JP2016014425A - Centrifugal pendulum type vibration absorption device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a degree of freedom of the adjustment of the inertia and a vibration order of a mass body of a centrifugal pendulum type vibration absorption device.SOLUTION: In a centrifugal pendulum type vibration absorption device 20, a resilience force for returning a first mass body 21 to a balanced position is imparted to the first mass body 21 from an elastic body 100 accompanied by the oscillation of the first mass body 21, the resilience force for returning the first mass body 21 which oscillates around a pendulum fulcrum PF1 to the balanced position can be set larger than a resilience force which is originally possessed by the centrifugal pendulum type vibration absorption device 20, the equivalent rigidity of the first mass body 21 of the centrifugal pendulum type vibration absorption device 20 can be thereby set larger, and the inertia of the first mass body 21 can be increased by using a first annular mass body 25 without lowering a vibration order.

Description

  The present invention relates to a centrifugal pendulum type vibration absorber that applies a vibration having a phase opposite to that of a vibration transmitted from a driving device to a rotating element that rotates by power from the driving device.

  Conventionally, a centrifugal pendulum type vibration absorber of this type includes a ring gear and at least two pendulum elements (mass bodies) that swing around a pendulum fulcrum (see, for example, Patent Document 1). In this centrifugal pendulum type vibration absorber, the ring gear and at least two pendulum elements are arranged in the same manner as the planetary gear, and the at least one pendulum element contacts the contact contour of the ring gear so as to roll on the gear teeth of the ring gear. ). As a result, when the pendulum element swings, the ring gear swings around the axis, and an inertia moment (rotational moment) is applied from the ring gear to the pendulum element.

International Publication No. 2012/175213

  According to the conventional centrifugal pendulum vibration absorber, the inertia of the pendulum element (mass body) can be substantially increased, and the vibration damping effect of the centrifugal pendulum vibration absorber can be enhanced. However, the vibration order q of the mass body is expressed as q = √ (K / M) when the equivalent stiffness of the centrifugal pendulum absorber is “K” and the equivalent mass is “M”, and the inertia of the pendulum element Increases the equivalent mass of the pendulum element, the vibration order of the mass body decreases. Therefore, the conventional centrifugal pendulum type vibration absorber has room for improvement in terms of the inertia of the mass body and the degree of freedom in adjusting the vibration order. Such a problem also occurs when the inertia of the pendulum element (mass body) is increased without using the ring gear as described above.

  Therefore, the main object of the present invention is to improve the freedom of adjustment of the inertia and vibration order of the mass body of the centrifugal pendulum type vibration absorber.

The centrifugal pendulum type vibration absorber according to the present invention is:
A centrifugal pendulum type vibration absorber that imparts vibration having a phase opposite to vibration transmitted from the driving device to the rotating element with respect to the rotating element that rotates by power from the driving device,
A mass connected to the rotating element to swing about a pendulum fulcrum;
A restoring force applying means for applying a restoring force for returning the mass body to the balanced position as the mass body swings is provided.

  This centrifugal pendulum type vibration absorber includes a mass body connected to a rotating element so as to swing around a pendulum fulcrum, and imparts a vibration having a phase opposite to that transmitted from a driving device to the rotating element. Is. In this centrifugal pendulum vibration absorber, a restoring force for returning the mass body to the balanced position is applied from the restoring force applying means to the mass body as the mass body swings. As a result, the restoring force to return the mass body swinging around the pendulum fulcrum to the balanced position is made larger than that originally possessed by the centrifugal pendulum absorber, and the equivalent stiffness of the centrifugal pendulum absorber is increased. Can do. Therefore, the inertia of the mass body can be increased without reducing the vibration order, and the vibration order can be increased without reducing the inertia of the mass body. As a result, this centrifugal pendulum vibration absorber can improve the freedom of adjustment of the inertia and vibration order of the mass body. In addition, the deflection angle of the mass body can be adjusted by adjusting the restoring force applied to the mass body from the restoring force applying means.

It is a schematic block diagram of the starting apparatus containing the centrifugal pendulum type vibration absorber which concerns on one Embodiment of this invention. It is a fragmentary sectional view which shows the starting apparatus of FIG. FIG. 3 is a front view of the centrifugal pendulum vibration absorber shown in FIG. 2. FIG. 4 is an enlarged cross-sectional view of the centrifugal pendulum vibration absorber shown in FIGS. 2 and 3. FIG. 4 is a front view of first and second annular mass bodies included in the centrifugal pendulum vibration absorber shown in FIGS. 2 and 3. (A) And (b) is a schematic diagram for demonstrating operation | movement of the centrifugal pendulum type vibration absorber shown in FIG. 2 and FIG. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is an enlarged view which shows the principal part of the centrifugal pendulum type vibration absorber shown in FIG. It is a front view of the centrifugal pendulum type vibration absorber which concerns on other embodiment of this invention. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is a front view of the centrifugal pendulum type vibration absorber which concerns on other embodiment of this invention. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is an enlarged view which shows the principal part of the centrifugal pendulum type vibration absorber shown in FIG. It is a front view of the centrifugal pendulum type vibration absorber which concerns on other embodiment of this invention. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is an enlarged view which shows the principal part of the centrifugal pendulum type vibration absorber shown in FIG. It is a front view of the centrifugal pendulum type vibration absorber which concerns on other embodiment of this invention. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is an enlarged view which shows the principal part of the centrifugal pendulum type vibration absorber shown in FIG. It is a front view of the centrifugal pendulum type vibration absorber which concerns on other embodiment of this invention. It is a front view of a centrifugal pendulum type vibration absorber according to another embodiment of the present invention. It is an enlarged view which shows the principal part of the centrifugal pendulum type vibration absorber shown in FIG.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram of a starting device 1 including a centrifugal pendulum vibration absorber 20 according to an embodiment of the present invention, and FIG. 2 is a partial cross-sectional view showing the starting device 1. The starting device 1 shown in these drawings is mounted on a vehicle including an engine (internal combustion engine) having a cylinder deactivation function as a driving device. In addition to the centrifugal pendulum vibration absorber 20, the crankshaft of the engine is mounted. A front cover 3 as an input member coupled to the front cover 3, a pump impeller (input side fluid transmission element) 4 fixed to the front cover 3 and rotating integrally with the front cover 3, and a turbine rotatable coaxially with the pump impeller 4 An output connected to a runner (output-side fluid transmission element) 5 and a damper device 10 and fixed to an input shaft IS (see FIG. 1) of a transmission which is an automatic transmission (AT) or a continuously variable transmission (CVT). It includes a damper hub 7 as a member, a lock-up clutch 8 that is a single-plate hydraulic clutch, a damper device 10 and the like.

  In the following description, “axial direction” basically extends the center axis (axial center) of the starting device 1 and the damper device 10 (centrifugal pendulum vibration absorber 20), unless otherwise specified. Indicates direction. The “radial direction” is basically the radial direction of the rotating element such as the starting device 1, the damper device 10, and the damper device 10, unless otherwise specified, that is, the center of the starting device 1 or the damper device 10. An extending direction of a straight line extending from the axis in a direction (radial direction) orthogonal to the central axis is shown. Further, “circumferential direction” basically indicates the circumferential direction of the rotating element of the starting device 1 or the damper device 10, that is, the direction along the rotating direction of the rotating element, unless otherwise specified.

  The pump impeller 4 includes a pump shell 40 that is tightly fixed to the front cover 3, and a plurality of pump blades 41 that are disposed on the inner surface of the pump shell 40. The turbine runner 5 includes a turbine shell 50 and a plurality of turbine blades 51 disposed on the inner surface of the turbine shell 50. An inner peripheral portion of the turbine shell 50 is fixed to the damper hub 7 via a plurality of rivets. The pump impeller 4 and the turbine runner 5 face each other, and a stator 6 that rectifies the flow of hydraulic oil (working fluid) from the turbine runner 5 to the pump impeller 4 is coaxially disposed between the pump impeller 4 and the turbine runner 5. The stator 6 has a plurality of stator blades 60, and the rotation direction of the stator 6 is set in only one direction by the one-way clutch 61. The pump impeller 4, the turbine runner 5, and the stator 6 form a torus (annular flow path) for circulating hydraulic oil, and function as a torque converter (fluid transmission device) having a torque amplification function. In the starting device 1, the stator 6 and the one-way clutch 61 may be omitted, and the pump impeller 4 and the turbine runner 5 may function as a fluid coupling.

  The lock-up clutch 8 executes a lock-up that connects the front cover 3 and the damper hub 7, that is, the input shaft IS via the damper device 10, and can release the lock-up. It includes a lockup piston 80 having an annular friction material 81 that engages. As shown in FIG. 2, the lock-up piston 80 is disposed inside the front cover 3 and in the vicinity of the inner wall surface of the front cover 3 on the engine side (right side in FIG. 2), and slides in the axial direction with respect to the damper hub 7. Fits freely. The friction material 81 is attached to the outer peripheral side of the lockup piston 80 and the surface on the front cover 3 side.

  A lockup chamber 85 is defined between the lockup piston 80 (the right side surface in FIG. 2) and the front cover 3. The lockup chamber 85 is supplied with hydraulic oil from a hydraulic control device (not shown) via an oil passage (not shown) formed in the input shaft IS, and the hydraulic oil supplied into the lockup chamber 85 is The lockup chamber 85 flows into a fluid transmission chamber (liquid chamber) 9 in which the pump impeller 4, the turbine runner 5 and the like (torus) are accommodated. Therefore, if the fluid transmission chamber 9 and the lockup chamber 85 are kept at the same pressure, the lockup piston 80 does not move to the front cover 3 side, and the lockup piston 80 is frictionally engaged with the front cover 3. Never do. On the other hand, if the inside of the lockup chamber 85 is depressurized by a hydraulic control device (not shown), the lockup piston 80 moves toward the front cover 3 due to the pressure difference and frictionally engages with the front cover 3. Thereby, the front cover 3 is connected to the damper hub 7 via the damper device 10. The lock-up clutch 8 may be configured as a multi-plate hydraulic clutch.

  As shown in FIGS. 1 and 2, the damper device 10 includes, as a rotating element, an annular drive member (input element) 11 that is coupled so as to rotate integrally with a lockup piston 80 of the lockup clutch 8, and a speed change A plurality of (for example, four) springs including a ring-shaped driven member (output element) 15 connected to the input shaft IS of the machine and arranged as concentric circles at intervals in the circumferential direction as a power transmission element (Elastic body) SP is included. As the spring SP, an arc coil spring made of a metal material wound so as to have an arc extending in an arc shape when no load is applied, or an axis extending straight when no load is applied. Thus, a straight coil spring made of a spirally wound metal material is employed. Further, as the spring SP, a so-called double spring as illustrated may be employed.

  The drive member 11 that is an input element of the damper device 10 has a ring-shaped first input plate member 12 disposed so as to be close to the lock-up piston 80 (front cover 3), and locks up more than the first input plate member 12. An annular second input plate member 13 that is disposed on the pump impeller 4 and the turbine runner 5 side so as to be separated from the piston 80 and is connected to the first input plate member 12 through a plurality of rivets is included.

  As shown in FIG. 2, the first input plate member 12 is rotatably supported by the damper hub 7. The first input plate member 12 includes a plurality of (for example, four) spring support portions 12a that support (guide) the outer peripheral portions of the corresponding springs SP from the front cover 3 (engine) side, and the corresponding springs. A plurality (for example, four) of spring support portions 12b that support (guide) the inner peripheral portion of the SP from the front cover 3 side, and a plurality of (in the radial direction) spring support portions 12a and 12b that extend in the radial direction. For example, four spring contact portions 12c are provided. Further, a plurality of engaging recesses are formed on the outer peripheral portion of the first input plate member 12, and engaging convex portions formed on the outer peripheral portion of the lockup piston 80 are fitted in each engaging recess. Is done. Thus, the first input plate member 12 (drive member 11) is coupled to the lockup piston 80 so as to rotate integrally.

  The second input plate member 13 includes a plurality of (for example, four) spring support portions 13a that support (guide) the outer peripheral portion of the corresponding spring SP from the turbine runner 5 (transmission) side, and the corresponding spring SP. A plurality of (for example, four) spring support portions 13b that support (guide) the inner peripheral portion of the turbine runner 5 from the turbine runner 5 side and a plurality (for example, a plurality of radial support portions) that extend in the radial direction between the spring support portions 13a and 13b that are adjacent in the circumferential direction. 4) spring contact portions 13c.

  When the first and second input plate members 12 and 13 are connected to each other, the spring support portions 12a of the first input plate member 12 face the corresponding spring support portions 13a of the second input plate member 13, and Each spring support portion 12 b of the first input plate member 12 faces the corresponding spring support portion 13 b of the second input plate member 13. The springs SP are supported by the first and second input plate members 12 and 13 constituting the drive member 11, and are spaced in the circumferential direction in the vicinity of the inner peripheral portion of the turbine shell 50 (at equal intervals). line up. Further, in the mounted state of the damper device 10, each spring contact portion 12c of the first input plate member 12 and each spring contact portion 13c of the second input plate member 13 are both between the adjacent springs SP. Abuts against the end of the.

  The driven member 15 is disposed between the first input plate member 12 and the second input plate member 13 of the drive member 11 and is fixed to the damper hub 7 together with the turbine shell 50 of the turbine runner 5 through a plurality of rivets. The Thereby, the driven member 15 is connected to the input shaft IS of the transmission via the damper hub 7. The driven member 15 includes a plurality (for example, four) of spring contact portions 15c that can contact the end portions of the corresponding springs SP. In the mounted state of the damper device 10, each spring contact portion 15 c comes into contact with both ends between adjacent springs SP.

  The centrifugal pendulum vibration absorber 20 is connected to the driven member 15 of the damper device 10 configured as described above, and is disposed inside the fluid transmission chamber 9 filled with hydraulic oil. In the present embodiment, the centrifugal pendulum vibration absorber 20 is configured as a so-called bifilar device, and is supported so as to swing around the first pendulum fulcrum PF1 as shown in FIG. A plurality of (in this embodiment, three) first mass bodies 21 connected to a driven member 15 as a member and each driven member 15 so as to swing around a second pendulum fulcrum PF2. A plurality of (in this embodiment, three) second mass bodies 22. The plurality of first and second mass bodies 22 are arranged at equal intervals (60 ° intervals in this embodiment) so as to be alternately arranged around the axis of the damper device 10, that is, the rotation center RC of the driven member 15. The second mass body 22 is positioned between the two first mass bodies 21 adjacent to each other at an interval in the circumferential direction. The centrifugal pendulum vibration absorber 20 supports the first and second mass bodies 21 and 22 in a swingable manner and has a dedicated support member connected (fixed) to the driven member 15 of the damper device 10. It may be configured.

  As shown in FIGS. 3 and 4, each first mass body 21 includes two first weight bodies 210 and a plurality (four in this embodiment) of first link members 23. The two first weights 210 are each formed by a metal plate in a generally circular arc shape that is symmetric with respect to the outer periphery of the driven member 15 when viewed from the axial direction of the damper device 10 (driven member 15). The damper devices 10 face each other in the axial direction and are connected to each other via a connecting shaft. A plurality of first link members 23 are provided on each of the two first weight bodies 210 so as to be arranged in parallel with each other, and the two first link members 23 paired with each other include two first link members 23. It faces the axial direction of the damper device 10 via the weight body 210.

  One ends (outer ends) of the two first link members 23 facing each other are rotatably connected to the two first weight bodies 210 (first mass bodies 21) via the connecting shaft as a support shaft. The Each connecting shaft includes a rotation center RC of the driven member 15, a center of gravity of the first mass body 21 in a balanced position, and a swing centerline of the first mass body 21 including the first pendulum fulcrum PF1 (centerline of amplitude, diagram) 3 (see the alternate long and short dash line in FIG. 3). The “balance position” is a position where the centrifugal force acting on the mass body as the rotating element rotates and the force acting from the center of gravity acting on the mass body toward the pendulum fulcrum are balanced. This is the position where the component force in the direction perpendicular to the direction from the center of gravity to the center of rotation of the force in the direction from the center of gravity acting on the mass body toward the pendulum fulcrum when the force acts is zero. Further, the other ends (inner ends) of the two first link members 23 facing each other are inserted into connection holes formed in the driven member 15 so as to be symmetric with respect to the swing center line of the first mass body 21. It is rotatably connected to the driven member 15 via a support shaft. Further, each first weight body 210 constituting the first mass body 21 has a rectangular (rectangular) first guide opening extending in the radial direction of the driven member 15 so that the longitudinal direction thereof is along the oscillation center line. (Guide part) 215 is formed.

  Each first mass body 21 is connected to a first annular mass body 25 as an additional mass body. The first annular mass body 25 is formed of a metal plate, and as shown in FIGS. 3 and 5, the first annular portion 250 having an inner diameter and an outer diameter larger than the outer diameter of the driven member 15, and the first annular mass A plurality of (in this embodiment, three) inner protrusions 251 extending radially inward from the inner peripheral surface of the portion 250. The plurality of inner protrusions 251 are formed around the axis of the first annular portion 250 so as to be arranged at equal intervals (in the present embodiment, at intervals of 120 °), and are respectively more than the inner peripheral surface of the first annular portion 250. It has an inner peripheral surface extending in the shape of a small-diameter arc. Furthermore, a first shaft portion 255 is formed on the front and back surfaces of each inner protruding portion 251 so as to be parallel to the axial center of the first annular portion 250 and extend in the opposite direction. In the present embodiment, each first shaft portion 255 has a circular cross section with the same diameter, and is formed integrally with the first annular portion 250 and the inner protruding portion 251. However, a separate first shaft portion 255 may be fixed to the inner protruding portion 251.

  In the first guide opening 215 of each first weight body 210 described above, one first slider 27 having a substantially square cross-sectional shape (a dimension shorter than the length of the first guide opening 215 in the longitudinal direction) is provided. The first guide openings 215 are arranged movably along the longitudinal direction (extending direction) of the first guide openings 215 one by one. Each first slider 27 is made of resin or metal, and as shown in FIG. 3, each of the pair of side surfaces of each first slider 27 facing each other extends in the longitudinal direction of the first guide opening 215. Makes sliding contact with the inner surface. Further, each first shaft portion 255 of the first annular mass body 25 is rotatably supported by the corresponding first slider 27, and the first annular portion 250 and the inner protruding portion 251 are 2 of each first mass body 21. It arrange | positions between the two 1st weight bodies 210. FIG.

  Thus, the first annular mass body 25 is connected via the coupling mechanism 29 constituted by the first guide opening 215 of the first weight body 210, the first slider 27, and the first shaft portion 255 of the first annular mass body 25. Connected to each first mass body 21. When each first mass body 21 is in a balanced position (when the centrifugal pendulum vibration absorber 20 is attached), each first slider 27 is in the radial direction of the corresponding first guide opening 215 as shown in FIG. The axis of the first shaft portion 255 of the first annular mass body 25 that is in contact with a part of the first weight body 210 that forms the inner wall surface on the inside and is supported by each first slider 27 is the first mass body 21. Located on the rocking center line. Furthermore, between each 1st slider 27 and a part of 1st weight body 210 which forms the inner wall surface of the radial direction outer side of each 1st guide opening part 215, both are contact | abutted and 1st mass body 21 is contact | abutted. The elastic body 100 as the restoring force applying means is arranged so that it bends (shrinks) as it swings. In the present embodiment, the elastic body 100 is a disc spring, a leaf spring, a coil spring, or a resin such as rubber having flexibility and oil resistance that functions as a compression spring, and each first mass body 21 is in a balanced position. At some point, it is maintained in an uncompressed state or a compressed state.

  As shown in FIGS. 3 and 4, each second mass body 22 includes two second weight bodies 220 and a plurality (four in the present embodiment) of second link members 24. The two second weight bodies 220 are each formed by a metal plate in a generally arcuate shape that is symmetrical to the left and right along the outer periphery of the driven member 15 when viewed from the axial direction of the damper device 10 (driven member 15). The damper devices 10 face each other in the axial direction and are connected to each other via a connecting shaft. The plurality of second link members 24 are provided on the two second weights 220 so as to be arranged in parallel with each other, and the two second link members 24 that are paired with each other are two second link members 24. It faces the axial direction of the damper device 10 via the weight body 220.

  One ends (outer ends) of the two second link members 24 facing each other are rotatably connected to the two second weight bodies 220 (second mass bodies 22) via the connection shaft as a support shaft. The Each connecting shaft includes a rotation center RC of the driven member 15, a center of gravity of the second mass body 22 in a balanced position, and a swing centerline of the second mass body 22 including the second pendulum fulcrum PF2 (a centerline of amplitude, 3 (see the alternate long and short dash line in FIG. 3). The other end (inner end) of the two second link members 24 facing each other is inserted into a connecting hole formed in the driven member 15 so as to be symmetric with respect to the swing center line of the second mass body 22. It is rotatably connected to the driven member 15 via a support shaft. Further, each second weight body 220 constituting the second mass body 22 has a rectangular (rectangular) second guide opening portion (a rectangular shape) extending in the radial direction of the driven member 15 so that the longitudinal direction thereof is along the oscillation center line. Guide part) 225 is formed.

  In addition, each second mass body 22 is connected to a second annular mass body 26 as an additional mass body. The second annular mass body 26 is formed of a metal plate, and is smaller than the inner diameter of the first annular mass body 25 (first annular portion 250) and has an outer diameter of the driven member 15, as shown in FIGS. A second annular portion 260 having a larger inner diameter and outer diameter, and a plurality (three in the present embodiment) of enlarged diameter portions 261 extending radially outward from the outer peripheral surface of the second annular portion 260; Have The plurality of enlarged diameter portions 261 are formed around the axis of the second annular portion 260 so as to be arranged at equal intervals (in this embodiment, 120 ° intervals), and are larger than the outer peripheral surface of the second annular portion 260, respectively. The outer circumferential surface has a diameter and extends in an arc shape having a slightly smaller diameter than the inner circumferential surface of the first annular portion 250 of the first annular mass body 25. Furthermore, a second shaft portion 265 is formed on the front surface and the back surface of each enlarged diameter portion 261 so as to be parallel to the axis of the second annular portion 260 and extend in the opposite direction. In the present embodiment, each of the second shaft portions 265 has a circular cross section with the same diameter, and is formed integrally with the second annular portion 260 and the enlarged diameter portion 261. However, a separate second shaft portion 265 may be fixed to the enlarged diameter portion 261.

  In the second guide opening 225 of each second weight body 220 described above, there is one second slider 28 having a substantially square cross-sectional shape (dimension shorter than the length of the second guide opening 225 in the longitudinal direction). The second guide openings 225 are movably arranged one by one along the longitudinal direction (extending direction). Each second slider 28 is formed of resin or metal, and as shown in FIG. 3, each of the pair of side surfaces facing each other of each second slider 28 extends in the longitudinal direction of the second guide opening 225. Makes sliding contact with the inner surface. Each second shaft portion 265 of the second annular mass body 26 is rotatably supported by the corresponding second slider 28 and is disposed between the two second weight bodies 220 of each second mass body 22. . Accordingly, the second annular mass body 26 includes the coupling mechanism 30 configured by the second guide opening 225 of each second weight body 220, the second slider 28, and the second shaft portion 265 of the second annular mass body 26. It is connected to each 2nd mass body 22 via. When each second mass body 22 is in a balanced position (when the centrifugal pendulum vibration absorber 20 is attached), each second slider 28 is in the radial direction of the corresponding second guide opening 225 as shown in FIG. The axial center of the second shaft portion 265 of the second annular mass body 26 that is in contact with the inner inner wall surface and supported by the second sliders 28 is located on the oscillation center line of the second mass body 22.

  In the present embodiment, as shown in FIGS. 3 to 5, the first and second annular mass bodies 25 and 26 are configured such that the first annular portion 250 of the first annular mass body 25 is the second annular mass body 26. It arrange | positions between the two 1st weight bodies 210 of each 1st mass body 21, and between the 2nd 2 mass bodies 220 of each 2nd mass body 22 so that the cyclic | annular part 260 and the enlarged diameter part 261 may be enclosed. Further, the inner peripheral surface of the first annular portion 250 is in contact (sliding contact) with the outer peripheral surface of each of the enlarged diameter portions 261 of the second annular mass body 26. Furthermore, the inner peripheral surface of the second annular portion 260 of the second annular mass body 26 comes into contact (sliding contact) with the outer peripheral surfaces of the plurality of projecting portions 15 p formed on the outer peripheral portion of the driven member 15. Thus, the second annular mass body 26 is rotatably supported by the driven member 15 fixed to the damper hub 7, and the first annular mass body 25 is rotatably supported by the second annular mass body 26. In the centrifugal pendulum vibration absorber 20, the inner peripheral surface of the first annular portion 250 of the first annular mass body 25 is brought into contact (sliding contact) with the outer peripheral surface of each of the enlarged diameter portions 261 of the second annular mass body 26. Instead, the inner circumferential surface of each inner protrusion 251 of the first annular mass body 25 and the second annular mass body 26 so that the first annular mass body 25 is rotatably supported by the second annular mass body 26. You may contact | abut with the outer peripheral surface of the 2nd annular part 260. FIG.

  In the centrifugal pendulum type vibration absorber 20 configured as described above, the driven member 15 of the damper device 10 is rotated by the power from the engine, and the first mass body 21 is moved to the first pendulum as the driven member 15 rotates. It swings around the fulcrum PF1. When the first mass body 21 swings to one side in the swing direction, as shown in FIGS. 6A and 6B, the first mass body 21 is directed toward the rotation center RC of the driven member 15 along the swing center line. And translate so as to be separated from the swing center line along a direction orthogonal to the swing center line. With such movement (swing) of the first mass body 21, the first slider 27 in the first guide opening 215 of the first weight body 210 has an inner wall surface on the radially outer side of the first guide opening 215. It moves with respect to the 1st weight body 210 (1st mass body 21) so that it may approach, and the elastic body 100 is compressed. Thereby, as the first mass body 21 swings, each first slider 27 has a movement amount (elastic body) of the first slider 27 in the longitudinal direction (extending direction) of the first guide opening 215. In accordance with the compression amount of 100, a thrust (see the dotted arrow in FIG. 6B) toward the rotation center RC along the longitudinal direction of the first guide opening 215 is applied from the corresponding elastic body 100.

  Further, when the first mass body 21 reaches one end in the swing range (when the swing angle is maximized), the first mass body 21 moves outward from the rotation center RC side of the driven member 15 along the swing center line and swings. The translation is performed so as to approach the oscillation center line along a direction orthogonal to the movement center line. As the first mass body 21 moves (swings), the first slider 27 in the first guide opening 215 receives the thrust from the elastic body 100 and is radially inward of the first guide opening 215. It moves with respect to the 1st weight body 210 (1st mass body 21) so that it may approach the inner wall surface of this, and the compression of the elastic body 100 is cancelled | released. After the first slider 27 comes into contact with the radially inner wall surface of the first guide opening 215, the first mass body 21 swings to the other side in the swing direction through the balanced position.

  As the first mass body 21 moves (swings) as described above, the first shaft portion 255 of the first annular mass body 25 supported by the first slider 27 is pivoted with respect to the moving first slider 27. Rotate around the heart. As a result, the first annular mass body 25 connected to each first mass body 21 swings around the rotation center RC of the driven member 15 as the rotating element as the first mass body 21 swings. (Refer to FIG. 6B). Then, each first mass body 21 is brought into a balanced position with respect to the first annular mass body 25 swinging around the rotation center RC by a reaction force of the thrust applied from the elastic body 100 to the first slider 27. It is energized in the return direction. That is, when the first mass body 21 swings around the first pendulum fulcrum PF1, the first mass body 21 has a restoring force for returning to the balanced position (see the white arrow in FIG. 6B). ) Is applied from the elastic body 100. Thereby, in the centrifugal pendulum type vibration absorber 20, the centrifugal pendulum type vibration absorber 20 originally has a restoring force to return the first mass body 21 that swings around the first pendulum fulcrum PF1 to the balanced position ( It is possible to increase the restoring force when the elastic body 100 is not present (see the black thick arrow in FIG. 6B).

  Similarly, when the driven member 15 of the damper device 10 is rotated by the power from the engine, the second mass body 22 swings around the second pendulum fulcrum PF2 as the driven member 15 rotates. When the second mass body 22 swings to one side in the swing direction, the second mass body 22 moves toward the rotation center RC of the driven member 15 along the swing center line and along the direction orthogonal to the swing center line. Translate away from the swing center line. With such movement (swing) of the second mass body 22, the second slider 28 in the second guide opening 225 of the second weight body 220 has an inner wall surface on the radially outer side of the second guide opening 225. It moves with respect to the 2nd weight body 220 (2nd mass body 22) so that it may approach.

  In addition, when the second mass body 22 reaches one end in the swing range (when the swing angle is maximized), the second mass body 22 moves from the rotational center RC side of the driven member 15 toward the outside along the swing center line and swings. The translation is performed so as to approach the oscillation center line along a direction orthogonal to the movement center line. As the second mass body 22 moves (swings), the second slider 28 in the second guide opening 225 moves closer to the inner wall surface on the radially inner side of the second guide opening 225. It moves relative to the double weight body 220 (second mass body 22). After the second slider 28 contacts the inner wall surface on the radially inner side of the second guide opening 225, the second mass body 22 swings to the other side in the swinging direction through the balanced position. As the second mass body 22 moves (swings) as described above, the second shaft portion 265 of the second annular mass body 26 supported by the second slider 28 is pivoted with respect to the moving second slider 28. Rotate around the heart. As a result, the second annular mass body 26 connected to each second mass body 22 swings around the rotation center RC of the driven member 15 as the rotating element as the second mass body 22 swings. Move).

  As a result, in the centrifugal pendulum vibration absorber 20, when the first annular mass body 25 swings around the rotation center RC of the driven member 15 as the plurality of first mass bodies 21 swing, An inertia moment (rotational moment) is applied to the mass body 21 from the first annular mass body 25. Further, when the second annular mass body 26 swings around the rotation center RC of the driven member 15 with the swing of each second mass body 22, the second annular mass with respect to each second mass body 22. A moment of inertia is applied from the body 26. Thereby, the inertia of the 1st and 2nd mass bodies 21 and 22 can be increased, and the vibration damping effect of the centrifugal pendulum type vibration absorber 20 can be improved more.

  Here, if the equivalent stiffness of the centrifugal pendulum vibration absorber is “K” and the equivalent mass is “M”, the vibration order q of the mass body is expressed as q = √ (K / M). When the inertia of the body increases, the equivalent mass M increases accordingly, and the vibration order q of the mass body decreases. Based on this, in the centrifugal pendulum vibration absorber 20, the first mass bodies 21 and the first mass bodies 21 are connected so that the vibration order of the first mass bodies 21 connected to the first annular mass body 25 is not decreased so as to increase the inertia. The elastic body 100 is disposed between the first annular mass body 25. As a result, as described above, the restoring force for returning the first mass body 21 oscillating around the first pendulum fulcrum PF1 to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20. Therefore, the equivalent rigidity K of the first mass body 21 can be further increased. Therefore, in the centrifugal pendulum vibration absorber 20, it is possible to increase the inertia of the first mass body 21 without reducing the vibration order (first vibration order).

  Further, the engine to which the starting device 1 including the centrifugal pendulum vibration absorber 20 is connected has a cylinder deactivation function. That is, when all cylinder operation of the engine is executed (when cylinder deactivation is not performed) and when reduced cylinder operation (cylinder deactivation) is performed (for example, in a three cylinder engine or a four cylinder engine, two cylinder operation (one cylinder deactivation or The order of vibrations transmitted from the engine to the driven member 15 of the damper device 10 is different from that when the two cylinders are deactivated). Therefore, in the centrifugal pendulum vibration absorber 20, the vibration order (first vibration order) of each first mass body 21 connected to the first annular mass body 25 is reduced from the engine to the driven member 15 ( The first mass body 21 (first weight body 210, first link) so as to coincide with the order of vibration transmitted to the damper device 10) (for example, the second order for a four-cylinder engine and the first order for a three-cylinder engine). Specifications of the member 23 and the first slider 27), the first annular mass body 25, and the elastic body 100 are determined. In the centrifugal pendulum vibration absorber 20, the specifications of the second mass body 22 (the second weight body 220, the second link member 24, and the second slider 28) and the second annular mass body 26 are the second annular mass body. The vibration order (second vibration order) of each second mass body 22 connected to the engine 26 is the vibration order (for example, primary) transmitted from the engine to the driven member 15 (damper device 10) when the reduced cylinder operation is performed. ).

  As described above, the centrifugal pendulum vibration absorber 20 is connected to the first annular mass body 25 by adjusting the specifications of the first and second annular mass bodies 25 and 26 and the rigidity (spring constant) of the elastic body 100. The vibration order (first vibration order) of each first mass body 21 and the vibration order (second vibration order) of each second mass body 22 connected to the second annular mass body 26 are easily obtained. Can be different. Further, the first annular mass body 25 connected to the first mass body 21 corresponding to the higher-order vibration is replaced with the second annular mass body 26 connected to the second mass body 22 corresponding to the lower-order vibration. By arrange | positioning around, the rotation radius of the 1st annular mass body 25, ie, the moment of inertia provided to the 1st mass body 21 from the 1st annular mass body 25 can be enlarged more. When the vibration orders of the first and second mass bodies 21 and 22 are set, the first and second mass bodies 21 are generated by centrifugal hydraulic pressure (centrifugal fluid pressure) generated in the fluid transmission chamber 9 as the engine rotates. , 22 and the forces acting on the first and second annular mass bodies 25, 26 are preferable.

  Next, the operation of the starting device 1 configured as described above will be described.

  When the lock-up clutch 8 of the starting device 1 is released, as shown in FIG. 1, torque (power) from the engine as the prime mover is applied to the front cover 3, the pump impeller 4, and the turbine runner 5. Then, the signal is transmitted to the input shaft IS of the transmission via the path of the damper hub 7. Further, when lockup is executed by the lockup clutch 8 of the starter 1, as shown in FIG. 1, the torque (power) from the engine is applied to the front cover 3, the lockup clutch 8 (lockup piston 80). ), The transmission member 11, the spring SP, the driven member 15, and the damper hub 7 are transmitted to the input shaft IS of the transmission.

  When the lockup clutch 8 is executing the lockup, when the drive member 11 connected to the front cover 3 is rotated by the lockup clutch 8 as the engine rotates, the spring contact portion of the first input plate member 12 is rotated. 12c and the spring contact portion 13c of the second input plate member 13 press one end of the corresponding spring SP, and the other end of each spring SP presses the spring contact portion 15c of the corresponding driven member 15. Thereby, torque from the engine transmitted to the front cover 3 is transmitted to the input shaft IS of the transmission, and torque fluctuations from the engine are attenuated (absorbed) mainly by the spring SP of the damper device 10. The Further, in the starting device 1, when the damper device 10 connected to the front cover 3 by the lock-up clutch 8 rotates together with the front cover 3 along with the lock-up, the driven member 15 of the damper device 10 also rotates around the axis of the starting device 1. One of the first and second mass bodies 21 and 22 constituting the centrifugal pendulum vibration absorber 20 is rotated with respect to the driven member 15 according to the number of rotations of the driven member 15. Will swing.

  That is, when the lock-up and the all-cylinder operation of the engine are executed, each first mass body 21 of the centrifugal pendulum type vibration absorber 20 swings around the pendulum fulcrum PF1 in the fluid transmission chamber 9, and accordingly, the first annular body The mass body 25 swings around the rotation center RC of the driven member 15 to apply an inertia moment to each first mass body 21. As a result, vibration having a phase opposite to the vibration (resonance) transmitted to the driven member 15 from the engine operated by all cylinders is applied from the centrifugal pendulum vibration absorber 20 to the driven member 15, and the front cover 3 and the damper hub 7 are The vibration can be attenuated (absorbed) also by the centrifugal pendulum vibration absorber 20. Further, the inertia of each first mass body 21 is increased by the moment of inertia from the first annular mass body 25, so that the vibration damping effect of the centrifugal pendulum type vibration absorber 20 during all cylinder operation of the engine can be further improved. Then, by disposing the elastic body 100 between each first mass body 21 and the first annular mass body 25, the first mass body 21 that swings around the first pendulum fulcrum PF1 is returned to the balanced position. It is possible to increase the inertia of the first mass body 21 using the first annular mass body 25 without increasing the restoring force to be increased and reducing the vibration order (first vibration order).

  In addition, when the lockup and the reduced-cylinder operation of the engine are executed, each second mass body 22 of the centrifugal pendulum vibration absorber 20 swings around the pendulum fulcrum PF2 in the fluid transmission chamber 9, and accordingly, the second annular body The mass body 26 swings around the rotation center RC of the driven member 15 to apply an inertia moment to each second mass body 22. As a result, a vibration having a phase opposite to the vibration (resonance) transmitted from the engine operated in the reduced cylinder operation to the driven member 15 is applied from the centrifugal pendulum type vibration absorber 20 to the driven member 15, and the front cover 3 and the damper hub 7 are The vibration can be attenuated (absorbed) also by the centrifugal pendulum vibration absorber 20. In this case as well, the inertia of each second mass body 22 is increased by the moment of inertia from the second annular mass body 26, and the vibration damping effect of the centrifugal pendulum type vibration absorber 20 during the reduced cylinder operation of the engine can be further improved. it can.

  As described so far, in the centrifugal pendulum type vibration absorber 20 of the starting device 1, the restoring force for returning to the balanced position as the first mass body 21 swings is an elastic body (restoring force applying means). 100 to the first mass body 21. Thereby, the restoring force for returning the first mass body 21 oscillating around the first pendulum fulcrum PF1 to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20, so that the centrifugal pendulum vibration absorption is achieved. The equivalent rigidity of the first mass body 21 of the device 20 can be further increased. Therefore, the centrifugal pendulum vibration absorber 20 can increase the inertia of the first mass body 21 using the first annular mass body 25 without reducing the vibration order (first vibration order). The degree of freedom of adjusting the inertia and vibration order of the one mass body 21 can be improved. Furthermore, it is possible to adjust the deflection angle of the first mass body 21 by adjusting the restoring force applied from the elastic body 100 to the first mass body 21, that is, the rigidity (spring constant) of the elastic body 100. .

  Further, in the centrifugal pendulum vibration absorber 20, when the first annular mass body 25 swings around the rotation center RC with the swing of the first mass body 21, the first mass body 21 has a first An inertia moment (rotation moment) is applied from the annular mass body 25, and the second mass body 22 is swung around the rotation center RC as the second mass body 22 is swung. In contrast, a moment of inertia (rotation moment) is applied from the second annular mass body 26. Thereby, the inertia of the 1st and 2nd mass bodies 21 and 22 can be increased, and it becomes possible to improve the vibration damping effect of the centrifugal pendulum type vibration absorber 20 more. The inertia of the first mass body 21 is increased by applying a restoring force for returning the elastic body 100 to the balanced position with respect to the first mass body 21 having a higher vibration order than the second mass body 22. By doing so, it is possible to satisfactorily suppress (maintain high) the vibration order of the first mass body 21 from being lowered.

  Furthermore, in the centrifugal pendulum vibration absorber 20, the vibration order of the first mass body 21 and the vibration order of the second mass body 22 can be easily made different as described above. Therefore, even if the order of vibration transmitted from the engine to the damper device 10 (driven member 15) is changed in accordance with switching between all cylinder operation and reduced cylinder operation, the first or second mass bodies 21 and 22 are driven. The vibration of the driven member 15 can be satisfactorily damped by swinging the member 15 and applying a vibration having a phase opposite to the vibration from the engine to the driven member 15. As a result, the vibration transmitted from the engine to the driven member 15 is satisfactorily attenuated both when the all-cylinder operation of the engine is performed (when cylinder deactivation is not performed) and when the reduced cylinder operation (cylinder deactivation) is performed. be able to.

  Further, in the centrifugal pendulum vibration absorber 20, the connection mechanism 29 that connects each first mass body 21 and the first annular mass body 25 as the additional mass body includes each first weight body constituting the first mass body 21. 210, a first guide opening (guide portion) 215 formed to extend in the radial direction of the driven member 15, and a first guide opening extending from the first annular mass body 25 and via the first slider 27. And a first shaft portion 255 that is rotatably guided by 215 and is movable in the extending direction (longitudinal direction) of the first guide opening 215. As a result, the first annular mass body 25 can be swung around the rotation center RC when the first mass body 21 is swung around the first pendulum fulcrum PF1 while the connecting mechanism 29 is made compact. It becomes possible. The elastic body 100 as the restoring force applying means is a part of the first weight body 210 that forms the first slider 27 (first shaft portion 255) and the radially inner wall surface of the first guide opening 215 in the radial direction. Between the first guide opening 215 and the first guide opening 215. In this way, if the elastic body 100 as the restoring force applying means is disposed between the first mass body 21 and the first annular mass body 25 so as to bend as the first mass body 21 swings, the elastic body 100. From the reaction force of the thrust applied to the first slider 27, the first mass body 21 is urged in the direction of returning the first mass body 21 to the balanced position with respect to the first annular mass body 25 swinging around the rotation center RC. Is possible.

  Further, the first and second shaft portions 255 and 265 are rotatably supported, and the first and second sliders 27 and 28 guided by the first or second guide opening portions 215 and 225 are used. When the first mass body 21 and the second mass body 22 swing, the first annular mass body 25 and the second annular mass body 26 can be smoothly swung around the rotation center RC of the driven member 15. it can. In addition, since the contact area between the first slider 27 and the first guide opening 215 and the contact area between the second slider 28 and the second guide opening 225 can be increased, the durability of the coupling mechanisms 29 and 30 can be increased. It becomes possible to improve the property. However, the first slider 27 is omitted from the coupling mechanism 29, and the coupling mechanism 29 is so supported that the first shaft portion 255 of the first annular mass body 25 is directly supported by the first guide opening 215 of the first mass body 21. It may be configured. In this case, the elastic body 100 is positioned between the first shaft portion 255 and a part of the first weight body 210 that forms the radially inner wall surface of each first guide opening 215. What is necessary is just to arrange | position in 1 guide opening part 215. FIG. Further, the second slider 28 is omitted from the coupling mechanism 30, and the coupling mechanism 30 is configured so that the second shaft portion 265 of the second annular mass body 26 is directly supported by the second guide opening 225 of the second mass body 22. It may be configured.

  In the centrifugal pendulum type vibration absorber 20, it is elastic so as to bend between the second mass body 22 and the second annular mass body 26 (within the second guide opening 225) as the second mass body 22 swings. A body may be arranged and a restoring force for returning to the balanced position as the second mass body 22 swings may be applied from the elastic body to the second mass body 22. In this case, the elastic body as the restoring force applying means is the second slider 28 (second shaft portion 265) and a part of the second weight body 220 that forms the radially inner wall surface of the second guide opening 225. It is good to arrange | position in the 2nd guide opening part 225 so that it may be located between. In the centrifugal pendulum vibration absorber 20, the first and second guide openings may be formed in the first and second annular mass bodies 25 and 26 (at least one of them), and the first and second masses may be formed. The first or second shaft portion may be formed on the bodies 21 and 22 (at least one of them). In such a case, the elastic body 100 includes at least one of the first and second sliders 27 and 28 (first and second shaft portions) and an inner wall surface on the radially outer side of the first and second guide openings. May be disposed in at least one of the first and second guide openings so as to be positioned between a part of at least one of the first and second annular mass bodies 25 and 26 forming the.

  Further, when the order of vibration transmitted from the driving device connected to the starting device 1 to the driven member 15 as the rotating element changes in three or more stages, the vibration is added to the first and second mass bodies 21 and 22. While using a further mass body, the additional mass body may be connected to at least one of the plurality of mass bodies. Further, depending on the weights of the first and second mass bodies 21 and 22, one of the first and second annular mass bodies 25 and 26 may be omitted. Further, by using the first and second annular mass bodies 25 and 26 formed in an annular shape, the centrifugal force acting on both of the first and second annular mass bodies 25 and 26 with respect to the oscillation around the rotation center RC. Although the influence of (centrifugal oil pressure) can be eliminated, at least one of the first and second annular mass bodies 25 and 26 may be replaced with a plurality of additional mass bodies. In this case, each of the additional mass bodies may be connected to the two first or second mass bodies 21 and 22 arranged at intervals in the circumferential direction.

  FIG. 7 is a front view of a centrifugal pendulum vibration absorber 20B according to another embodiment of the present invention, and FIG. 8 is an enlarged view showing a main part of the centrifugal pendulum vibration absorber 20B. Note that among the components of the centrifugal pendulum vibration absorber 20B, the same elements as those of the above-described centrifugal pendulum vibration absorber 20 are denoted by the same reference numerals, and redundant description is omitted.

  In the centrifugal pendulum vibration absorber 20B shown in FIG. 7, a coil spring (tensile spring) is employed as the elastic body (restoring force applying means) 100B. The elastic body 100B uses the first mass body 21 as a rotating element and a support member. One pair is disposed between the pair of first link members 23B coupled to the driven member 15 as one, and one is disposed between the pair of second link members 24B coupling the second mass body 22 to the driven member 15. Placed one by one. As shown in the drawing, each first link member 23B has an L-shape and has a protruding portion 23p extending so as to be orthogonal to the longitudinal direction. The pair of first link members 23B that are paired in parallel with each other are attached to the driven member 15 so that the protruding portions 23p face each other. Furthermore, one end of the elastic body 100B is connected to one protrusion 23p of the two first link members 23B that make a pair, and the other end of the elastic body 100B is connected to the protrusion 23p of the other first link member 23B. The Similarly, each second link member 24B also has an L shape and has a protruding portion 24p extending so as to be orthogonal to the longitudinal direction. A pair of second link members 24B that are paired in parallel with each other are attached to the driven member 15 so that the protruding portions 24p face each other. Furthermore, one end of the elastic body 100B is connected to one protrusion 24p of the two second link members 24B that make a pair, and the other end of the elastic body 100B is connected to the protrusion 24p of the other second link member 24B. The

  In the centrifugal pendulum vibration absorber 20B configured as described above, when the first mass body 21 swings from the balance position to one side in the swing direction, the pair of first link members 23B are parallel to each other as shown in FIG. Rotate around the connecting shaft so as to be inclined with respect to the swing center line (see the one-dot chain line in FIG. 8). Thereby, the protrusions 23p of the pair of first link members 23B are separated from each other, and the elastic body 100B is pulled and extended by the protrusions 23p on both sides. As a result, as the first mass body 21 swings, the pair of first link members 23B has a pair of first link members corresponding to the extension amount of the elastic body 100B (interval between the protruding portions 23p). A restoring force for returning 23B and the first mass body 21 to the balanced position is applied from the corresponding elastic body 100B. When the first mass body 21 reaches one end in the swing range (when the swing angle is maximized), the first mass body 21 swings toward the other side in the swing direction, and the pair of first link members 23B has the centrifugal pendulum type vibration absorption. The device 20B is rotated around the connecting shaft so as to be parallel to the swing center line by the original (unique) restoring force and the restoring force from the elastic body 100B. Similarly, in the centrifugal pendulum vibration absorber 20B, as the second mass body 22 swings, the elastic body 100B expands with respect to the pair of second link members 24B (the interval between the protrusions 24p). Thus, a restoring force for returning the pair of second link members 24B and the second mass body 22 to the balanced position is applied from the corresponding elastic body 100B.

  As described above, in the so-called bifilar centrifugal pendulum vibration absorber 20B, a pair of first and second mass bodies 21 and 22 (at least one of them) for connecting to the driven member (support member) 15 is used. Even if the elastic body 100B is disposed between the first and second link members 23B and 24B, a restoring force for returning to the balanced position can be applied from the elastic body 100B to the first and second mass bodies. As a result, the inertia of the first and second mass bodies 21 and 22 can be increased using the first and second annular mass bodies 25 and 26 without reducing the first and second vibration orders. Become.

  The protrusions 23p and 24p may be omitted from the first and second link members 23B and 24B. Further, the elastic body 100B may be provided only on one of the first and second mass bodies 21 and 22. Further, the first and second annular mass bodies 25 and 26 may be omitted as in the centrifugal pendulum vibration absorber 20B ′ shown in FIG. Further, in the centrifugal pendulum vibration absorbers 20B and 20B ′, an elastic body 100B disposed between the pair of first link members 23B and an elastic body 100B disposed between the pair of second link members 24B. Specifications (spring constant, etc.) may be varied. Further, in the centrifugal pendulum vibration absorber 20B ′, the specifications of the first and second mass bodies 21 and 21 may be the same.

  FIG. 10 is a front view of a centrifugal pendulum vibration absorber 20C according to another embodiment of the present invention. Note that among the components of the centrifugal pendulum vibration absorber 20C, the same elements as those of the above-described centrifugal pendulum vibration absorber 20 are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20C shown in FIG. 10 includes a plurality of pendulum mass bodies 21C that have the same specifications and are arranged to be spaced apart in the circumferential direction. Each pendulum mass body 21C is connected to a driven member 15 as a support member so as to swing around a pendulum fulcrum PF via a plurality of link members (not shown). Further, an annular mass body (additional mass body) 25C is coupled to each pendulum mass body 21C via a coupling mechanism 29. In the centrifugal pendulum vibration absorber 20C, an elastic body (restoring force applying means) 100C made of a resin such as a coil spring, a disc spring, a leaf spring, or rubber having flexibility and oil resistance has a plurality of pendulum mass bodies 21C. It arrange | positions between the two pendulum mass bodies 21C adjacent to each other so that it may be bent with rocking | fluctuation. Thus, even if the elastic body 100C is disposed between two adjacent pendulum mass bodies 21C, a restoring force for returning to the balanced position can be applied from the elastic body 100C to the pendulum mass bodies 21C on both sides. It becomes possible. As a result, it is possible to increase the inertia of the pendulum mass body 21C using the annular mass body 25C without reducing the vibration order. In the centrifugal pendulum vibration absorber 20C, the annular mass body 25C may be omitted.

  FIG. 11 is a front view of a centrifugal pendulum vibration absorber 20D according to still another embodiment of the present invention. Note that among the components of the centrifugal pendulum vibration absorber 20D, the same elements as those of the above-described centrifugal pendulum vibration absorber 20 are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20D shown in FIG. 11 includes a plurality (here, six) of pendulum mass bodies 21D and an annular mass body 25D as an additional mass body connected to each pendulum mass body 21D. The pendulum mass body 21 </ b> D has two weight bodies 210 </ b> D formed so as to have a substantially fan-shaped cross-sectional shape by a metal plate. The two weights 210D have one connecting shaft 230 facing each other in the axial direction of the damper device via a driven member 15D as a supporting member and fixed to a tapered base end (a position of the fan). Are connected to each other. The connecting shaft 230 is inserted into one of a plurality of connecting holes formed at equal intervals around the shaft center on the outer peripheral portion of the driven member 15D, whereby each pendulum mass body 21D swings with respect to the driven member 15D. Connected freely. Each weight 210D has a rectangular (rectangular) guide opening (guide portion) extending in the radial direction of the driven member 15D so that the longitudinal direction thereof is along the oscillation center line (see the alternate long and short dash line in FIG. 11). 215 is formed.

  The annular mass body 25D is formed of a metal plate, and has an annular portion 250D having an inner diameter and an outer diameter larger than the outer diameter of the driven member 15D, and is annular with respect to the front and back surfaces of the annular portion 250D, as shown in FIG. And a plurality of (here, six on one side, twelve in total) shaft portions 25s disposed at equal intervals around the axis of the mass body 25D. A pair of shaft portions 25s corresponding to one pendulum mass body 21D extends from the front surface and the back surface of the annular portion 250D in parallel and opposite to each other in parallel with the axis of the annular mass body 25D. Further, the inner peripheral surface of the annular portion 250D of the annular mass body 25D comes into contact (sliding contact) with the outer peripheral surfaces of the plurality of protruding portions 15p formed on the outer peripheral portion of the driven member 15D. Thereby, the annular mass body 25D is rotatably supported by the driven member 15D fixed to the damper hub 7.

  Similar to the above-described centrifugal pendulum vibration absorber 20, the first guide opening 215 of each weight 210D has a substantially square cross-sectional shape (a dimension shorter than the length of the first guide opening 215 in the longitudinal direction). Each of the sliders 270 having s is arranged so as to be movable along the longitudinal direction (extending direction) of the first guide opening 215. Each shaft portion 25s of the annular mass body 25D is rotatably supported by a corresponding slider 270, and the annular portion 250D is disposed between the two weight bodies 210D of each pendulum mass body 21D. Accordingly, the annular mass body 25D is connected to each pendulum mass body 21D via the connection mechanism 29 configured by the first guide opening 215 of the weight body 210D, the slider 270, and the shaft portion 25s of the annular mass body 25D. .

  In the centrifugal pendulum vibration absorber 20D, the pendulum mass body is in contact with both the slider 270 and a part of the weight body 210D that forms the radially inner wall surface of each first guide opening 215. The elastic body 100D as the restoring force applying means is arranged so as to bend (shrink) as 21D swings. In the example of FIG. 11, the elastic body 100D is a coil spring, and is maintained in an uncompressed state or a compressed state when each pendulum mass body 21D is in a balanced position. The elastic body 100D may be a disc spring, a leaf spring, or a resin such as rubber having flexibility and oil resistance.

  Also in the centrifugal pendulum type vibration absorber 20D configured as described above, as the pendulum mass body 21D swings, the restoring force for returning to the balanced position is changed from the elastic body (restoring force applying means) 100D to the pendulum mass body. To 21D. As a result, the restoring force for returning the pendulum mass body 21D swinging around the pendulum fulcrum PF to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20D, and the equivalent of the centrifugal pendulum vibration absorber 20D is obtained. The rigidity can be further increased. Therefore, also in the centrifugal pendulum vibration absorber 20D, it is possible to increase the inertia of the pendulum mass body 21D using the annular mass body 25D without reducing the vibration order, and the inertia and vibration order of the pendulum mass body 21D can be increased. The degree of freedom of adjustment can be improved. Furthermore, the swing angle of the pendulum mass body 21D can be adjusted by adjusting the restoring force applied from the elastic body 100D to the pendulum mass body 21D, that is, the rigidity (spring constant) of the elastic body 100D.

  FIG. 12 is a front view of a centrifugal pendulum vibration absorber 20E according to another embodiment of the present invention, and FIG. 13 is an enlarged view showing a main part of the centrifugal pendulum vibration absorber 20E. Of the constituent elements of the centrifugal pendulum vibration absorber 20E, the same elements as those of the centrifugal pendulum vibration absorbers 20 and 20D described above are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20E shown in FIG. 12 includes a plurality (here, six) of pendulum mass bodies 21E and an annular mass body 25E as an additional mass body connected to each pendulum mass body 21E. The pendulum mass body 21E has two weight bodies 210E formed by a metal plate so as to have a substantially fan-like cross-sectional shape, similar to the above-described pendulum mass body 21D. The two weights 210E have a single connecting shaft 230 which is opposed to the axial direction of the damper device via a driven member 15E as a supporting member and is fixed to a tapered base end (a position of the fan). Are connected to each other. The connecting shaft 230 is inserted into any of a plurality of connecting holes formed at equal intervals on the outer peripheral portion of the driven member 15E, whereby each pendulum mass body 21E has a pendulum fulcrum PF (the axis of the connecting shaft 230). It is connected to the driven member 15E so as to swing around.

  The annular mass body 25E is formed of a metal plate and includes an annular portion 250E having an inner diameter and an outer diameter larger than the outer diameter of the driven member 15E as shown in FIG. The annular portion 250E is disposed between the two weights 210E of each pendulum mass body 21E. Further, the inner peripheral surface of the annular portion 250E comes into contact (sliding contact) with the outer peripheral surfaces of the plurality of projecting portions 15p formed on the outer peripheral portion of the driven member 15E so as to be positioned in the vicinity of the connecting hole. Thereby, the annular mass body 25E is rotatably supported by the driven member 15E. The annular mass body 25E is coupled to each pendulum mass body 21E via a coupling mechanism 29 configured by the first guide opening 215 of the weight body 210E, the slider 270, and the shaft portion 25s of the annular mass body 25E.

  Further, in the centrifugal pendulum type vibration absorber 20E, a coil spring, a disc spring, a leaf spring, or a flexible member is bent between the driven member 15E and each pendulum mass body 21E so as to be bent with the swing of the pendulum mass body 21E. An elastic body (compression spring) 100E made of a resin such as rubber having heat resistance and oil resistance is disposed. That is, as shown in FIG. 13, in each weight body 210E, an arc-shaped elastic body accommodating portion (for example, opening) 211 is symmetric with respect to the swing center line (see the alternate long and short dash line in FIG. 13) and the pendulum fulcrum It is located outside the PF (axial center of the connecting shaft 230) in the radial direction of the driven member 15E and protrudes radially outward (opposite the pendulum fulcrum PF and the rotation center RC). . In addition, an arcuate elastic body receiving window (opening) 151 is symmetric with respect to the swing center line of the pendulum mass body 21E at the protruding portion 15p of the driven member 15E, and radially outward (pendulum fulcrum PF or rotation). It is formed so as to be convex on the side opposite to the center RC. The circumferential lengths of the elastic body accommodating portion 211 and the elastic body accommodating window 151 are the same length according to the natural length of the elastic body 100E, and when each pendulum mass body 21E is in a balanced position, The elastic body accommodating portion 211 and the elastic body accommodating window 151 of the driven member 15E corresponding to both overlap with each other when viewed from the axial direction of the centrifugal pendulum vibration absorber 20E.

  The elastic body 100E is disposed in the elastic body accommodating portion 211 of the two (a pair) weights 210E constituting the pendulum mass body 21E and the elastic body accommodating window 151 of the protruding portion 15p corresponding to the pendulum mass body 21E. Thus, it is located outside the pendulum fulcrum PF in the radial direction of the driven member 15E. When each pendulum mass body 21E is in a balanced position, both ends of the elastic body 100E abut both of a part of the weight body 210E (pendulum mass body 21E) and a part of the driven member 15E. That is, when each pendulum mass body 21 </ b> E is in a balanced position, one end of the elastic body 100 </ b> E is part of the weight body 210 </ b> E that forms a wall surface on one end side in the circumferential direction of the elastic body housing portion 211 and the elastic body housing window 151. The other end of the driven member 15E that forms the wall surface on one end side in the circumferential direction is in contact with the other end of the elastic body 100E, and the weight body 210E that forms the wall surface on the other end side in the circumferential direction of the elastic body accommodating portion 211 And a part of the driven member 15E that forms the wall surface on the other end side in the circumferential direction of the elastic body receiving window 151.

  In the centrifugal pendulum type vibration absorber 20E configured as described above, when each pendulum mass body 21E swings to one side in the swinging direction around the pendulum fulcrum PF, as shown by a two-dot chain line in FIG. The elastic body accommodating portion 211 of the body 210E rotates around the pendulum fulcrum PF to one side in the swinging direction with respect to the elastic body accommodating window 151 of the driven member 15E. Thereby, each elastic body 100E is compressed by the pendulum mass body 21E and the driven member 15E, and each pendulum mass body 21E has a compression amount of the elastic body 100E (a rotation amount of the pendulum mass body 21E with respect to the driven member 15E). Accordingly, a restoring force for returning the pendulum mass body 21E to the balanced position is applied from the corresponding elastic body 100E. Further, even when each pendulum mass body 21E swings around the pendulum fulcrum PF to the other side in the swinging direction, the elastic body accommodating portion 211 of each weight 210E is relative to the elastic body accommodating window 151 of the driven member 15E. It rotates around the pendulum fulcrum PF to the other side in the swinging direction. Thereby, each elastic body 100E is compressed by the pendulum mass body 21E and the driven member 15E, and each pendulum mass body 21E has a compression amount of the elastic body 100E (a rotation amount of the pendulum mass body 21E with respect to the driven member 15E). Accordingly, a restoring force for returning the pendulum mass body 21E to the balanced position is applied from the corresponding elastic body 100E.

  Thus, in the centrifugal pendulum vibration absorber 20E, even if the pendulum mass body 21E is swung to one side or the other side in the swing direction, the elastic body 100E causes the pendulum mass body 21E to be balanced with the driven member 15E. It is possible to energize in the direction to return to. Accordingly, the restoring force for returning the pendulum mass body 21E swinging around the pendulum fulcrum PF to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20E, so that the equivalent rigidity of the centrifugal pendulum vibration absorber 20E is obtained. Can be made larger. As a result, also in the centrifugal pendulum vibration absorber 20E, the inertia of the pendulum mass body 21E can be increased using the annular mass body 25E without reducing the vibration order, and the inertia and vibration order of the pendulum mass body 21E can be increased. The degree of freedom of adjustment can be improved. Furthermore, the swing angle of the pendulum mass body 21E can be adjusted by adjusting the restoring force applied from the elastic body 100E to the pendulum mass body 21E, that is, the rigidity (spring constant) of the elastic body 100E. The annular mass body 25E may be omitted as in the centrifugal pendulum vibration absorber 20E ′ shown in FIG.

  FIG. 15 is a front view of a centrifugal pendulum vibration absorber 20F according to another embodiment of the present invention, and FIG. 16 is an enlarged view showing a main part of the centrifugal pendulum vibration absorber 20F. Of the constituent elements of the centrifugal pendulum vibration absorber 20F, the same elements as those of the centrifugal pendulum vibration absorbers 20 and 20E described above are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20F shown in FIG. 15 includes a plurality of (here, six) pendulum mass bodies 21F and an annular mass body as an additional mass body connected to each pendulum mass body 21F via a coupling mechanism 29. 25F. Similarly to the above-described pendulum mass body 21E, the pendulum mass body 21F also includes two weight bodies 210F formed by a metal plate so as to have a substantially fan-like cross-sectional shape. The two weights 210F have a single connecting shaft 230 that faces the axial direction of the damper device via a driven member 15F as a support member and is fixed to a tapered base end (a position of the fan). Are connected to each other. The connecting shaft 230 is inserted into any of a plurality of connecting holes formed at equal intervals on the outer periphery of the driven member 15E, whereby each pendulum mass body 21F has a pendulum fulcrum PF (the axis of the connecting shaft 230). It is connected to the driven member 15F so as to swing around. The annular mass body 25F includes an annular portion 250F having an inner diameter and an outer diameter larger than the outer diameter of the driven member 15F, and the annular portion 250F is disposed between the two weight bodies 210F of each pendulum mass body 21F.

  As shown in FIGS. 15 and 16, the centrifugal pendulum vibration absorber 20F functions as a compression spring between the driven member 15F and each pendulum mass body 21F so as to bend as the pendulum mass body 21F swings. A first elastic body 101F and a second elastic body 102F which are a coil spring, a disc spring, a leaf spring, or a resin such as rubber having flexibility and oil resistance are disposed. That is, the driven member 15F includes a plurality of arc-shaped elastic body receiving windows (openings) 151 formed at equal intervals so as to be positioned on the rotation center RC (axial center) side with respect to the connection hole through which the connection shaft is inserted. (6 here). Each elastic body receiving window 151 is symmetric with respect to the swing center line of the pendulum mass body 21F (see the alternate long and short dash line in FIG. 16) and from the corresponding connecting hole so as to protrude toward the rotation center RC of the driven member 15F. Is also formed radially inward. Further, as shown in FIGS. 15 and 16, the base end portion of each weight body 210 </ b> F is on the opposite side (rotation center RC side) from the fixed portion of the connecting shaft 230 to the widened portion side (connecting mechanism 29 side) on the outer peripheral side. ) Including an extending portion 212 extending in the direction of). Furthermore, the extended portion 212 has a contact portion 214 that protrudes from the surface of the tip portion on the driven member 15F side toward the driven member 15F, and the contact portion 214 corresponds to the corresponding elastic property of the driven member 15F. It is inserted into the body accommodation window 151.

  In each elastic body receiving window 151 of the driven member 15, the first and second elastic bodies 101F and 102F are disposed together with the contact portion 214 of the weight body 210F. The first and second elastic bodies 101F and 102F are arranged in the elastic body receiving window 151 so as to be arranged in the circumferential direction via the contact portion 214, and are closer to the rotation center RC side (diameter of the driven member 15F than the pendulum fulcrum PF). (Inward direction). As shown in the drawing, one end of the first and second elastic bodies 101F, 102F (the end on the side close to the swing center line) is the weight body 210F when the pendulum mass body 21F is in the balanced position. It contacts with the contact part 214. That is, when the pendulum mass body 21F is in the balanced position, the abutment portion 214 of each weight body 210F (pendulum mass body 21F) abuts against both ends between the first and second elastic bodies 101F and 102F. . Further, the other end portions (end portions far from the swinging center line) that do not come into contact with the contact portions 214 of the first and second elastic bodies 101F and 102F are end faces in the circumferential direction of the elastic body receiving window 151, respectively. A part of the driven member 15F that forms

  In the centrifugal pendulum type vibration absorber 20F configured as described above, when each pendulum mass body 21F swings around the pendulum fulcrum PF to one side in the swinging direction, the contact portion 214 of each weight body 210F is driven by the driven member 15F. Move around the pendulum fulcrum PF to one side in the swing direction within the elastic body receiving window 151. Thereby, for example, each first elastic body 101F is compressed by the abutting portion 214 of the pendulum mass body 21F and the driven member 15F, and each pendulum mass body 21F has a compression amount (relative to the driven member 15F) of the first elastic body 101F. A restoring force for returning the pendulum mass body 21F to the balanced position is applied from the corresponding first elastic body 101F in accordance with the pendulum mass body 21F (the rotation amount of the abutment portion 214).

  Further, when each pendulum mass body 21F swings around the pendulum fulcrum PF to the other side in the swinging direction, the abutment portion 214 of each weight 210F has a pendulum fulcrum within the elastic body receiving window 151 of the driven member 15F. Move around the PF to the other side in the swing direction. Thereby, for example, each second elastic body 102F is compressed by the pendulum mass body 21F (contact portion 214) and the driven member 15F, and each pendulum mass body 21F has a compression amount (driven member 15F) of the second elastic body 102F. The restoring force for returning the pendulum mass body 21F to the balanced position is applied from the corresponding second elastic body 102F in accordance with the pendulum mass body 21F (the amount of rotation of the contact portion 214).

  Thus, in the centrifugal pendulum type vibration absorber 20F, when the pendulum mass body 21F swings to one side in the swinging direction, the first elastic body 101F causes the pendulum mass body 21F to be in a balanced position with respect to the driven member 15F. It can be urged in the returning direction. Further, when the pendulum mass body 21F swings to the other side in the swinging direction, the second elastic body 102F can bias the driven pendulum mass body 21F in a direction to return it to the balanced position. Accordingly, also in the centrifugal pendulum vibration absorber 20F, the restoring force for returning the pendulum mass body 21F swinging around the pendulum fulcrum PF to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20F, The equivalent rigidity of the centrifugal pendulum vibration absorber 20F can be further increased. As a result, the inertia of the pendulum mass body 21F can be increased using the annular mass body 25F without reducing the vibration order, and the degree of freedom in adjusting the inertia and vibration order of the pendulum mass body 21F can be improved. Can do. Further, by adjusting the restoring force applied to the pendulum mass body 21F from the first and second elastic bodies 101F and 102F, that is, the rigidity (spring constant) of the first and second elastic bodies 101F and 102F, the pendulum mass body is adjusted. It is also possible to adjust the deflection angle of 21F.

  Note that one end of the first and second elastic bodies 101F, 102F (the end near the swinging center line) may be coupled to the contact portion 214 of the weight body 210F. The other end of the two elastic bodies 101F and 102F that does not come into contact with the contact portion 214 (the end on the side far from the swing center line) may be connected to a corresponding part of the driven member 15F. Further, the annular mass body 25F may be omitted as in the centrifugal pendulum vibration absorber 20F ′ shown in FIG.

  18 is a front view of a centrifugal pendulum vibration absorber 20G according to another embodiment of the present invention, and FIG. 19 is an enlarged view showing a main part of the centrifugal pendulum vibration absorber 20G. Note that, among the constituent elements of the centrifugal pendulum vibration absorber 20G, the same elements as those of the centrifugal pendulum vibration absorbers 20 and 20D described above are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20G shown in FIG. 18 has a plurality of (here, six) pendulum mass bodies 21G having the same configuration as the pendulum mass body 21D of the centrifugal pendulum vibration absorber 20D shown in FIG. An annular mass body 25G as an additional mass body having an annular portion 250G disposed between two weight bodies 210G of the mass body 21G and coupled to each pendulum mass body 21G via a coupling mechanism 29 is included. In the centrifugal pendulum vibration absorber 20G, as shown in FIG. 19, the first torsion spring 101G and the second torsion spring 101G each having an arm part (free end part) 101a or 102a and a coil part (base end part) 101c or 102c, respectively. A torsion spring 102G is employed as a restoring force applying means.

  One first and second torsion springs 101G and 102G are provided for each pendulum mass body 21G. The coil portion 101c of the first torsion spring 101G and the coil portion 102c of the second torsion spring 102G are supported by a driven member 15G as a support member so as to face each other with the coupling shaft 230 (pendulum fulcrum PF) interposed therebetween. . Further, the tip of the arm portion 101a of the first torsion spring 101G is in contact with one end portion (the right end portion in FIG. 19) in the swinging direction of the pendulum mass body 21G (weight body 210G), and the second torsion spring 101G The tip of the arm 102a of the spring 102G is in contact with the other end (the left end in FIG. 19) in the swinging direction of the pendulum mass 21G (weight 210G). That is, the first and second torsion springs 101G and 102G are attached to the driven member 15G so as to be symmetric with respect to the swing center line of the pendulum mass body 21G when the pendulum mass body 21G is in the balanced position.

  In the centrifugal pendulum type vibration absorber 20G configured as described above, when each pendulum mass body 21G swings to one side in the swing direction around the pendulum fulcrum PF, as shown by a broken line in FIG. 19, the pendulum mass body 21G The arm portion 101a of the first torsion spring 101G is bent with the coil portion 101c as a base point. Thus, each pendulum mass body 21G is restored to return the pendulum mass body 21G to the balanced position according to the amount of bending of the first torsion spring 101G (the amount of rotation of the pendulum mass body 21G relative to the driven member 15G). A force is applied from the corresponding first torsion spring 101G. Further, when each pendulum mass body 21G swings around the pendulum fulcrum PF to the other side in the swinging direction, the arm portion 102a of the second torsion spring 102G is pressed by the pendulum mass body 21G so that the coil portion 102c. Deflection from the base point. Accordingly, each pendulum mass body 21G is restored to return the pendulum mass body 21G to the balanced position according to the amount of bending of the second torsion spring 102G (the amount of rotation of the pendulum mass body 21G relative to the driven member 15G). A force is applied from the corresponding second torsion spring 102G.

  Thus, in the centrifugal pendulum vibration absorber 20G, when the pendulum mass body 21G swings to one side in the swing direction, the pendulum mass body 21G is brought into the balanced position with respect to the driven member 15G by the first torsion spring 101G. It can be urged in the returning direction. Further, when the pendulum mass body 21G swings to the other side in the swinging direction, the second torsion spring 102G can urge the driven member 15G in a direction to return the pendulum mass body 21G to the balanced position. Therefore, also in the centrifugal pendulum vibration absorber 20G, the restoring force for returning the pendulum mass body 21G swinging around the pendulum fulcrum PF to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20G, The equivalent rigidity of the centrifugal pendulum vibration absorber 20G can be further increased. As a result, the inertia of the pendulum mass body 21G can be increased using the annular mass body 25G without lowering the vibration order, and the degree of freedom in adjusting the inertia and vibration order of the pendulum mass body 21G can be improved. Can do. Further, by adjusting the restoring force applied to the pendulum mass body 21G from the first and second torsion springs 101G and 102G, that is, the rigidity (spring constant) of the first and second torsion springs 101G and 102G, the pendulum mass body is adjusted. It is also possible to adjust the swing angle of 21G. The annular mass body 25G may be omitted as in a centrifugal pendulum vibration absorber 20G ′ shown in FIG.

  FIG. 21 is a front view of a centrifugal pendulum vibration absorber 20H according to another embodiment of the present invention, and FIG. 22 is an enlarged view showing a main part of the centrifugal pendulum vibration absorber 20H. Of the constituent elements of the centrifugal pendulum vibration absorber 20H, the same elements as those of the centrifugal pendulum vibration absorbers 20 and 20D described above are denoted by the same reference numerals, and redundant description is omitted.

  A centrifugal pendulum vibration absorber 20H shown in FIG. 21 has a plurality of (here, six) pendulum mass bodies 21H having the same configuration as the pendulum mass body 21D of the centrifugal pendulum vibration absorber 20D shown in FIG. And an annular mass body 25H as an additional mass body having an annular portion 250H disposed between two weight bodies 210H of the mass body 21H and coupled to each pendulum mass body 21H via a coupling mechanism 29. In the centrifugal pendulum type vibration absorber 20H, a plurality of (here, six) elastic members are bent between the driven member 15H serving as the support member and the annular mass body 25H as the pendulum mass body 21H swings. A body 100H is arranged. The elastic body 100H is a coil spring, a disc spring, a leaf spring, or a resin such as rubber having flexibility and oil resistance, and functions as a compression spring.

  As shown in FIGS. 21 and 22, a plurality of enlarged diameter portions 155 having an outer diameter larger than the inner diameter of the annular portion 250 </ b> H of the annular mass body 25 </ b> H are adjacent to each other on the outer peripheral portion of the driven member 15 </ b> H. Are formed at equal intervals so as to be positioned one by one. Each enlarged diameter portion 155 of the driven member 15H is formed with an arcuate elastic body receiving window (opening) 151, and each enlarged diameter portion 155 overlaps with the annular portion 250H of the annular mass body 25H. It arrange | positions between the two weight bodies 210H of the pendulum mass body 21H. In addition, in the annular portion 250H of the annular mass body H, arc-shaped elastic body accommodating portions (for example, openings) 259 extending along the circumferential direction of the annular portion 250H are formed at equal intervals. The circumferential lengths of the elastic body accommodating window 151 and the elastic body accommodating portion 259 are the same length according to the natural length of the elastic body 100H, and when each pendulum mass body 21H is in a balanced position, the elasticity of the driven member 15H is The body housing window 151 and the corresponding elastic body housing portion 259 of the annular mass body 25H overlap each other when viewed from the axial direction of the centrifugal pendulum vibration absorber 20H.

  The elastic body 100H is disposed in the elastic body accommodating window 151 of the driven member 15H and the elastic body accommodating portion 259 of the corresponding annular mass body 25H, and is located on the outer side in the radial direction of the driven member 15E from the pendulum fulcrum PF. Will do. When each pendulum mass body 21H is in a balanced position, both ends of the elastic body 100H abut against both a part of the driven member 15H and a part of the annular mass body 25H. That is, when each pendulum mass body 21 </ b> H is in a balanced position, one end of the elastic body 100 </ b> H is part of the driven member 15 </ b> H that forms a wall surface on one end side in the circumferential direction of the elastic body receiving window 151 and the elastic body receiving portion 259. The driven member that abuts both of a part of the annular mass body 25 </ b> H that forms the wall surface on one end side in the circumferential direction and that forms the wall surface on the other end side in the circumferential direction of the elastic body housing window 151. A part of 15H and a part of the annular mass body 25H forming the wall surface on the other end side in the circumferential direction of the elastic body accommodating portion 259 are in contact with each other.

  In the centrifugal pendulum type vibration absorber 20H configured as described above, when each pendulum mass body 21H swings around the pendulum fulcrum PF to one side in the swinging direction, as shown by a two-dot chain line in FIG. Each elastic body accommodating portion 259 of the body 25H rotates to one side in the swing direction around the pendulum fulcrum PF with respect to the elastic body accommodating window 151 of the driven member 15H. As a result, each elastic body 100H is compressed by the annular mass body 25H and the driven member 15H, and the annular mass body 25H corresponds to the compression amount of the elastic body 100H (the amount of rotation of the annular mass body 25H relative to the driven member 15H). Thus, a restoring force for returning the pendulum mass body 21H to the balanced position is applied from the corresponding elastic body 100H. Further, when each pendulum mass body 21H swings around the pendulum fulcrum PF to the other side in the swinging direction, the elastic body accommodating portion 259 of the annular mass body 25H is opposed to the elastic body accommodating window 151 of the driven member 15H. It rotates around the pendulum fulcrum PF to the other side in the swinging direction. As a result, each elastic body 100H is compressed by the pendulum mass body 21H and the driven member 15H, and the annular mass body 25H corresponds to the compression amount of the elastic body 100H (the amount of rotation of the pendulum mass body 21H relative to the driven member 15H). Thus, a restoring force for returning the pendulum mass body 21H to the balanced position is applied from the corresponding elastic body 100H.

  As described above, in the centrifugal pendulum vibration absorber 20H, the driven member is configured such that the elastic body 100H returns the pendulum mass body 21H to the balanced position regardless of whether the pendulum mass body 21H is swung to one side or the other side in the swinging direction. The annular mass body 25H connected to the pendulum mass body 21H can be biased with respect to 15H. Therefore, also in the centrifugal pendulum vibration absorber 20H, the restoring force for returning the pendulum mass body 21H swinging around the pendulum fulcrum PF to the balanced position is made larger than that originally possessed by the centrifugal pendulum vibration absorber 20H, The equivalent rigidity of the centrifugal pendulum vibration absorber 20H can be further increased. As a result, the inertia of the pendulum mass body 21H can be increased using the annular mass body 25H without lowering the vibration order, and the degree of freedom in adjusting the inertia and vibration order of the pendulum mass body 21H can be improved. Can do. Furthermore, the swing angle of the pendulum mass body 21H can be adjusted by adjusting the restoring force applied from the elastic body 100H to the annular mass body 25H, that is, the rigidity (spring constant) of the elastic body 100H.

  The centrifugal pendulum vibration absorbers 20 to 20H described above may be coupled to the drive member (input element) 11 of the damper device 10. The damper device includes a drive member (input element), an intermediate member (intermediate element), and a driven member (output element) as rotating elements, and is disposed between the drive member and the intermediate member as a power transmission element. When the second spring disposed between the spring and the intermediate member and the driven member is included, the centrifugal pendulum vibration absorbers 20 to 20H may be connected to any of the drive member, the intermediate member, and the driven member of the damper device. Good. Furthermore, the damper device includes a drive member (input element), a first intermediate member (first intermediate element), a second intermediate member (second intermediate element), and a driven member (output element) as rotating elements, and transmits power. A first spring disposed as an element between the drive member and the first intermediate member, a second spring disposed between the first intermediate member and the second intermediate member, and between the second intermediate member and the driven member In the case of including the third spring arranged in the above, the centrifugal pendulum vibration absorbers 20 to 20H may be connected to any of the drive member, the first intermediate member, the second intermediate member, and the driven member of the damper device. Further, the restoring force applying means for applying a restoring force for returning the mass body to the balanced position as the mass body swings is not limited to the elastic body. When the mass body constituting the centrifugal pendulum type vibration absorber is arranged in a fluid chamber (liquid chamber) that contains hydraulic oil or the like, the mass of the liquid reservoir (oil reservoir) that stores fluid such as hydraulic oil is mass. A restoring force may be applied to the mass body so as to return to the balance position from the fluid in the liquid reservoir portion formed around the body.

  As described above, the centrifugal pendulum type vibration absorber according to the present invention applies a vibration having a phase opposite to the vibration transmitted from the driving device to the rotating element to the rotating element rotating by the power from the driving device. A centrifugal pendulum type vibration absorber, a mass body connected to the rotating element so as to swing around a pendulum fulcrum, and for returning the mass body to a balanced position as the mass body swings Restoring force applying means for applying a restoring force to the mass body.

  This centrifugal pendulum type vibration absorber includes a mass body connected to a rotating element so as to swing around a pendulum fulcrum, and imparts a vibration having a phase opposite to that transmitted from a driving device to the rotating element. Is. In this centrifugal pendulum vibration absorber, a restoring force for returning the mass body to the balanced position is applied from the restoring force applying means to the mass body as the mass body swings. As a result, the restoring force to return the mass body swinging around the pendulum fulcrum to the balanced position is made larger than that originally possessed by the centrifugal pendulum absorber, and the equivalent stiffness of the centrifugal pendulum absorber is increased. Can do. Therefore, the inertia of the mass body can be increased without reducing the vibration order, and the vibration order can be increased without reducing the inertia of the mass body. As a result, this centrifugal pendulum vibration absorber can improve the freedom of adjustment of the inertia and vibration order of the mass body. In addition, the deflection angle of the mass body can be adjusted by adjusting the restoring force applied to the mass body from the restoring force applying means.

  Moreover, you may further provide the additional mass body connected with the said mass body so that it may rock | fluctuate around the rotation center of the said rotation element with the rocking | fluctuation of the said mass body. In the centrifugal pendulum type vibration absorber configured as described above, when the additional mass body swings around the rotation center of the rotating element as the mass body swings, the inertial mass ( Rotational moment). Accordingly, it is possible to increase the inertia of the mass body and further improve the vibration damping effect of the centrifugal pendulum type vibration absorber. Then, as the mass body swings, the vibration order is lowered by increasing the inertia of the mass body by applying the restoring force for returning the restoring force from the restoring force applying means to the balanced position. Can be satisfactorily suppressed.

  Further, the mass body is connected to the rotating element so as to swing around the first pendulum fulcrum, and the first mass body connected to the rotating element so as to swing around the first pendulum fulcrum. The additional mass body may be coupled to at least one of the first and second mass bodies, and the first mass body has a first vibration order. The second mass body may have a second vibration order different from the first vibration order, and the restoring force applying means includes at least the first and second mass bodies. You may give the said restoring force with respect to one which has a higher vibration order. In the centrifugal pendulum vibration absorber configured as described above, the first mass body is further improved while increasing the inertia of at least one of the first and second mass bodies to further improve the vibration damping effect of the centrifugal pendulum vibration absorber. The first vibration order and the second vibration order of the second mass body can be easily made different. Then, by applying a restoring force for restoring the balance position to one of the first and second mass bodies having a higher vibration order from the restoring force applying means, the first and second mass bodies At least one vibration order can be maintained high. Therefore, according to this centrifugal pendulum type vibration absorber, even if the order of vibration transmitted from the driving device to the rotating element is changed, the first or second mass body is swung with respect to the rotating element so that the driving device can It is possible to satisfactorily dampen the vibration of the rotating element by applying a vibration having a phase opposite to that of the rotating element to the rotating element.

  The drive device may be an internal combustion engine having a cylinder deactivation function, and the centrifugal pendulum vibration absorber is configured such that when the vibration order of the first mass body performs all-cylinder operation, the rotation element And the vibration order of the second mass body coincides with the vibration order transmitted from the internal combustion engine to the rotating element when the reduced cylinder operation is performed. Good. As a result, the vibration transmitted from the drive device to the rotating element both during execution of all cylinder operation of the internal combustion engine, which is the drive device (when cylinder deactivation is not performed) and during execution of reduced cylinder operation (cylinder deactivation). Can be satisfactorily attenuated.

  Further, the restoring force applying means may be an elastic body arranged between the mass body and the additional mass body so as to bend as the mass body swings. Accordingly, the mass body can be biased in the direction of returning the mass body to the balanced position by the elastic body with respect to the additional mass body swinging around the rotation center of the rotating element.

  In this case, the centrifugal pendulum type vibration absorber includes a guide portion formed on one of the mass body and the additional mass body so as to extend in the radial direction of the rotating element, and the other of the mass body and the additional mass body. A coupling mechanism including a shaft portion that is extended and is rotatably guided by the guide portion and is movable in the extending direction of the guide portion. You may arrange | position in the said guide part so that it may be located between said one of the mass bodies and the said shaft part. As a result, when the mass body swings around the pendulum fulcrum while reducing the size of the coupling mechanism, the additional mass body swings around the rotation center of the rotating element, and the elastic body causes the mass body to move relative to the additional mass body. Can be biased in the direction of returning to the balanced position.

  The centrifugal pendulum type vibration absorber may further include a support member that swingably supports the mass body and rotates integrally with the rotating element, and the restoring force applying means is configured to swing the mass body. It may be an elastic body arranged between the mass body and the support member so as to bend with movement. Thereby, it becomes possible to urge the supporting member rotating integrally with the rotating element in a direction to return the mass body to the balanced position by the elastic body.

  In this case, the elastic body may be arranged outside the pendulum fulcrum in the radial direction of the rotating element so as to extend along the swinging direction of the mass body, and both end portions of the elastic body are When the mass body is in the balanced position, both of the mass body and the support member may be in contact with each other. Thereby, even if the mass body is swung to one side or the other side in the swinging direction, it is possible to bias the mass body to the support member in the direction of returning to the balance position by the elastic body.

  Further, the elastic body may include a first elastic body and a second elastic body that are arranged on the rotation center side of the rotating element with respect to the pendulum fulcrum so as to extend along the swinging direction of the mass body. Preferably, one end of each of the first and second elastic bodies may abut against an abutting portion provided on the mass body, and contact with the abutting portion of the first and second elastic bodies. The other end that is not in contact may abut against a part of the support member. As a result, when the mass body swings to one side in the swinging direction, for example, the first elastic body can bias the mass body with respect to the support member in a direction to return to the balanced position. When swinging to the other side in the swing direction, for example, the second elastic body can bias the mass body with respect to the support member in a direction to return to the balanced position.

  The elastic body is supported by the support member and a first torsion spring having a base end portion supported by the support member and a free end portion in contact with one end portion in the swinging direction of the mass body. And a second torsion spring having a free end portion that comes into contact with the other end portion in the swinging direction of the mass body. As a result, when the mass body swings to one side in the swinging direction, for example, the first torsion spring can bias the mass body to the support member in the returning direction to the balance position. When swaying to the other side in the swinging direction, for example, the second torsion spring can bias the mass body to the support member in the direction of returning to the balanced position.

  Further, the centrifugal pendulum type vibration absorber includes a support member that supports the mass body in a swingable manner and that rotates together with the rotating element, and a center of rotation of the rotating element as the mass body swings. An additional mass body connected to the mass body so as to swing, and the restoring force applying means includes a support member and the additional mass body so as to bend as the mass body swings. It may be an elastic body arranged between them. Thereby, it becomes possible to urge the additional mass body connected to the mass body with respect to the support member so that the mass body returns to the balanced position by the elastic body.

  In this case, the elastic body may be disposed outside the pendulum fulcrum in the radial direction of the rotating element so as to extend along the swing direction of the additional mass body, and both end portions of the elastic body When the mass body is in the balanced position, it may abut against both a part of the support member and a part of the additional mass body. This makes it possible to bias the additional mass body against the support member so that the mass body returns to the balanced position by the elastic body regardless of whether the mass body swings to one side or the other side in the swing direction. Become.

  The mass bodies may be coupled to the rotating element via a pair of link members arranged in parallel to each other, and the restoring force applying means is configured to expand and contract as the mass bodies swing. It may be an elastic body connected to the link member. Thus, in the so-called bifilar type centrifugal pendulum type vibration absorber, even if an elastic body is arranged between a pair of link members for connecting the mass body to the rotating element, the restoring force for returning to the balanced position is not affected. It becomes possible to give to a mass body from an elastic body.

  Further, the centrifugal pendulum vibration absorber may include a plurality of the mass bodies, the plurality of mass bodies may be arranged so as to be arranged at intervals in the circumferential direction, and the restoring force applying means is The elastic body may be disposed between the two mass bodies adjacent to each other so as to bend as the plurality of mass bodies swing. Thus, even if an elastic body is disposed between two adjacent mass bodies, it is possible to apply a restoring force for returning to the balanced position from the elastic body to the mass bodies on both sides.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in the field of manufacturing centrifugal pendulum vibration absorbers.

  DESCRIPTION OF SYMBOLS 1 Starter, 3 Front cover, 4 Pump impeller, 5 Turbine runner, 6 Stator, 7 Damper hub, 8 Lock-up clutch, 9 Fluid transmission chamber, 10 Damper device, 11 Drive member, 12 First input plate member, 12a, 12b , 13a, 13b Spring support portion, 12c, 13c Spring contact portion, 13 Second input plate member, 15, 15D, 15E, 15F, 15G, 15H Driven member, 15c Spring contact portion, 15p Protruding portion, 20, 20B , 20B ′, 20C, 20D, 20E, 20E ′, 20F, 20F ′, 20G, 20G ′, 20H Centrifugal pendulum absorber, 21 First mass body, 21C, 21D, 21E, 21F, 21G, 21H Pendulum mass body , 22 Second mass body, 23, 23B First link member, 23p 24p protrusion, 24, 24B second link member, 25 first annular mass, 25C, 25D, 25E, 25F, 25G, 25H annular mass, 25s shaft portion, 26 second annular mass, 27 first slider, 28 Second slider, 29, 30 coupling mechanism, 40 pump shell, 41 pump blade, 50 turbine shell, 51 turbine blade, 60 stator blade, 61 one-way clutch, 80 lock-up piston, 81 friction material, 85 lock-up chamber, 100 , 100B, 100C, 100D, 100E, 100H elastic body, 101F first elastic body, 101G first torsion spring, 101a, 102a arm part, 101c, 102c coil part, 102F second elastic body, 102G second torsion spring, 151 Elastic body receiving window, 15 Expanded portion, 210 first weight body, 210D, 210E, 210F, 210G, 210H weight body, 211 elastic body accommodating portion, 212 extension portion, 214 contact portion, 215 first guide opening portion, 220 second weight body 225 Second guide opening, 230 connecting shaft, 250 first annular portion, 250D, 250E, 250F, 250G, 250H annular portion, 251 inner projecting portion, 255 first shaft portion, 259 elastic body accommodating portion, 260 second Annular part, 261 enlarged diameter part, 265 second shaft part, 270 slider, IS input shaft, PF, PF1, PF2 pendulum fulcrum, RC rotation center, SP spring.

Claims (14)

A centrifugal pendulum type vibration absorber that imparts vibration having a phase opposite to vibration transmitted from the driving device to the rotating element with respect to the rotating element that rotates by power from the driving device,
A mass connected to the rotating element to swing about a pendulum fulcrum;
A centrifugal pendulum type vibration absorbing device comprising: a restoring force applying unit that applies a restoring force to the mass body to return the mass body to a balanced position as the mass body swings. The centrifugal pendulum type vibration absorber according to claim 1,
The centrifugal pendulum type vibration absorber is further provided with an additional mass body connected to the mass body so as to swing around the rotation center of the rotating element as the mass body swings. The centrifugal pendulum vibration absorber according to claim 2,
The mass body is connected to the rotating element so as to swing around a first pendulum fulcrum, and a first mass body connected to the rotating element so as to swing around a second pendulum fulcrum. 2 masses,
The additional mass body is connected to at least one of the first and second mass bodies,
The first mass body has a first vibration order, and the second mass body has a second vibration order different from the first vibration order;
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means applies the restoring force to at least one of the first and second mass bodies having a higher vibration order. The centrifugal pendulum vibration absorber according to claim 3,
The drive device is an internal combustion engine having a cylinder deactivation function,
The first vibration order coincides with the vibration order transmitted from the internal combustion engine to the rotating element when the all-cylinder operation is performed, and the second vibration order is from the internal combustion engine when the reduced-cylinder operation is performed. A centrifugal pendulum type vibration absorber configured to match the order of vibration transmitted to the rotating element. In the centrifugal pendulum type vibration absorber according to any one of claims 2 to 4,
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means is an elastic body disposed between the mass body and the additional mass body so as to bend as the mass body swings. The centrifugal pendulum vibration absorber according to claim 5,
A guide portion formed on one of the mass body and the additional mass body so as to extend in a radial direction of the rotating element; and extends from the other of the mass body and the additional mass body and is rotatable by the guide portion. A coupling mechanism including a shaft portion that is movably guided in the extending direction of the guide portion;
The centrifugal pendulum type vibration damping device according to claim 1, wherein the elastic body is disposed in the guide portion so as to be positioned between the one of the mass body and the additional mass body and the shaft portion. In the centrifugal pendulum type vibration absorber according to any one of claims 1 to 4,
A support member that swingably supports the mass body and rotates integrally with the rotating element;
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means is an elastic body arranged between the mass body and the support member so as to bend as the mass body swings. The centrifugal pendulum vibration absorber according to claim 7,
The elastic body is disposed outside the pendulum fulcrum in the radial direction of the rotating element so as to extend along the swinging direction of the mass body, and both ends of the elastic body have the mass body A centrifugal pendulum type vibration absorber, which is in contact with both a part of the mass body and a part of the support member when in the balanced position. The centrifugal pendulum vibration absorber according to claim 7,
The elastic body includes first and second elastic bodies arranged on the rotation center side of the rotating element with respect to the pendulum fulcrum so as to extend along the swinging direction of the mass body, respectively.
One end of each of the first and second elastic bodies is in contact with a contact portion provided on the mass body, and the other end is not in contact with the contact portion of the first and second elastic bodies. The parts are in contact with a part of the support member, respectively. The centrifugal pendulum vibration absorber according to claim 7,
The elastic body is supported by the support member and a first torsion spring having a base end portion supported by the support member and a free end portion in contact with one end portion in the swinging direction of the mass body. A centrifugal pendulum type vibration absorber comprising a second torsion spring having a base end portion and a free end portion in contact with the other end portion in the swinging direction of the mass body. The centrifugal pendulum type vibration absorber according to claim 1,
A support member that swingably supports the mass body and rotates integrally with the rotating element;
An additional mass body connected to the mass body so as to swing around the rotation center of the rotating element as the mass body swings;
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means is an elastic body arranged between the support member and the additional mass body so as to bend as the mass body swings. The centrifugal pendulum type vibration absorber according to claim 11,
The elastic body is disposed outside the pendulum fulcrum in the radial direction of the rotating element so as to extend along the swinging direction of the additional mass body, and both ends of the elastic body have the mass body The centrifugal pendulum type vibration absorber is in contact with both a part of the support member and a part of the additional mass body when in the balanced position. In the centrifugal pendulum type vibration absorber according to any one of claims 1 to 4,
The mass body is connected to the rotating element via a pair of link members arranged in parallel to each other,
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means is an elastic body connected to the pair of link members so as to expand and contract as the mass body swings. In the centrifugal pendulum type vibration absorber according to any one of claims 1 to 4,
A plurality of the mass bodies;
The plurality of mass bodies are arranged to be arranged at intervals in the circumferential direction,
The centrifugal pendulum type vibration absorber is characterized in that the restoring force applying means is an elastic body arranged between the two mass bodies adjacent to each other so as to bend as the plurality of mass bodies swing.

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