative to each other in the circumferential direction of the rotation axis J. As a result, the coil spring 6 absorbs the shock due to the rotational difference between the disc plate 3 and the disc plate 4, the flange portion 2b, and the intermediate plate 5 (first plate 51 and second plate 52). ..

The spring seat 7 and the spring seat 8 are provided at the ends of the coil spring 6 in the circumferential direction, respectively. The spring seat 7 and the spring seat 8 have windows formed on the disc plate 3, the disc plate 4, the flange portion 2b of the hub member 2, and the intermediate plate 5 (first plate 51 and second plate 52), respectively. It is housed in the department. As a result, the spring seat 7 and the spring seat 8 are arranged between the window portion and the end portion of the coil spring 6.

The small spring 9 is arranged on the inner peripheral side of the coil spring 6. The small spring 9 comes into contact with the opposing spring seat 7 and the spring seat 8 when the coil spring 6 contracts. As a result, the small spring 9 absorbs the shock due to the rotational difference between the disc plate 3 and the disc plate 4 and the flange portion 2b.

Here, the coil spring 6, the spring seat 7, the spring seat 8 and the small spring 9 connected in series constitute the vibration absorbing member A.

The thrust member 10 which is the first sliding contact member is arranged between the disc spring 12 which is the outer periphery of the boss portion 2a of the hub member 2 and is the first pressing member and the flange portion 2b of the hub member 2, and is a boss portion. It is in sliding contact with 2a and the flange portion 2b. As shown in FIGS. 1 and 2, the thrust member 10 includes a detent portion 10a, a small diameter portion 10b, and a large diameter portion 10c. As shown in FIG. 1, the detent portion 10a extends along the circumferential direction of the rotation axis J so as to make the portion extending toward the disc plate 3 side unable to rotate relative to the disc plate 3 and the disc spring 12. It is formed in an uneven shape. The small diameter portion 10b is inserted through the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5. The large diameter portion 10c has a larger diameter than the small diameter portion 10b and is in sliding contact with the flange portion 2b. The outer diameter of the large diameter portion 10c is set to be larger than the inner diameter of the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5.

The thrust member 10 is urged toward the flange portion 2b by the disc spring 12. As a result, the thrust member 10 cooperates with the disc spring 12, and the hub member 2 (more specifically, the flange portion 2b of the hub member 2) is based on the axial position of the disc plate 3 which is the reference outer plate. ) In the axial direction of the rotation axis J, that is, the position of the flange portion is determined.

The thrust member 11 is the outer periphery of the hub member 2, is arranged between the disc plate 4 and the flange portion 2b of the hub member 2, and is in sliding contact with the flange portion 2b. The thrust member 11 is connected by the disc plate 4 so as to be relatively non-rotatable and axially movable at a portion extending toward the disc plate 4 on the inner peripheral side.

The disc spring 12, which is the first pressing member, is the outer periphery of the thrust member 10 and is arranged between the thrust member 10 and the disc plate 3. The disc spring 12 urges the thrust member 10 to the flange portion 2b side of the hub member 2. As shown in FIG. 1, the disc spring 12 has a concavo-convex portion corresponding to the detent portion 10a of the thrust member 10 on the inner peripheral portion, and the detent portion 10a is engaged with the concavo-convex portion to the thrust member 10. It is assembled so that it cannot rotate relative to each other and can move in the axial direction.

The support plate 13 has a diameter larger than that of the disc plate 3 and the disc plate 4, and is formed in an annular shape extending in the radial direction of the rotation axis J. The support plate 13 is fixed between the disc plate 3 and the disc plate 4 together with the disc plate 3 and the disc plate 4 by, for example, rivets. The support plate 17, the cover plate 18, the friction plate 19, and the disc spring 20 are assembled to the outer peripheral side portion of the support plate 13. The support plate 13, the support plate 17, the cover plate 18, the friction plate 19, and the disc spring 20 constitute the limit mechanism of the present device 1.

The thrust member 14, which is the second sliding contact member, is arranged radially outward from the thrust member 10 between the disc plate 3 and the first plate 51 of the intermediate plate 5, and is arranged with the first plate 51. Sliding contact. The thrust member 14 is urged toward the first plate 51 by a disc spring 15 which is a second pressing member. The thrust member 14 has a pull-out prevention portion 14a that extends through a hole portion 3b provided on the outer peripheral side of the disc plate 3 with a contact portion with the disc spring 15. The thrust member 14 assembled to the disc plate 3 by engaging the pull-out prevention portion 14a and the hole portion 3b cooperates with the disc spring 15 and refers to the axial position of the disc plate 3 which is the reference outer plate. The position of the first plate 51 in the axial direction of the rotation axis J, that is, the position of the intermediate plate is determined.

The disc spring 15, which is the second pressing member, is arranged between the disc plate 3 and the thrust member 14. The disc spring 15 urges the thrust member 14 toward the first plate 51. Therefore, the disc spring 15 determines the intermediate plate position of the first plate 51 with reference to the axial position of the disc plate 3.

The thrust member 16 is arranged radially outward from the thrust member 11 between the disc plate 4 and the second plate 52 of the intermediate plate 5, and is in sliding contact with the second plate 52. The thrust member 16 has a pull-out prevention portion 16a extending radially outward from the thrust member 11 through a hole portion 4a provided in the disc plate 4. The thrust member 16 assembled to the disc plate 4 by engaging the pull-out prevention portion 16a and the hole portion 4a determines the axial position of the second plate 52 with respect to the disc plate 4.

The support plate 17 is formed in an annular shape. The support plate 17 is arranged between the flywheel F and the cover plate 18 in the vicinity of the outer periphery. The support plate 17 is fixed to the cover plate 18 by rivets, for example, and is fixed to the flywheel F together with the cover plate 18 by bolts and nuts (not shown). The support plate 17 is separated from the cover plate 18 on the inner peripheral side. The support plate 17 is slidably in contact with one end side of the disc spring 20.

The cover plate 18 is formed in an annular shape. The cover plate 18 is arranged near the outer periphery so as to face the opposite surface of the support plate 17 on the flywheel F side. The cover plate 18 is fixed to the support plate 17 by rivets, for example, and is fixed to the flywheel F together with the support plate 17 by bolts and nuts (not shown). The cover plate 18 is separated from the support plate 17 on the inner peripheral side. The cover plate 18 is slidably in contact with the support plate 13.

The friction plate 19 is formed in an annular shape and is held on the outer peripheral side of the support plate 13. The friction plate 19 is arranged between the support plate 13 and the other end side of the disc spring 20, and is slidably in contact with the support plate 13. The friction plate 19 has a pull-out prevention portion 19a extending radially outward from the support plate 13 through a hole portion 18a provided in the cover plate 18. The friction plate 19 is fixed to the cover plate 18 so as not to rotate relative to the cover plate 18 by the engagement between the pull-out prevention portion 19a and the hole portion 18a, and is urged toward the support plate 13 side by the disc spring 20.

The disc spring 20 is arranged between the support plate 17 and the friction plate 19. The disc spring 20 urges the friction plate 19 toward the support plate 13. Here, the support plate 17, the cover plate 18, the friction plate 19, and the disc spring 20 exert the limiter function of the present device 1. That is, when the disc spring 20 urges the friction plate 19 toward the support plate 17, a frictional force is generated between the support plate 17 and the friction plate 19. The generated frictional force is connected to the friction plate 19 connected to the flywheel F side and the input shaft S side when the relative torque that causes relative rotation between the flywheel F and the input shaft S becomes excessive. A slip is caused between the support plate 13 and the support plate 13. This prevents excessive relative torque from being transmitted from the flywheel F side to the input shaft S side.

As can be understood from the above description, the torque fluctuation absorbing device 1 of the first embodiment occurs in the torque transmission path from the fly wheel F which is the input side rotating member to the input shaft S of the transmission which is the output side rotating member. A torque fluctuation absorber that absorbs vibrations caused by torque fluctuations, and is a vibration absorbing member A (coil springs 6) that absorbs vibrations caused by torque fluctuations by connecting a plurality of elastic members coil springs 6 in series. , Spring seats 7 and 8 and small springs 9), and disc plates 3 and 4 which are a pair of outer plates connected to the fly wheel F and arranged apart from each other in the axial direction of the input shaft S of the transmission. , A hub member 2 having a boss portion 2a connected to the input shaft S of the transmission, and a flange portion 2b provided on the boss portion 2a and arranged between the disc plates 3 and 4, and a flange of the hub member 2. From the coil spring 6 of one of the series coil springs 6 which is arranged between the portion 2b and the disc plates 3 and 4 and connected between the series coil springs 6 constituting the vibration absorbing member A. An annular intermediate plate 5 (first plate 51 and second plate 52) that transmits torque to the other coil spring 6 of the series coil springs 6 is provided, and the flange portion 2b of the hub member 2 is provided. The position of the flange portion, which is the axial position, is determined with reference to the axial position of the disc plate 3 as the reference outer plate, which is one of the pair of disc plates 3 and 4, and the first plate 51 of the intermediate plate 5 is determined. The position of the intermediate plate, which is the axial position of, is determined with reference to the axial position of the disc plate 3, which is the reference outer plate.

According to this, the position of the flange portion of the flange portion 2b of the hub member 2 is determined with reference to the disc plate 3 which is the reference outer plate. Further, the intermediate plate position of the first plate 51 constituting the intermediate plate 5 is determined with reference to the disc plate 3 which is the reference outer plate. That is, in the present device 1, the flange portion position and the intermediate plate position can be determined independently of each other with the disc plate 3 as a reference.

Therefore, the number of members that determine the flange position can be reduced, and the number of members that determine the intermediate plate position can be reduced, so that the allowable tolerance set for each member and added can be reduced. be able to. As a result, the axial dimension of the apparatus 1 can be reduced, and the miniaturization of the apparatus 1 can be achieved.

In this case, the torque fluctuation absorbing device 1 is assembled on the outer periphery of the boss portion 2a of the hub member 2, and is a thrust member 10 which is a cylindrical first sliding contact member that is in sliding contact with the boss portion 2a and is in sliding contact with the flange portion 2b. And, the countersunk spring 12 which is the first pressing member that presses the thrust member 10 from the disc plate 3 which is the reference outer plate toward the flange portion 2b, and the annular first plate which is in sliding contact with the first plate 51 of the intermediate plate 5. The thrust member 14, which is a two-sliding contact member, and the countersunk spring 15, which is a second pressing member that presses the thrust member 14 from the disc plate 3 which is the reference outer plate toward the first plate 51 of the intermediate plate 5. The flange portion position is determined by the thrust member 10 and the countersunk spring 12, and the intermediate plate position is determined by the thrust member 14 and the countersunk spring 15.

According to this, the flange portion position and the intermediate plate position are determined by using the thrust member 10 and the disc spring 12 and the thrust member 14 and the disc spring 15 that exert a function of absorbing (attenuating) torque fluctuations. be able to. As a result, it is not necessary to add other members to determine the flange portion position and the intermediate plate position, and in addition to being able to achieve miniaturization of the present device 1, the manufacturing cost of the present device 1 can be reduced.

Further, in these cases, the thrust member 10 which is the first sliding contact member is larger than the outer diameter of the small diameter portion 10b which is slidably contacted with the flange portion 2b and the small diameter portion 10b inserted into the first plate 51 of the intermediate plate 5. It has a large diameter portion 10c provided with a large diameter, and the size of the outer diameter of the large diameter portion 10c is the size of the inner diameter of the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5. It can be provided so as to be larger than the relative size.

According to this, since the outer diameter of the large diameter portion 10c of the thrust member 10 can be made larger than the inner diameter of the inner peripheral portion 51a of the first plate 51, the friction of the large diameter portion 10c in sliding contact with the flange portion 2b The area can be increased. As a result, the amount of wear associated with the sliding contact of the large diameter portion 10c can be reduced, so that the axial thickness of the large diameter portion 10c can be reduced. Therefore, since the axial dimension of the thrust member 10 can be reduced, the miniaturization of the present device 1 can be achieved.

In this case, the small diameter portion 10b can come into contact with the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5.

According to this, the small diameter portion 10b of the thrust member 10 can be brought into contact with the inner peripheral portion 51a through the first plate 51 of the intermediate plate 5, so that the first plate 51 can be pivotally supported. can. As a result, it is not necessary to separately provide a bearing to support the first plate 51, and the manufacturing cost of the apparatus 1 can be reduced.

Further, in these cases, the magnitude of the thrust load generated by the thrust member 10 which is the first sliding contact member in sliding contact with the flange portion 2b and the thrust member 14 which is the second sliding contact member are the first of the intermediate plate 5. The magnitude of the thrust load generated by sliding contact with the plate 51 can be made different from each other, and the magnitude of the pressing force with which the disc spring 12 which is the first pressing member presses the thrust member 10 against the flange portion 2b and the second pressing force. The magnitude of the pressing force that the disc spring 15 which is a member presses the thrust member 14 against the first plate 51 of the intermediate plate 5 can be different from each other.

According to this, when the present device 1 absorbs the vibration caused by the torque fluctuation generated in the torque transmission path, it represents the change characteristic of the torque (transmission torque) with respect to the twist angle generated between the device 1 and the input shaft S of the transmission. The hysteresis characteristics can be set appropriately. That is, with respect to the rotational fluctuation of the flange portion 2b, a frictional force is applied to the flange portion 2b by the thrust member 10 and the disc spring 12, and the hysteresis characteristic of the torque with respect to the twist angle can be set. Further, with respect to the rotational fluctuation of the first plate 51, a frictional force is applied to the first plate 51 by the thrust member 14 and the disc spring 15, and the hysteresis characteristic of the torque with respect to the twist angle can be set. Thereby, for example, the thrust load of the thrust member 10 and the pressing force of the disc spring 12 are set so that the frictional force applied to the flange portion 2b is larger than the frictional force applied to the first plate 51. As a result, the hysteresis characteristic as shown in FIG. 3 can be obtained. Therefore, in the present device 1, it is possible to achieve miniaturization and appropriately set the hysteresis characteristic for reducing (damping) the vibration caused by the torque fluctuation.

(Second Embodiment)
In the first embodiment, the hysteresis characteristic is obtained by the thrust member 10 and the thrust member 11, which are the first sliding contact members, in sliding contact with the flange portion 2b of the hub member 2. In this case, it is also possible to make the obtained hysteresis characteristic variable. Hereinafter, the second embodiment will be described in detail, but the same parts as those of the first embodiment will be designated by the same reference numerals, and the description thereof will be omitted.

In this second embodiment, as shown in FIGS. 4 and 5, the control plate 21, the control plate 22, the thrust member 23, the disc spring 24, and the thrust member 25 are relative to the apparatus 1 in the upper first embodiment. And the pin member 26 is provided.

The control plate 21 is arranged between the flange portion 2b of the hub member 2 and the thrust member 10 on the disc plate 3 side in the axial direction of the rotation shaft J. The control plate 21 is formed in an annular shape, and one side thereof is slidably in contact with the thrust member 10. As a result, as shown in FIG. 5, the position of the control plate 21 is determined by the thrust member 10 in the axial direction of the rotation axis J. The inner peripheral portion of the control plate 21 is pivotally supported by a thrust member 23 extending to the boss portion 2a of the hub member 2.

The control plate 22 is arranged between the flange portion 2b of the hub member 2 and the thrust member 11 on the disc plate 4 side in the axial direction of the rotation shaft J. The control plate 22 is formed in an annular shape, and one side thereof is slidably in contact with the thrust member 11. The inner peripheral portion of the control plate 22 is separated from the outer peripheral portion of the boss portion 2a of the hub member 2.

The thrust member 23 is the outer periphery of the boss portion 2a of the hub member 2, is arranged between the flange portion 2b of the hub member 2 and the control plate 21, and is in sliding contact with the flange portion 2b. The thrust member 23 is urged toward the flange portion 2b of the hub member 2 by the disc spring 24.

The disc spring 24 is arranged between the control plate 21 and the thrust member 23. One end side of the disc spring 24 is fixed to the thrust member, and the other end side abuts on the other surface side of the control plate 21. The disc spring 24 urges the control plate 21 toward the thrust member 10 and urges the thrust member 23 toward the flange portion 2b of the hub member 2 by the reaction force thereof.

Here, in the second embodiment, the flange portion position of the flange portion 2b of the hub member 2 is determined by the thrust member 10 and the thrust member 23, and the disc spring 12 and the disc spring 24. That is, in this second embodiment, the first sliding contact member is composed of the thrust member 10 and the thrust member 23, and the first pressing member is composed of the disc spring 12 and the disc spring 24. Therefore, also in this second embodiment, the flange portion position is determined independently of the intermediate plate 5 with reference to the disc plate 3 which is the reference outer plate.

The thrust member 25 is the outer periphery of the boss portion 2a of the hub member 2, is arranged between the flange portion 2b of the hub member 2 and the other surface side of the control plate 22, and is slidably in contact with the flange portion 2b. .. The thrust member 25 determines the axial position of the control plate 22 with respect to the flange portion 2b.

As shown in FIG. 5, the pin member 26 fixes the control plate 21 by caulking at the end on the disc plate 3 side. Further, the pin member 26 fixes the control plate 22 by caulking at the end portion on the disc plate 4 side. Here, the size of the outer diameter of the pin member 26 is set smaller than the size of the inner diameter of the insertion hole formed in the control plates 21 and 22 and through which the pin member 26 is inserted.

The apparatus 1 of the second embodiment configured in this way has a control plate 21 and a control plate 22, as well as a thrust member 23, a disc spring 24, and a thrust member 25. As a result, as shown in FIG. 6, the hysteresis characteristic representing the relationship between the twist angle and the torque can be switched according to the twist angle of the disc plate 3 and the disc plate 4 with respect to the input shaft S. Specifically, as shown in FIG. 6, for example, a small hysteresis characteristic is exhibited with respect to a positive torsion angle corresponding to the rotation direction of the input shaft S, and a negative torsion opposite to the rotation direction of the input shaft S is exhibited. The hysteresis characteristic can be switched (variable) according to the twist angle so as to exhibit a large hysteresis characteristic with respect to the angle. When such a hysteresis characteristic is exhibited, the thrust members 10, 11, 14, 16, 23, 25 and the disc springs 12, 15 and 24 provided in the present device 1 are independent of each other. Therefore, the frictional force generated by the sliding contact can be freely set.

Therefore, according to the second embodiment, the flange portion position and the intermediate plate position are independently determined with reference to the disc plate 3 which is the reference outer plate, respectively, as in the first embodiment. Can be done. As a result, the size of the apparatus 1 in the axial direction can be reduced. Then, in the second embodiment, the control plates 21, 22 and the thrust members 23, 25 and the disc spring 24 can be added to the apparatus 1 having a smaller axial size to switch the hysteresis characteristics. Therefore, it is possible to achieve miniaturization as compared with the case where the conventional torque fluctuation absorbing device is provided with a configuration for switching the hysteresis characteristics. Regarding other effects in the second embodiment, the same effects as in the case of the first embodiment can be obtained.

(Third Embodiment)
In the present device 1 of the first embodiment, as shown in FIGS. 1 and 2, the thrust member 10 which is the first sliding contact member is cylindrical and has an uneven shape along the circumferential direction of the rotation axis J. A detent portion 10a is provided so that the inner peripheral portion 3a of the disc plate 3, which is a reference outer plate, engages with the detent portion 10a. As a result, when the rotation of the thrust member 10 is hindered by the disc plate 3, the hub member 2 rotates integrally with the input shaft S, and a relative rotation occurs between the thrust member 10 and the flange portion 2b, the thrust is thrust. A frictional force is generated between the member 10 and the flange portion 2b.

By the way, the size of the outer diameter of the large diameter portion 10c of the thrust member 10 is larger than the size of the inner diameter of the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5. Therefore, when assembling the apparatus 1, first, the first plate 51 and the second plate 52 constituting the intermediate plate 5 are crimped by the pin member 53 with the thrust member 10 arranged on the hub member 2. .. In this case, the thrust member 10 generates a frictional force between the boss portion 2a and the flange portion 2b of the hub member 2, but is not fixed to the flange portion 2b or the first plate 51 so as to be non-rotatable. ..

Therefore, when assembling the disc plate 3, the thrust member 10 is rotated and adjusted so as to correspond to the assembling rotation position of the disc plate 3, or the disc plate 3 is engaged with the detent portion 10a of the thrust member 10. After that, it is necessary to adjust the assembly rotation position. Therefore, the assembly work of the present device 1 becomes complicated. Therefore, in the third embodiment, the above-mentioned effect described in the first embodiment is maintained, and the assembling workability of the present device 1 is improved and improved. Hereinafter, the third embodiment will be specifically described.

As shown in FIGS. 7 and 8, the apparatus 1 of the third embodiment replaces the thrust member 10 which is the first sliding contact member in the first embodiment with the thrust member which is the third sliding contact member. It has 30. The thrust member 30 is arranged between the disc spring 31 which is the third pressing member and the disc plate 3 which is the outer periphery of the boss portion 2a of the hub member 2 and is the reference outer plate, and is in sliding contact with the disc plate 3. ..

The thrust member 30 is formed in a stepped cylindrical shape, and includes a detent portion 30a, a small diameter portion 30b, and a large diameter portion 30c. As shown in FIG. 8, the detent portion 30a is provided in the large diameter portion 30c and is formed in a protruding shape protruding toward the flange portion 2b of the hub member 2. The detent portion 30a is inserted into the engagement hole 2b1 formed in the flange portion 2b to fix the thrust member 30 to the hub member 2 and the disc spring 31 described later so as not to rotate relative to each other. The small diameter portion 30b is inserted through the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5. The small diameter portion 30b is in sliding contact with the disc plate 3 at the tip. Here, as shown in FIG. 8, the size of the outer diameter of the small diameter portion 30b is provided so as to be larger than the size of the inner diameter of the inner peripheral portion 3a of the disc plate 3. The large diameter portion 30c is formed at the base end of the small diameter portion 30b to have a diameter larger than the outer diameter of the small diameter portion 30b, and a detent portion 30a is integrally provided on the outer peripheral side.

As shown in FIG. 8, the disc spring 31 which is the third pressing member is arranged between the thrust member 30 and the flange portion 2b of the hub member 2. One end of the disc spring 31 is fixed so as not to rotate relative to the detent portion 30a of the thrust member 30, and the other end is in contact with the small diameter portion 30b of the thrust member 30. As a result, the disc spring 31 cannot rotate relative to the thrust member 30, and the thrust member 30 is urged toward the disc plate 3.

In the thrust member 30 of the present apparatus 1 in the third embodiment, the detent portion 30a is fixed to the flange portion 2b of the hub member 2, and the small diameter portion 30b is a reference outer plate by the disc spring 31 fixed to the detent portion 30a. It slides (contacts) with a certain disc plate 3. As a result, the thrust member 30 cooperates with the disc spring 31, and the hub member 2 (more specifically, the flange portion 2b of the hub member 2) is based on the axial position of the disc plate 3 which is the reference outer plate. ) In the axial direction of the rotation axis J, that is, the position of the flange portion is determined.

The thrust member 32, which is the fourth sliding contact member, is configured in the same manner as the thrust member 14 as the second sliding contact member in the first embodiment. That is, the thrust member 32 is arranged radially outward from the thrust member 30 between the disc plate 3 and the first plate 51 of the intermediate plate 5, and is in sliding contact with the first plate 51. The thrust member 32 is urged toward the first plate 51 by a disc spring 33 which is a fourth pressing member. Like the thrust member 14, the thrust member 32 has a pull-out prevention portion 32a that extends through a hole portion 3b provided on the outer peripheral side of the disc plate 3 with a contact portion with the disc spring 33. The thrust member 32 assembled to the disc plate 3 by engaging the pull-out prevention portion 32a and the hole portion 3b cooperates with the disc spring 33 and refers to the axial position of the disc plate 3 which is the reference outer plate. The position of the intermediate plate, which is the position of the first plate 51 in the axial direction of the rotation axis J, is determined.

The disc spring 33, which is the fourth pressing member, is arranged between the disc plate 3 and the thrust member 32, similarly to the disc spring 15 of the first embodiment. The disc spring 33 urges the thrust member 32 toward the first plate 51. Therefore, the disc spring 33, like the disc spring 15, determines the intermediate plate position of the first plate 51 with reference to the axial position of the disc plate 3. In the apparatus 1 of the third embodiment, the configuration of the disc plate 4 side is the same as that of the first embodiment.

When assembling the apparatus 1 of the third embodiment configured in this way, the thrust member 30 which is the third sliding contact member and the disc spring 31 which is the third pressing member are inserted into the boss portion 2a of the hub member 2. .. Then, the detent portion 30a of the thrust member 30 is inserted into the engagement hole 2b1 formed in the flange portion 2b, and the thrust member 30 and the disc spring 31 are fixed to the hub member 2 so as not to rotate relative to each other. In this way, with the thrust member 30 and the disc spring 31 fixed, the first plate 51 of the intermediate plate 5, the thrust member 32 and the fourth sliding contact member, which are the fourth sliding contact members, are the same as in the first embodiment. The disc spring 33, which is a pressing member, is assembled, and the disc plate 3 is assembled. Here, in the third embodiment, when the disc plate 3 is assembled, unlike the case of the first embodiment, the disc plate 3 is a hub member without adjusting the assembly rotation position with respect to the thrust member 30. It is assembled with the boss portion 2a of 2 inserted.

As can be understood from the above description, the torque fluctuation absorbing device 1 of the third embodiment is the disc plate 3 and the hub member 2 which are at least the reference outer plates of the disc plates 3 and 4 which are the pair of outer plates. A cylindrical third slide which has a detent portion 30a which is arranged between the flange portion 2b and fixed to the flange portion 2b so as not to rotate relative to the flange portion 2b, and which is in sliding contact with the disc plate 3 which is a reference outer plate. The thrust member 30 which is a contact member, the countersunk spring 31 which is an annular third pressing member that presses the thrust member 30 from the flange portion 2b toward the disc plate 3 which is the reference outer plate, and the first of the intermediate plate 5. The thrust member 32, which is an annular fourth sliding contact member that is in sliding contact with the plate 51 of the above, and the fourth member that presses the thrust member 32 from the disc plate 3 which is the reference outer plate toward the first plate 51 of the intermediate plate 5. The countersunk spring 33, which is a pressing member, is provided, the flange portion position is determined by the thrust member 30 and the countersunk spring 31, and the intermediate plate position is determined by the thrust member 32 and the countersunk spring 33.

According to this, the flange portion position and the intermediate plate position can be determined by using the thrust member 30 and the disc spring 31 and the thrust member 32 and the disc spring 33 that exert a function of absorbing (attenuating) torque fluctuations. .. As a result, in the third embodiment as well, as in the first embodiment, it is not necessary to add other members to determine the flange portion position and the intermediate plate position, and the miniaturization of the present device 1 can be achieved. In addition, the manufacturing cost of the apparatus 1 can be reduced.

Further, in the third embodiment, the thrust member is attached to the flange portion 2b of the hub member 2 before the intermediate plate 5 (first plate 51 and second plate 52) is crimped and fixed by the pin member 53. The 30 and the disc spring 31 can be easily fixed so as not to rotate relative to each other. Further, the disc plate 3 can be easily assembled to the boss portion 2a of the hub member 2 without adjusting the assembly rotation position of the disc plate 3 with respect to the thrust member 30 fixed so as to be relatively non-rotatable. Therefore, in the present device 1 in the third embodiment, the assembly workability can be significantly improved.

Further, in this case, the thrust member 30 which is the third sliding contact member inserts the first plate 51 of the intermediate plate 5 and at least the reference outer shell of the disc plates 3 and 4 which are a pair of outer shell plates at the tip. It has a small diameter portion 30b that is in sliding contact with the disc plate 3 that is a plate, and a large diameter portion 30c that has a larger diameter than the outer diameter of the small diameter portion 30b at the base end of the small diameter portion 30b and is provided with a detent portion 30a. The size of the outer diameter of the small diameter portion 30b is relative to the size of the inner diameter of the inner peripheral portion 3a of the disc plate 3 which is at least the reference outer plate of the pair of outer plate disc plates 3 and 4. It can be provided so as to be large.

According to this, since the outer diameter of the small diameter portion 30b of the thrust member 30 can be made larger than the inner diameter of the inner peripheral portion 3a of the disc plate 3, the friction area of the small diameter portion 30b that is in sliding contact with the disc plate 3 is increased. be able to. As a result, when the relative rotation occurs between the hub member 2 and the disc plate 3 due to the torque fluctuation, the thrust member 30 can satisfactorily absorb (attenuate) the generated torque fluctuation.

(Fourth Embodiment)
In the third embodiment, the thrust member 30, which is the third sliding contact member, is fixed to the flange portion 2b of the hub member 2 so as not to rotate relative to the flange portion 2b via the detent portion 30a. Here, also in the present device 1 of the third embodiment, the control plate 21, the control plate 22, the thrust member 23, the disc spring 24, the thrust member 25, and the pin member 26 are provided as in the second embodiment. , The hysteresis characteristic can be made variable.

In this case, as shown in FIGS. 9 and 10, the control plate 21, the thrust member 23, and the disc spring 24 have the flange portion 2b of the hub member 2 and the thrust member 30 as in the case of the second embodiment. It is provided between them. By the way, as described in the second embodiment, the control plate 21 is fixed by the pin member 26 together with the control plate 22 to the flange portion 2b of the hub member 2 so as to be integrally rotatable. Therefore, in the fourth embodiment, the thrust member 30, which is the third sliding contact member, is fixed to the control plate 21 which rotates integrally with the flange portion 2b of the hub member 2 so as to be relatively non-rotatable. Improves assembly workability. Hereinafter, the fourth embodiment will be specifically described.

In the fourth embodiment, as shown in FIG. 10, the detent portion 30a of the thrust member 30 is provided on the large diameter portion 30c and is formed in a protruding shape protruding toward the control plate 21. Then, the detent portion 30a in the fourth embodiment is inserted into the engaging hole 21a formed in the control plate 21 and fixed to the control plate 21 so as not to rotate relative to the control plate 21. Here, the control plate 21 is fixed to the flange portion 2b of the hub member 2 so as to be integrally rotatable. Therefore, also in this fourth embodiment, the thrust member 30 is fixed to the hub member 2 and the disc spring 31 which is the third pressing member so as not to rotate relative to each other. The other configurations are the same as those in the second embodiment and the third embodiment.

When assembling the apparatus 1 of the fourth embodiment configured in this way, first, the thrust member 23 and the disc spring 24 are inserted into the disc plate 3 side of the boss portion 2a of the hub member 2, and the boss portion 2a is inserted. The thrust member 25 is inserted through the disc plate 4 side of the above. Then, in this state, the control plate 21 and the control plate 22 are fixed by the pin member 26 to the flange portion 2b of the hub member 2 so as to be integrally rotatable.

Subsequently, the thrust member 30 which is the third sliding contact member and the disc spring 31 which is the third pressing member are inserted into the boss portion 2a of the hub member 2. Then, the detent portion 30a of the thrust member 30 is inserted into the engagement hole 21a formed in the control plate 21, and the thrust member 30 and the disc spring 31 are made unable to rotate relative to the control plate 21 and the hub member 2. Fix it. In this way, with the thrust member 30 and the disc spring 31 fixed, the first plate 51 of the intermediate plate 5, the thrust member 32 and the fourth sliding contact member, which are the fourth sliding contact members, are the same as in the third embodiment. The disc spring 33, which is a pressing member, is assembled, and the disc plate 3 is assembled. Here, also in the fourth embodiment, when the disc plate 3 is assembled, the disc plate 3 is the hub member 2 without adjusting the assembly rotation position with respect to the thrust member 30 as in the third embodiment. It is assembled with the boss portion 2a of the above inserted.

Therefore, the torque fluctuation absorbing device 1 of the fourth embodiment includes the annular control plates 21 and 22 rotatably connected together with the hub member 2 and around the thrust member 30 which is the third sliding contact member. The stopper 30a is fixed so as not to rotate relative to the control plate 21 of the control plates 21 and 22.

According to this, even when the control plates 21 and 22 are provided, the control plate 21 is before the intermediate plate 5 (first plate 51 and second plate 52) is crimped and fixed by the pin member 53. That is, the thrust member 30 and the disc spring 31 can be easily fixed to the hub member 2 which is integrally rotatably connected so as not to rotate relative to each other. Further, the disc plate 3 can be easily assembled to the boss portion 2a of the hub member 2 without adjusting the assembly rotation position of the disc plate 3 with respect to the thrust member 30 fixed so as to be relatively non-rotatable. Therefore, even in the present device 1 in the fourth embodiment, the assembly workability can be significantly improved. Regarding other effects, the same effects as those of the second embodiment and the third embodiment can be obtained.

(Modified examples of the third embodiment and the fourth embodiment)
In the third embodiment and the fourth embodiment, among the disc plates 3 and 4 which are a pair of outer plates, the disc plate 3 is used as the reference outer plate. Then, a detent portion 30a is provided on the thrust member 30 which is the third sliding contact member arranged on the disc plate 3 side, and the engagement hole 2b1 or the control plate 21 provided on the flange portion 2b of the hub member 2 is provided. The detent portion 30a is engaged with the joint hole 21a.

In addition to this, as shown in FIG. 11, with respect to the thrust member 11 arranged on the disc plate 4 side, the detent portion corresponding to the detent portion 30a provided on the thrust member 30 which is the third sliding contact member. It is also possible to provide 11a. In this case, the uneven detent portion provided on the thrust member 11 and engaging with the inner peripheral portion of the disc plate 4 is omitted. Note that FIG. 11 shows the case of the present device 1 in the third embodiment.

In this way, when the detent portion 11a is provided on the thrust member 11, the detent portion 11a is provided on the flange portion 2b as in the case of the third embodiment and the fourth embodiment. It is engaged with the engagement hole 22a provided in the joint hole 2b1 or the control plate 22. As a result, the thrust member 11 is fixed to the hub member 2 so as not to rotate relative to the hub member 2, similarly to the thrust member 30 in the third embodiment and the fourth embodiment.

As a result, in this modification, it is not necessary to adjust the assembly rotation position of the disc plate 4 when assembling the disc plate 4. Therefore, in this modification, the disc plates 3 and 4 can be easily assembled to the hub member 2, and as a result, the assembly workability can be significantly improved.

In carrying out the present invention, various modifications can be adopted without being limited to the above embodiments and as long as the object of the present invention is not deviated.

For example, in each of the above embodiments, the disc plate 3 is used as a reference outer plate, and the flange portion position of the flange portion 2b of the hub member 2 and the intermediate plate position of the intermediate plate 5 (first plate 51) are determined. .. Instead of this, the disc plate 4 which is one of the disc plates 3 and 4 which is a pair of outer plates is used as the reference outer plate, and the flange portion position and the intermediate plate position of the intermediate plate 5 (second plate 52) are determined. It is also possible.

In this case, the thrust member 10 which is the first sliding contact member and the thrust member 14 which is the second sliding contact member in the first embodiment and the second embodiment are relative to a plane orthogonal to the rotation axis J. It is arranged symmetrically between the disc plate 4 and the flange portion 2b of the hub member 2. Alternatively, the thrust member 30 which is the third sliding contact member and the thrust member 32 which is the fourth sliding contact member in the third embodiment and the fourth embodiment are symmetrical with respect to the plane orthogonal to the rotation axis J. As described above, it is arranged between the disc plate 4 and the flange portion 2b of the hub member 2. As a result, even when the disc plate 4 is used as the reference outer plate, the same effect as that of each of the above embodiments can be obtained.

Further, in each of the above embodiments, the coil springs 6 are connected in series as a plurality of elastic members. In this case, the plurality of elastic members are not limited to coil springs, and it is also possible to use other forms of spring members and connect the plurality of spring members in series.

1 ... Torque fluctuation absorber, 2 ... Hub member, 2a ... Boss, 2b ... Flange, 2b1 ... Engagement hole, 3 ... Disc plate (outer plate, reference outer plate), 3a ... Inner circumference, 3b ... Hole Part, 4 ... Disc plate (outer plate), 4a ... Hole, 5 ... Intermediate plate, 51 ... First plate, 51a ... Inner circumference, 52 ... Second plate, 53 ... Pin member, 6 ... Coil spring (Multiple elastic members), 7 ... Spring seat, 8 ... Spring seat, 9 ... Small spring, 10 ... Thrust member (first sliding contact member), 10a ... Anti-rotation part, 10b ... Small diameter part, 10c ... Large diameter part , 11 ... Thrust member, 12 ... Countersunk spring (first pressing member), 13 ... Support plate, 14 ... Thrust member (second sliding contact member), 14a ... Detachment prevention part, 15 ... Countersunk spring (second pressing member) , 16 ... Thrust member, 16a ... Detachment prevention part, 17 ... Support plate, 18 ... Cover plate, 18a ... Hole, 19 ... Friction plate, 19a ... Detachment prevention part, 20 ... Countersunk spring, 21 ... Control plate, 21a ... Engagement hole, 22 ... Control plate, 22a ... Engagement hole, 23 ... Thrust member (first sliding contact member), 24 ... Countersunk spring (first pressing member), 25 ... Thrust member, 26 ... Pin member, 30 ... Thrust member (third sliding contact member), 31 ... countersunk spring (third pressing member), 32 ... thrust member (fourth sliding contact member), 33 ... countersunk spring (fourth pressing member), A ... vibration absorbing member, F ... Fly wheel (input side rotating member), J ... rotating shaft, S ... input shaft (output side rotating member)

Claims (8)

A torque fluctuation absorber that absorbs torque fluctuations that occur in the torque transmission path from the input side rotating member to the output side rotating member.
A vibration absorbing member in which a plurality of elastic members are connected in series to absorb the torque fluctuation,
A pair of annular outer plates connected to the input-side rotating member and arranged apart from each other in the axial direction of the output-side rotating member.
A hub member having a boss portion connected to the output-side rotating member and a flange portion provided on the boss portion and arranged between the pair of outer plates.
Among the elastic members in series, which are arranged between the flange portion of the hub member and the pair of outer shell plates and connected between the elastic members in series constituting the vibration absorbing member. A pair of annular intermediate plates that transmit torque from one elastic member to another of the elastic members in series.
It is provided with an annular control plate that is rotatably connected together with the flange portion.
A cylindrical first sliding contact member, which is assembled on the outer periphery of the boss portion of the hub member and is formed so as to be in sliding contact with the flange portion and in sliding contact with the control plate.
An annular first member that presses the first sliding contact member from the reference outer plate, which is one of the pair of outer plates, toward the flange portion and from the reference outer plate toward the control plate. Pressing member and
An annular second sliding contact member that slides in contact with the intermediate plate,
A second pressing member that presses the second sliding contact member from the reference outer plate toward the intermediate plate is provided.
The flange portion position, which is the axial position of the flange portion, is
Determined by the first sliding contact member and the first pressing member with reference to the axial position of the reference outer plate.
The intermediate plate position, which is the axial position of the intermediate plate, is
A torque fluctuation absorbing device determined by the second sliding contact member and the second pressing member with reference to the axial position of the reference outer plate. The first sliding contact member is
A small diameter part to be inserted through the intermediate plate and
It has a large diameter portion that is slidably contacted with the flange portion and is provided with a diameter larger than the outer diameter of the small diameter portion.
The size of the outer diameter of the large diameter part is
The torque fluctuation absorbing device according to claim 1, which is provided so as to be larger than the size of the inner diameter of the inner peripheral portion of the intermediate plate. The small diameter part
The torque fluctuation absorbing device according to claim 2, which comes into contact with the inner peripheral portion of the intermediate plate. The magnitude of the thrust load generated by the first sliding contact member sliding in contact with the flange portion and the magnitude of the thrust load generated by the second sliding contact member sliding in contact with the intermediate plate are different from each other.
The magnitude of the pressing force that the first pressing member presses the first sliding contact member against the flange portion and the magnitude of the pressing force that the second pressing member presses the second sliding contact member against the intermediate plate are determined. The torque fluctuation absorbing device according to any one of claims 1 to 3, which is different from each other. A torque fluctuation absorber that absorbs torque fluctuations that occur in the torque transmission path from the input side rotating member to the output side rotating member.
A vibration absorbing member in which a plurality of elastic members are connected in series to absorb the torque fluctuation,
A pair of annular outer plates connected to the input-side rotating member and arranged apart from each other in the axial direction of the output-side rotating member.
A hub member having a boss portion connected to the output-side rotating member and a flange portion provided on the boss portion and arranged between the pair of outer plates.
Among the elastic members in series, which are arranged between the flange portion of the hub member and the pair of outer shell plates and connected between the elastic members in series constituting the vibration absorbing member. A pair of annular intermediate plates for transmitting torque from one elastic member to the other elastic member among the elastic members in series are provided.
The reference outer shell is arranged between the reference outer shell plate, which is one of the pair of outer shell plates, and the flange portion, and has a detent portion which is fixed so as not to rotate relative to the flange portion. A cylindrical third sliding contact member that slides in contact with the plate,
An annular third pressing member that presses the third sliding contact member from the flange portion toward the reference outer plate.
An annular fourth sliding contact member that slides in contact with the intermediate plate,
A fourth pressing member that presses the fourth sliding contact member from the reference outer plate toward the intermediate plate is provided.
The flange portion position, which is the axial position of the flange portion, is
Determined by the third sliding contact member and the third pressing member with reference to the axial position of the reference outer plate.
The intermediate plate position, which is the axial position of the intermediate plate, is
A torque fluctuation absorbing device determined by the fourth sliding contact member and the fourth pressing member with reference to the axial position of the reference outer plate. The torque fluctuation absorber is
An annular control plate arranged between the flange portion of the hub member and the third sliding contact member and rotatably connected together with the flange portion is provided.
The detent portion of the third sliding contact member is
It is fixed so that it cannot rotate relative to the control plate.
The third pressing member is
The torque fluctuation absorbing device according to claim 5, wherein the third sliding contact member is pressed from the control plate toward the reference outer plate. The third sliding contact member is
A small diameter portion through which the intermediate plate is inserted and in sliding contact with at least the reference outer plate of the pair of outer plates at the tip thereof.
It has a large diameter portion at the base end of the small diameter portion, which is larger than the outer diameter of the small diameter portion and is provided with the detent portion.
The size of the outer diameter of the small diameter part is
The torque fluctuation absorbing device according to claim 5 or 6, which is provided so as to be larger than the size of the inner diameter of at least the inner peripheral portion of the reference outer plate of the pair of outer plates. The first sliding contact member is arranged between the flange portion and the control plate and is in sliding contact with the flange portion, and is arranged between the reference outer shell plate and the control plate and is provided on the control plate. Has a sliding contact part,
The first pressing member presses a portion that is in sliding contact with the flange portion from the control plate toward the flange portion and a portion that is in sliding contact with the control plate from the reference outer plate toward the control plate. The torque fluctuation absorbing device according to claim 1, further comprising a portion to be used.

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