JP2018096534A - Torque fluctuation absorbing apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torque fluctuation absorbing apparatus which can be downsized.SOLUTION: The torque fluctuation absorbing apparatus comprises: a vibration absorbing member A in which coil springs 6 are coupled in series, and which absorbs vibration resulting from a torque fluctuation; a pair of disc plates 3, 4 coupled to a flywheel F, and arranged to be spatially separated from each other in an axial direction of an input shaft S of a transmission; a hub member 2 including a boss section 2a coupled to the input shaft S, and a flange section 2b provided on the boss section 2a, and arranged between the disc plates 3, 4; and a circular intermediate plate 5 arranged between the flange section 2b of the hub member 2 and the disc plates 3, 4, and coupled between the coil springs 6. A flange section position of the flange section 2b of the hub member 2 is determined with an axial position of the disc part 3 as a reference, and an intermediate plate position of the intermediate plate 5 is determined with the axial position of the disc plate 3 as a reference.SELECTED DRAWING: Figure 2

Description

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

  Conventionally, a rotational vibration damper disclosed in Patent Document 1 below is known. This conventional rotational vibration damper has a plurality of 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.

International Publication No. 2009/036727

  In general, in a torque fluctuation absorber such as the above-described conventional rotational vibration damper, the axial position of the intermediate plate is determined with reference to the outer plates 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 disposed within the allowable tolerance with reference to the outer plate, and the axial position of the flange portion is disposed within the allowable tolerance with respect to the intermediate plate. Accordingly, the axial positions of the flange portion and the intermediate plate are determined within a range in which these tolerances are added.

  In the torque fluctuation absorber, 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 disposed 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 position of the flange portion and the intermediate plate needs to be determined so as to be coupled to the spring or the like within the allowable tolerance set for the spring or the like. In order not to disturb the operation of the springs and the like, the outer tolerance is set so that the outer plate can accommodate the springs and the like within the allowable tolerance.

  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, add the tolerance set for each member. Therefore, it is necessary to determine the axial positions of the flange portion and the intermediate plate. In this case, the axial dimension of the torque fluctuation absorber increases, and the torque fluctuation absorber increases in size.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a torque fluctuation absorber that can achieve downsizing.

  In order to solve the above-described problem, the invention of a torque fluctuation absorber according to claim 1 is a torque fluctuation absorber that absorbs torque fluctuation generated in a torque transmission path from an input side rotating member to an output side rotating member. A vibration absorbing member in which a plurality of elastic members are connected in series to absorb torque fluctuations, and a pair of outer plates connected to the input side rotating member and spaced 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 rotation member, a flange portion provided on the boss portion and disposed between the pair of outer plates, a flange portion of the hub member, and a pair of outer shells Between the elastic members arranged in series and constituting the vibration absorbing member between one elastic member of the serial elastic members and the other elastic member of the serial elastic members. Torque transmission The flange portion position, which is the axial position of the flange portion, is determined with reference to the axial position of the reference outer plate that is one of the pair of outer plates. The intermediate plate position, which is the axial position, is determined based on the axial position of the reference outer plate.

  According to this, the flange part position of the flange part of a hub member is determined on the basis of a reference outline plate. The intermediate plate position of the intermediate plate is determined with reference to the reference outline plate. That is, in the torque fluctuation absorber according to the present invention, the flange portion position and the intermediate plate position can be determined independently of each other on the basis of the reference outer plate. Accordingly, it is possible to reduce the number of members that determine the flange portion position, and it is possible to reduce the number of members that determine the intermediate plate position, thereby reducing the allowable tolerance set for each member and added. be able to. As a result, the axial dimension of the torque fluctuation absorber can be reduced, and the torque fluctuation absorber can be reduced in size.

1 is a partially cutaway view illustrating a configuration of a torque fluctuation absorber according to a first embodiment of the present invention. It is sectional drawing which shows the torque fluctuation absorber in the II-II cross section of FIG. It is a figure for demonstrating a hysteresis characteristic. FIG. 5 is a partially cutaway view showing a configuration of a torque fluctuation absorber according to a second embodiment of the present invention. It is sectional drawing which shows the torque fluctuation absorber in the VV cross section of FIG. It is a figure for demonstrating a hysteresis characteristic. FIG. 6 is a partially cutaway view showing a configuration of a torque fluctuation absorber according to a third embodiment of the present invention. It is sectional drawing which shows the torque fluctuation absorber in the VIII-VIII cross section of FIG. FIG. 10 is a partially cutaway view showing a configuration of a torque fluctuation absorber according to a fourth embodiment of the present invention. FIG. 10 is a cross-sectional view showing the torque fluctuation absorber in the XX cross section of FIG. 9. It is sectional drawing which shows the torque fluctuation absorber which concerns on 3rd embodiment of this invention, and the modification of 4th embodiment.

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

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

  As shown in FIGS. 1 and 2, the device 1 of the first embodiment includes a hub member 2 and a disk plate 3 and a disk plate as a pair of outer plates connected to a flywheel F that is an input side rotating member. 4 and an intermediate plate 5. The hub member 2, the disk plate 3, the disk plate 4, and the intermediate plate 5 are rotatable around the rotation axis J. In the following description, a direction orthogonal to the rotation axis J is referred to as “radial direction of the rotation axis J” or a unit “radial direction”, and a direction along the rotation axis J is referred to as “axial direction of the rotation axis J” or simply The direction of rotation about the rotation axis J is referred to as “axial direction”, and the “circumferential direction of the rotation axis J” or simply “circumferential direction” is referred to. In the following description, the disk plate 3 is used as a reference outline plate of the pair of outline 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 rotation axis J, and is spline-engaged with an input shaft S that is an output side rotation member of a transmission (not shown) on the inner peripheral side. Yes. The flange portion 2b is disposed between the disc plate 3 and the disc plate 4, which are a pair of outer plates, and is formed to extend in the radial direction of the rotation axis J on the outer peripheral side of the boss portion 2a. The flange portion 2 b forms a window portion for accommodating a coil spring 6, a spring seat 7, a spring seat 8, and a small spring 9, which will be described later, at an intermediate portion. They are in contact or can be separated. As shown in FIG. 2, the flange portion 2 b is slidably in contact with the thrust member 10 as the first sliding contact member on the surface on the side facing the disk plate 3, and on the side facing the disk plate 4. The surface is slidably in contact with the thrust member 11.

  The disc plate 3 as a reference outer plate is formed in an annular shape, and is spaced apart from the flange portion 2b of the hub member 2 in the axial direction (on the right side in FIG. 2). The disk plate 3 has a plurality of concavo-convex portions on the inner peripheral portion 3a, and a detent portion 10a of a thrust member 10 as a first sliding contact member described later is fitted to the concavo-convex portion. As a result, the disk plate 3 is not rotatable relative to the thrust member 10 and is movable in the axial direction. The disk plate 3 has one end of a disc spring 12 as a first pressing member disposed between a surface of the hub member 2 facing the flange portion 2b and the thrust member 10, and a side facing the flange portion 2b. It touches at the surface. 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 at the intermediate portion, and the circumferential end surface of the window portion is the spring seat 7. The spring seat 8 is in contact with or separated from the spring seat 8. The disk plate 3 is fixed to the outer peripheral side of the coil spring 6 together with a support plate 13 described later, for example, by rivets.

  The disk plate 4 is formed in an annular shape, and is disposed so as to be separated from the flange portion 2b of the hub member 2 in the axial direction (on the left side in FIG. 2). The disk plate 4 is connected to the thrust member 11 at the inner periphery. Thereby, the disk plate 4 cannot be rotated relative to the thrust member 11 and cannot be moved 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 at the intermediate portion, and the circumferential end surface of the window portion is the spring seat 7. The spring seat 8 is in contact with or separated from the spring seat 8. The disc plate 4 is fixed to the outer peripheral side of the coil spring 6 together with the support plate 13 by, for example, rivets.

  The intermediate plate 5 is disposed 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 is configured to connect a plurality (two in this embodiment) of coil springs 6 in series via a spring seat 7 and a spring seat 8, and from one coil spring 6 to the other coil spring 6. Torque is transmitted. The intermediate plate 5 includes a first plate 51 and a second plate 52.

  The first plate 51 is disposed so as to face the disk plate 3 in the axial direction of the rotation axis J. The 1st plate 51 is formed in the annular | circular shape, and as shown in FIG. 2, the small diameter part 10b of the thrust member 10 which is the 1st sliding contact member mentioned later in the inner peripheral part 51a is penetrated. As a result, the first plate 51 comes into contact with the small diameter portion 10 b of the thrust member 10 and is supported by the small diameter portion 10 b of the thrust member 10. As shown in FIG. 2, the first plate 51 is disposed so as to be separated from the flange portion 2 b of the hub member 2 in the axial direction (on the right side in FIG. 2). More specifically, the first plate 51 is disposed so that a gap is formed between the thrust member 10 and the surface facing the thrust member 10 while facing the flange portion 2 b of the hub member 2. Has been. Further, the first plate 51 is provided by a thrust member 14 as a second sliding contact member and a disc spring 15 as a second pressing member disposed between the surface on the side facing the disc plate 3 and the disc plate 3. The arrangement position in the axial direction of the rotation axis J with respect to the disk plate 3 is determined. The thrust member 14 is urged toward the first plate 51 by the disc spring 15.

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

  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 of the disk plate 3 side. A second plate 52 is fixed to the pin member 53 by caulking at the end on the disk plate 4 side.

  As shown in FIG. 1, the coil spring 6 which is an elastic member includes a disk plate 3, a disk plate 4, a flange portion 2b of the hub member 2, and an intermediate plate 5 (first plate 51 and second plate 52). It is accommodated in the window part formed in the. The coil spring 6 is in contact with a spring seat 7 and a spring seat 8 disposed at both ends. The coil spring 6 contracts when the disk plate 3 and the disk plate 4 and the flange portion 2 b are relatively rotated in the circumferential direction of the rotation axis J. As a result, the coil spring 6 absorbs shock due to a rotational difference between the disk plate 3 and the disk plate 4, the flange portion 2b, and the intermediate plate 5 (the first plate 51 and the second plate 52). .

  The spring seat 7 and the spring seat 8 are each provided at the end of the coil spring 6 in the circumferential direction. The spring seat 7 and the spring seat 8 are windows formed in 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. Housed in the department. Thereby, the spring seat 7 and the spring seat 8 are disposed between the window portion and the end portion of the coil spring 6.

  The small spring 9 is disposed on the inner peripheral side of the coil spring 6. The small spring 9 comes into contact with the opposing spring seat 7 and spring seat 8 when the coil spring 6 contracts. Thereby, the small spring 9 absorbs the shock due to the rotational difference between the disk plate 3 and the disk 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 a vibration absorbing member A.

  The thrust member 10 that is the first sliding contact member is disposed between the disc spring 12 that is the first pressing member and the flange portion 2b of the hub member 2 on the outer periphery of the boss portion 2a of the hub member 2, and the boss portion. 2a and the flange portion 2b are in sliding contact. As shown in FIGS. 1 and 2, the thrust member 10 includes a detent portion 10 a, a small diameter portion 10 b, and a large diameter portion 10 c. As shown in FIG. 1, the rotation stopper 10 a extends along the circumferential direction of the rotation axis J in order to prevent relative rotation with respect to the disk plate 3 and the disc spring 12 at the portion extending toward the disk plate 3. It is formed in an uneven shape. The small diameter portion 10 b is inserted through the inner peripheral portion 51 a 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 10 c is set larger than the inner diameter of the inner peripheral portion 51 a of the first plate 51 of the intermediate plate 5.

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

  The thrust member 11 is disposed on the outer periphery of the hub member 2 between the disk 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 disk plate 4 so as not to be relatively rotatable and axially movable at a portion extending toward the inner peripheral disk plate 4.

  The disc spring 12 as the first pressing member is disposed on the outer periphery of the thrust member 10 and between the thrust member 10 and the disk plate 3. The disc spring 12 biases the thrust member 10 toward the flange portion 2 b of the hub member 2. As shown in FIG. 1, the disc spring 12 has an uneven portion corresponding to the anti-rotation portion 10 a of the thrust member 10 on the inner peripheral portion, and the anti-rotation portion 10 a is engaged with the uneven portion, Thus, it is assembled so as not to be relatively rotatable and to be movable in the axial direction.

  The support plate 13 has a larger diameter than the disk plate 3 and the disk 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 13 is assembled with a support plate 17, a cover plate 18, a friction plate 19, and a disc spring 20 on the outer peripheral side portion. The support plate 13, the support plate 17, the cover plate 18, the friction plate 19, and the disc spring 20 constitute a limit mechanism of the apparatus 1.

  The thrust member 14, which is the second sliding contact member, is arranged between the disk plate 3 and the first plate 51 of the intermediate plate 5, radially outward from the thrust member 10. Make sliding contact. The thrust member 14 is urged toward the first plate 51 by a disc spring 15 that is a second pressing member. The thrust member 14 has a drop prevention portion 14a that extends through a hole portion 3b that is provided on the outer peripheral side of the contact portion of the disc plate 3 with the disc spring 15. The thrust member 14 assembled to the disc plate 3 by the engagement of the slip-off preventing portion 14a and the hole portion 3b cooperates with the disc spring 15 and uses the axial position of the disc plate 3 as the reference outer plate as a reference. 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 as the second pressing member is disposed between the disc plate 3 and the thrust member 14. The disc spring 15 biases the thrust member 14 toward the first plate 51. Accordingly, the disc spring 15 determines the position of the intermediate plate of the first plate 51 with reference to the axial position of the disc plate 3.

  The thrust member 16 is disposed between the disk plate 4 and the second plate 52 of the intermediate plate 5 at the outer side in the radial direction than the thrust member 11, and is in sliding contact with the second plate 52. The thrust member 16 has a removal prevention portion 16a extending through the hole 4a provided in the disk plate 4 at a radially outer side than the thrust member 11. The thrust member 16 assembled to the disc plate 4 by the engagement between the slip-off preventing portion 16a and the hole 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 disposed 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, for example, rivets, 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 disposed in the vicinity of the outer periphery so as to face the opposite surface of the 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 disposed between the support plate 13 and the other end side of the disc spring 20 and slidably contacts the support plate 13. The friction plate 19 has a removal prevention portion 19 a extending through the hole portion 18 a provided in the cover plate 18 on the outer side in the radial direction than the support plate 13. 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 of the stopper 19a and the hole 18a, and is urged toward the support plate 13 by the disc spring 20.

  The disc spring 20 is disposed between the support plate 17 and the friction plate 19. The disc spring 20 biases 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 exhibit the limiter function of the apparatus 1. That is, when the disc spring 20 biases the friction plate 19 toward the support plate 17, a frictional force is generated between the support plate 17 and the friction plate 19. When the relative torque that causes relative rotation between the flywheel F and the input shaft S becomes excessive, the generated friction force is connected to the friction plate 19 connected to the flywheel F side and the input shaft S side. A slip is generated 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 absorber 1 of the first embodiment is generated in the torque transmission path from the flywheel F that is the input side rotating member to the input shaft S of the transmission that is the output side rotating member. And a vibration absorbing member A (coil spring 6) that absorbs vibration caused by torque fluctuation by connecting a plurality of coil springs 6 as elastic members in series. , Spring seats 7 and 8 and small springs 9) and a pair of outer plates connected to the flywheel F and spaced apart from each other in the axial direction of the input shaft S of the transmission, The boss portion 2a connected to the input shaft S of the transmission and the boss portion 2a provided between the disc plates 3 and 4 Between the series of coil springs 6 constituting the vibration absorbing member A, which is disposed between the hub member 2 having the flange portion 2b, the flange portion 2b of the hub member 2, and the disk plates 3 and 4. And an annular intermediate plate 5 (the first plate 51 and the first plate 51) that transmits torque from one coil spring 6 of the series coil springs 6 to the other coil spring 6 of the series coil springs 6. The flange portion position, which is the axial position of the flange portion 2b of the hub member 2, is the axis of the disc plate 3 as a reference outer plate that is one of the pair of disc plates 3 and 4. The intermediate plate position, which is determined on the basis of the position of the direction and is the axial position of the first plate 51 of the intermediate plate 5, is the reference outer plate. That is determined relative to the axial position of the disc plate 3.

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

  Accordingly, it is possible to reduce the number of members that determine the flange portion position, and it is possible to reduce the number of members that determine the intermediate plate position, thereby reducing the allowable tolerance set for each member and added. be able to. As a result, the axial dimension of the apparatus 1 can be reduced, and downsizing of the apparatus 1 can be achieved.

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

  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 exhibit the function of absorbing (attenuating) torque fluctuation. be able to. Thereby, it is not necessary to add other members to determine the flange portion position and the intermediate plate position, and in addition to the reduction in size of the apparatus 1, the manufacturing cost of the apparatus 1 can be reduced.

  Further, in these cases, the thrust member 10 as the first sliding contact member has a smaller diameter portion 10b inserted into the first plate 51 of the intermediate plate 5 and an outer diameter of the smaller diameter portion 10b in sliding contact with the flange portion 2b. A large-diameter portion 10c provided on the large diameter, and the outer diameter of the large-diameter portion 10c is the same as the inner diameter of the inner peripheral portion 51a of the first plate 51 of the intermediate plate 5. It can provide so that it may become large compared with.

  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 that is 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 device 1 can be reduced in size.

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

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

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

  According to this, when the present apparatus 1 absorbs vibration caused by torque fluctuation generated in the torque transmission path, it represents a change characteristic of torque (transmission torque) with respect to a torsion angle generated with respect to the input shaft S of the transmission. Hysteresis characteristics can be set appropriately. That is, with respect to the rotation 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 torsion 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 torque hysteresis characteristic with respect to the torsion 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. Thus, a hysteresis characteristic as shown in FIG. 3 can be obtained. Therefore, in the present apparatus 1, it is possible to achieve a reduction in size and appropriately set a hysteresis characteristic for reducing (attenuating) vibration caused by torque fluctuation.

(Second embodiment)
In the first embodiment, hysteresis characteristics are obtained by the thrust member 10 and the thrust member 11 being the first sliding contact members being in sliding contact with the flange portion 2b of the hub member 2. In this case, it is possible to vary the obtained hysteresis characteristic. Hereinafter, although this 2nd embodiment is described in detail, the same code | symbol is attached | subjected to the same part as said 1st embodiment, and the description is abbreviate | omitted.

  In the 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 compared to the apparatus 1 in the upper first embodiment. And the pin member 26 is provided.

  The control plate 21 is disposed between the flange portion 2 b of the hub member 2 and the thrust member 10 on the disk plate 3 side in the axial direction of the rotation axis J. The control plate 21 is formed in an annular shape, and one surface side is slidably in contact with the thrust member 10. Thereby, as shown in FIG. 5, the control plate 21 is configured such that the position of the arrangement in the axial direction of the rotation axis J is determined by the thrust member 10. The control plate 21 is pivotally supported by a thrust member 23 whose inner peripheral portion extends to the boss portion 2 a of the hub member 2.

  The control plate 22 is disposed between the flange portion 2 b of the hub member 2 and the thrust member 11 on the disk plate 4 side in the axial direction of the rotation axis J. The control plate 22 is formed in an annular shape, and one surface side is slidably in contact with the thrust member 11. The control plate 22 has an inner peripheral portion spaced from the outer periphery of the boss portion 2 a of the hub member 2.

  The thrust member 23 is disposed on the outer periphery of the boss portion 2a of the hub member 2 and 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 2 b of the hub member 2 by a disc spring 24.

  The disc spring 24 is disposed between the control plate 21 and the thrust member 23. The disc spring 24 has one end fixed to the thrust member and the other end abutting against the other surface 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.

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

  The thrust member 25 is disposed on the outer periphery of the boss portion 2a of the hub member 2 and between the flange portion 2b of the hub member 2 and the other surface side of the control plate 22, and slidably contacts 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 portion on the disk plate 3 side. The pin member 26 fixes the control plate 22 by caulking at the end on the disk plate 4 side. Here, the outer diameter of the pin member 26 is set smaller than 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 according to the second embodiment configured as described above includes a control plate 21 and a control plate 22, and also includes a thrust member 23, a disc spring 24, and a thrust member 25. Thereby, 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 disk plate 3 and the disk plate 4 with respect to the input shaft S. Specifically, as shown in FIG. 6, for example, a negative torsion that exhibits a small hysteresis characteristic with respect to a positive torsion angle coinciding with the rotation direction of the input shaft S and is opposite to the rotation direction of the input shaft S. The hysteresis characteristic can be switched (variable) according to the twist angle so as to exhibit a large hysteresis characteristic with respect to the corner. And when exhibiting such a hysteresis characteristic, the thrust members 10, 11, 14, 16, 23, 25 and the disc springs 12, 15, 24 provided in the present apparatus 1 are independent of each other. Therefore, the frictional force generated with the sliding contact can be freely set.

  Therefore, according to the second embodiment, as in the first embodiment, the flange portion position and the intermediate plate position are independently determined based on the disk plate 3 which is the reference outer plate. Can do. Thereby, the magnitude | size of the axial direction of this apparatus 1 can be made small. In the second embodiment, the control plates 21 and 22, the thrust members 23 and 25, and the disc spring 24 can be added to the apparatus 1 having a reduced axial size to switch the hysteresis characteristics. Therefore, it is possible to achieve a reduction in size as compared with the case where a configuration for switching the hysteresis characteristics is provided in the conventional torque fluctuation absorber. In addition, about the other effect in 2nd embodiment, the effect equivalent to the case of said 1st embodiment is acquired.

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

  By the way, the outer diameter of the large-diameter portion 10 c of the thrust member 10 is larger than the inner diameter of the inner peripheral portion 51 a of the first plate 51 of the intermediate plate 5. For this reason, when the apparatus 1 is assembled, first, the first plate 51 and the second plate 52 constituting the intermediate plate 5 are caulked by the pin member 53 in a state where the thrust member 10 is disposed 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 not to be relatively rotatable. .

  Therefore, when the disk plate 3 is assembled, the thrust member 10 is rotated and adjusted so as to correspond to the assembly rotation position of the disk plate 3, or the disk plate 3 is engaged with the rotation stop portion 10a of the thrust member 10. After that, it is necessary to adjust the assembly rotation position. For this reason, the assembly work of this apparatus 1 becomes complicated. Therefore, in the third embodiment, the above-described effects described in the first embodiment are maintained, and the assembly workability of the apparatus 1 is improved and improved. The third embodiment will be specifically described below.

  As shown in FIGS. 7 and 8, the device 1 of the third embodiment is replaced with a thrust member that is a third sliding contact member instead of the thrust member 10 that is the first sliding contact member in the first embodiment. 30. The thrust member 30 is disposed on the outer periphery of the boss portion 2 a of the hub member 2 between the disc spring 31 that is the third pressing member and the disc plate 3 that 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 rotation preventing portion 30a, a small diameter portion 30b, and a large diameter portion 30c. As shown in FIG. 8, the rotation preventing portion 30 a is provided on the large diameter portion 30 c and is formed in a protruding shape that protrudes toward the flange portion 2 b of the hub member 2. The anti-rotation portion 30a is inserted into an engagement hole 2b1 formed in the flange portion 2b, and fixes the thrust member 30 to the hub member 2 and a disc spring 31 described later so as not to be relatively rotatable. The small diameter portion 30 b is inserted through the inner peripheral portion 51 a 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, the outer diameter of the small diameter portion 30b is provided to be larger than the inner diameter of the inner peripheral portion 3a of the disc plate 3, as shown in FIG. The large-diameter portion 30c is formed with a larger diameter than the outer diameter of the small-diameter portion 30b at the base end of the small-diameter portion 30b, and an anti-rotation portion 30a is integrally provided on the outer peripheral side.

  As shown in FIG. 8, the disc spring 31 as the third pressing member is disposed between the thrust member 30 and the flange portion 2 b of the hub member 2. One end of the disc spring 31 is fixed so as not to rotate relative to the rotation preventing portion 30 a of the thrust member 30, and the other end contacts the small diameter portion 30 b of the thrust member 30. As a result, the disc spring 31 cannot rotate relative to the thrust member 30 and urges the thrust member 30 toward the disk plate 3.

  In the thrust member 30 of the present apparatus 1 in the third embodiment, the anti-rotation portion 30a is fixed to the flange portion 2b of the hub member 2, and the small diameter portion 30b is a reference outline plate by a disc spring 31 fixed to the anti-rotation portion 30a. It is in sliding contact (contact) with a certain disk plate 3. Thus, the thrust member 30 cooperates with the disc spring 31 and uses the hub member 2 (more specifically, the flange portion 2b of the hub member 2 as a reference) based on the axial position of the disc plate 3 that is the reference outer plate. ) In the axial direction of the rotation axis J, that is, the flange position.

  The thrust member 32 that is the fourth sliding contact member is configured similarly to the thrust member 14 as the second sliding contact member in the first embodiment. In other words, the thrust member 32 is disposed between the disk plate 3 and the first plate 51 of the intermediate plate 5 at the outer side in the radial direction than the thrust member 30, 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 that is a fourth pressing member. Similar to the thrust member 14, the thrust member 32 has a slip prevention portion 32 a that extends through the hole 3 b provided on the outer peripheral side of the contact portion of the disc plate 3 with the disc spring 33. The thrust member 32 assembled to the disc plate 3 by the engagement of the slip-off preventing portion 32a and the hole portion 3b cooperates with the disc spring 33 and uses the axial position of the disc plate 3 as a reference outer plate as a reference. The intermediate plate position, which is the position of the first plate 51 in the axial direction of the rotation axis J, is determined.

  The disc spring 33 as the fourth pressing member is disposed between the disc plate 3 and the thrust member 32 in the same manner as the disc spring 15 of the first embodiment. The disc spring 33 biases the thrust member 32 toward the first plate 51 side. Accordingly, the disc spring 33 determines the position of the intermediate plate of the first plate 51 on the basis of the axial position of the disc plate 3, similarly to the disc spring 15. In the present apparatus 1 in the third embodiment, the configuration on the disk plate 4 side is the same as that in the first embodiment.

  When assembling the apparatus 1 of the third embodiment configured as described above, the thrust member 30 as the third sliding contact member and the disc spring 31 as the third pressing member are inserted into the boss portion 2a of the hub member 2. . Then, the rotation preventing 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 be relatively rotatable. As described above, in the state where the thrust member 30 and the disc spring 31 are fixed, the first plate 51 of the intermediate plate 5, the thrust member 32 and the fourth sliding contact member, and the fourth, as in the first embodiment. A disc spring 33 as a pressing member is assembled, and the disc plate 3 is assembled. Here, in the third embodiment, when the disk plate 3 is assembled, unlike the case of the first embodiment, the disk plate 3 is a hub member without adjusting the assembly rotation position with respect to the thrust member 30. It is assembled in a state where the two boss portions 2a are inserted.

  As can be understood from the above description, the torque fluctuation absorber 1 according to the third embodiment includes at least the disc plate 3 that is the reference outer plate and the hub member 2 of the disc plates 3 and 4 that are the pair of outer plates. A cylindrical third slide which is disposed between the flange portion 2b and has a non-rotating portion 30a which is fixed 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. A thrust member 30 that is a contact member, a disc spring 31 that is an annular third pressing member that presses the thrust member 30 toward the disc plate 3 that is a reference outer plate from the flange portion 2b, and a first of the intermediate plate 5 A thrust member 32 that is an annular fourth sliding contact member that is in sliding contact with the plate 51, and a disk plate that is a reference outer plate. And a disc spring 33 that is a fourth pressing member that presses toward the first plate 51 of the intermediate plate 5, and the flange portion position is determined by the thrust member 30 and the disc spring 31. The position is determined by the thrust member 32 and the disc spring 33.

  According to this, the flange portion position and the intermediate plate position can be determined using the thrust member 30, the disc spring 31, the thrust member 32, and the disc spring 33 that exhibit the function of absorbing (attenuating) torque fluctuations. . Thereby, also in 3rd embodiment, it is not necessary to add another member in order to determine a flange part position and an intermediate | middle plate position similarly to said 1st embodiment, and it can achieve size reduction of this apparatus 1. In addition, the manufacturing cost of the device 1 can be reduced.

  In the third embodiment, before the intermediate plate 5 (the first plate 51 and the second plate 52) is caulked and fixed by the pin member 53, the thrust member is fixed to the flange portion 2b of the hub member 2. 30 and the disc spring 31 can be easily fixed in a relatively non-rotatable manner. Furthermore, the disk plate 3 can be easily assembled to the boss portion 2a of the hub member 2 without adjusting the assembly rotation position of the disk plate 3 with respect to the thrust member 30 fixed so as not to be relatively rotatable. Therefore, in this apparatus 1 in the third embodiment, assembly workability can be greatly improved.

  Further, in this case, the thrust member 30 as the third sliding contact member is inserted through the first plate 51 of the intermediate plate 5 and at least the reference outline of the disk plates 3 and 4 as a pair of outline plates at the tip. A small-diameter portion 30b that is in sliding contact with the disk plate 3, which is a plate, and a large-diameter portion 30c that is larger in diameter than the outer diameter of the small-diameter portion 30b at the proximal end of the small-diameter portion 30b and is provided with a rotation-preventing portion 30a. The outer diameter of the small-diameter portion 30b is at least as large as the inner diameter of the inner peripheral portion 3a of the disc plate 3 that is the reference outer plate of the disc plates 3 and 4 that are the pair of outer plates. And can be provided 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 relative rotation occurs between the hub member 2 and the disk plate 3 due to torque fluctuation, the thrust member 30 can absorb (attenuate) the generated torque fluctuation satisfactorily.

(Fourth embodiment)
In the third embodiment, the thrust member 30 that 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 hub member 2 via the rotation preventing portion 30a. Here, also in the apparatus 1 of the third embodiment, as in the second 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. 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 are formed between the flange portion 2 b of the hub member 2 and the thrust member 30 as in the case of the second embodiment. Between. Incidentally, as described in the second embodiment, the control plate 21 is fixed to the flange portion 2b of the hub member 2 together with the control plate 22 by the pin member 26 so as to be integrally rotatable. Therefore, in the fourth embodiment, the thrust member 30 as the third sliding contact member is fixed to the control plate 21 that rotates integrally with the flange portion 2b of the hub member 2 so as not to be relatively rotatable. Improve assembly workability. Hereinafter, the fourth embodiment will be specifically described.

  In the fourth embodiment, the anti-rotation portion 30 a of the thrust member 30 is provided in the large-diameter portion 30 c and has a protruding shape that protrudes toward the control plate 21 as shown in FIG. 10. The rotation preventing portion 30 a in the fourth embodiment is inserted into an engagement hole 21 a formed in the control plate 21 and fixed to the control plate 21 so as not to be relatively rotatable. Here, the control plate 21 is fixed so as to be integrally rotatable with respect to the flange portion 2 b of the hub member 2. Therefore, also in the fourth embodiment, the thrust member 30 is fixed so as not to rotate relative to the hub member 2 and the disc spring 31 that is the third pressing member. In addition, about another structure, it is the same as that of said 2nd embodiment and said 3rd embodiment.

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

  Subsequently, the thrust member 30 that is the third sliding contact member and the disc spring 31 that is the third pressing member are inserted into the boss portion 2 a of the hub member 2. Then, the rotation preventing portion 30a of the thrust member 30 is inserted into the engagement hole 21a formed in the control plate 21 so that the thrust member 30 and the disc spring 31 cannot be rotated relative to the control plate 21 and thus 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, and the fourth, as in the third embodiment. A disc spring 33 as a pressing member is assembled, and the disc plate 3 is assembled. Here, also in the fourth embodiment, when the disk plate 3 is assembled, the disk plate 3 is mounted on the hub member 2 without adjusting the assembly rotation position with respect to the thrust member 30 as in the third embodiment. The boss 2a is assembled in a state of being inserted.

  Therefore, the torque fluctuation absorber 1 of the fourth embodiment includes the annular control plates 21 and 22 that are integrally connected to the hub member 2 so as to be rotatable integrally therewith, and is arranged around the thrust member 30 that 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, before the intermediate plate 5 (the first plate 51 and the second plate 52) is caulked and fixed by the pin member 53, the control plate 21 is provided. That is, the thrust member 30 and the disc spring 31 can be easily fixed to the hub member 2 that is connected so as to be integrally rotatable so that the thrust member 30 and the disc spring 31 cannot be rotated relative to each other. Furthermore, the disk plate 3 can be easily assembled to the boss portion 2a of the hub member 2 without adjusting the assembly rotation position of the disk plate 3 with respect to the thrust member 30 fixed so as not to be relatively rotatable. Therefore, also in this apparatus 1 in the fourth embodiment, the assembly workability can be greatly improved. About the other effect, the effect similar to said 2nd embodiment and said 3rd embodiment is acquired.

(Modifications of the third embodiment and the fourth embodiment)
In the third embodiment and the fourth embodiment, the disk plate 3 is the reference outer plate among the disk plates 3 and 4 that are a pair of outer plates. The thrust member 30, which is the third sliding contact member arranged on the disk plate 3 side, is provided with a rotation preventing portion 30 a and the engagement hole 2 b 1 provided in the flange portion 2 b of the hub member 2 or the control plate 21. The rotation stopper 30a is engaged with the joint hole 21a.

  In addition to this, as shown in FIG. 11, the anti-rotation part corresponding to the anti-rotation part 30a provided in the thrust member 30 which is the third sliding contact member with respect to the thrust member 11 arranged on the disk plate 4 side. It is also possible to provide 11a. In this case, the uneven rotation preventing portion provided on the thrust member 11 and engaged with the inner peripheral portion of the disk plate 4 is omitted. FIG. 11 shows the case of the apparatus 1 in the third embodiment.

  As described above, when the anti-rotation portion 11a is provided on the thrust member 11, the anti-rotation portion 11a is connected to the flange portion 2b as in the case of the third embodiment and the fourth embodiment. The engagement hole 2b1 or the engagement hole 22a provided in the control plate 22 is engaged. Thereby, the thrust member 11 is fixed to the hub member 2 so as not to rotate relative to the hub member 2 in the same manner as the thrust member 30 in the third embodiment and the fourth embodiment.

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

  In carrying out the present invention, the present invention is not limited to the above embodiments, and various modifications can be employed without departing from the object of the present invention.

  For example, in each of the above embodiments, the disk plate 3 is used as the 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, the disc plate 4 which is one of the pair of outer plates, ie, the disc plates 3 and 4, is used as a 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 that is the first slidable contact member and the thrust member 14 that is the second slidable contact member in the first embodiment and the second embodiment described above are in a plane perpendicular to the rotation axis J. It arrange | positions between the disk plate 4 and the flange part 2b of the hub member 2 so that it may become symmetrical. Alternatively, the thrust member 30 that is the third sliding contact member and the thrust member 32 that 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. Thus, it arrange | positions between the disk plate 4 and the flange part 2b of the hub member 2. FIG. As a result, even when the disk plate 4 is a reference outline plate, the same effects as those of the above embodiments can be obtained.

  Furthermore, in each said embodiment, the coil spring 6 was connected in series as a some elastic member. In this case, the plurality of elastic members are not limited to coil springs, and other forms of spring members may be used, and the plurality of spring members may be connected in series.

DESCRIPTION OF SYMBOLS 1 ... Torque fluctuation absorption device, 2 ... Hub member, 2a ... Boss part, 2b ... Flange part, 2b1 ... Engagement hole, 3 ... Disc plate (outer plate, reference outer plate), 3a ... Inner peripheral part, 3b ... Hole 4, 4 disc plate (outer plate), 4a ... hole, 5 ... intermediate plate, 51 ... first plate, 51a ... inner periphery, 52 ... second plate, 53 ... pin member, 6 ... coil spring (Plural elastic members), 7 ... Spring seat, 8 ... Spring seat, 9 ... Small spring, 10 ... Thrust member (first sliding contact member), 10a ... Non-rotating portion, 10b ... Small diameter portion, 10c ... Large diameter portion , 11 ... Thrust member, 12 ... Belleville spring (first pressing member), 13 ... Support plate, 14 ... Thrust member (second sliding contact member), 14a ... Falling prevention part, 15 ... Belleville spring (second pressing member) 16 Thrust Material: 16a ... Preventing part, 17 ... Support plate, 18 ... Cover plate, 18a ... Hole, 19 ... Friction plate, 19a ... Preventing part, 20 ... Disc spring, 21 ... Control plate, 21a ... Engaging hole, 22 ... control plate, 22a ... engagement hole, 23 ... thrust member (first sliding member), 24 ... disc spring (first pressing member), 25 ... thrust member, 26 ... pin member, 30 ... thrust member (first) Three sliding contact members), 31 ... Disc spring (third pressing member), 32 ... Thrust member (fourth sliding contact member), 33 ... Disc spring (fourth pressing member), A ... Vibration absorbing member, F ... Flywheel (Input-side rotating member), J ... rotating shaft, S ... input shaft (output-side rotating member)

Claims (8)

A torque fluctuation absorbing device that absorbs torque fluctuation generated 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 coupled to the input-side rotating member and spaced 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 rotation member, and a flange portion provided on the boss portion and disposed between the pair of outer plates;
Between the flange portion of the hub member and the pair of outer plates, and connected between the series of elastic members constituting the vibration absorbing member, of the series of elastic members An annular intermediate plate that transmits torque from one elastic member to the other elastic member of the series of elastic members;
The flange portion position, which is the axial position of the flange portion, is
Determined based on the position in the axial direction of a reference outline plate that is one of the pair of outline plates;
The intermediate plate position, which is the axial position of the intermediate plate,
A torque fluctuation absorber that is determined on the basis of the axial position of the reference outer plate. The torque fluctuation absorber is
A cylindrical first slidable contact member assembled to the outer periphery of the boss portion of the hub member, in sliding contact with the boss portion and in sliding contact with the flange portion,
An annular first pressing member that presses the first sliding contact member from the reference outer plate toward the flange portion;
An annular second sliding contact member that is in sliding 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,
The flange portion position is
Determined by the first sliding contact member and the first pressing member,
The intermediate plate position is
The torque fluctuation absorber according to claim 1, which is determined by the second sliding contact member and the second pressing member. The first sliding contact member is
A small diameter portion inserted through the intermediate plate;
A large-diameter portion that is in sliding contact with the flange portion and is provided with a larger diameter than the outer diameter of the small-diameter portion
The outer diameter of the large diameter portion is
The torque fluctuation absorber according to claim 2, wherein the torque fluctuation absorber is provided so as to be larger than an inner diameter of an inner peripheral portion of the intermediate plate. The small diameter portion is
The torque fluctuation absorber according to claim 3, wherein the torque fluctuation absorber is in contact with the inner periphery of the intermediate plate. The magnitude of the thrust load generated when the first sliding contact member is in sliding contact with the flange portion is different from the magnitude of the thrust load generated when the second sliding contact member is in sliding contact with the intermediate plate,
The magnitude of the pressing force by which the first pressing member presses the first sliding contact member against the flange portion, and the magnitude of the pressing force by which the second pressing member presses the second sliding contact member against the intermediate plate. The torque fluctuation absorber according to any one of claims 2 to 4, which are different from each other. The torque fluctuation absorber is
The reference outer plate has a detent portion disposed between at least the reference outer plate and the flange portion of the pair of outer plates and fixed to the flange portion so as not to rotate relative to the flange portion. A cylindrical third sliding contact member in sliding contact with,
An annular third pressing member for pressing the third sliding contact member from the flange portion toward the reference outer plate;
An annular fourth sliding contact member in sliding 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,
The flange portion position is
Determined by the third sliding contact member and the third pressing member,
The intermediate plate position is
The torque fluctuation absorber according to claim 1, which is determined by the fourth sliding contact member and the fourth sliding contact member. The torque fluctuation absorber is
An annular control plate connected to the hub member so as to be integrally rotatable,
The detent portion of the third sliding contact member is
The torque fluctuation absorber according to claim 6, wherein the torque fluctuation absorber is fixed so as not to rotate relative to the control plate. The third sliding contact member is
A small-diameter portion that is inserted through the intermediate plate and is in sliding contact with at least the reference outer plate of the pair of outer plates at the tip;
A large-diameter portion having a larger diameter than the outer diameter of the small-diameter portion at the base end of the small-diameter portion and provided with the detent portion,
The outer diameter of the small diameter portion is
The torque fluctuation absorber according to claim 6 or 7, wherein the torque fluctuation absorber is provided so as to be larger than an inner diameter of at least an inner peripheral portion of the reference outer plate of the pair of outer plates.

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