JP2016142350A5 - - Google Patents

Description

Dynamic vibration absorber for automobile

  The present invention relates to a dynamic vibration absorber for an automobile.

A conventional torque converter including a damper device and a dynamic vibration absorber is disclosed (see Patent Document 1). In this torque converter, the damper device reduces torque fluctuations over a wide range of rotation speeds, and the dynamic vibration absorber reduces torque fluctuations due to resonance or the like at specific rotation speeds. For example, in the conventional dynamic vibration absorber (5), a rotating member (10) to which the rotation of the engine is transmitted, and an inertia mass portion (9) swingably disposed on the rotating member via a rolling roller (27). (See FIGS. 1 and 4 of Patent Document 1). In this dynamic vibration absorber, when the rotation of the engine is transmitted to the rotating member, centrifugal force acts on the inertial mass portion, and the inertial mass portion swings relative to the rotating member. The fluctuation of torque is reduced by the oscillation of the inertial mass portion.

Special table 2011-504986 gazette

  In the conventional dynamic vibration absorber, when the engine rotates and centrifugal force acts on the inertial mass portion, the inertial mass portion swings in a circular arc path with respect to the rotating member via the rolling roller. Here, when the engine is stopped and the rotation of the rotating member gradually decreases, the centrifugal force acting on the inertial mass portion becomes smaller than the gravity acting on the inertial mass portion, and the inertial mass portion falls downward. Then, a collision noise between the inertial mass portion and the rolling roller, a collision noise between the rotating member and the rolling roller, or the like may occur.

  In the process of rotating the rotating member, not all of the plurality of inertia mass parts swing in the same state, but only a part of the plurality of inertia mass parts falls downward and swings. There is also a risk. Due to the unbalanced oscillation of the inertial mass portion, there is a possibility that a vibration unexpected by the designer may occur.

  This invention is made | formed in view of said problem, Comprising: The objective of this invention is providing the dynamic vibration damper which can operate a mass part stably.

  (1) A dynamic vibration damping device for an automobile according to one aspect of the present invention is for attenuating vibration transmitted from an engine to a transmission. The dynamic vibration absorber includes a rotating part, a plurality of mass parts, a connecting part, and a guide mechanism.

  The rotating part can rotate around the center of rotation. Each of the plurality of mass parts can attenuate the vibration of the rotating part by moving relative to the rotating part when the rotating part rotates. A connection part connects a rotation part and a mass part. The guide mechanism guides the mass portion in the radial direction when the rotating portion rotates.

  In this dynamic vibration absorber, when the rotating part rotates around the rotation center, each of the plurality of mass parts connected to the rotating part by the connecting part is guided in the radial direction by the guide mechanism. Thereby, each of the plurality of mass parts moves relative to the rotating part and attenuates the vibration of the rotating part.

  Thus, in this dynamic vibration absorber, the rotating part and each mass part are connected by the connecting part, and the movement of each mass part is restricted in the radial direction by the guide mechanism. That is, each mass part moves in a direction (radial direction) different from the rotation direction of the rotating part while being supported by the rotating part by the connecting part.

  For example, when the case where a plurality of mass parts is a pair of mass parts is taken as an example, one center of gravity of the pair of mass parts is located above the center of rotation, and the other center of gravity of the pair of mass parts is from the center of rotation. When the rotation of the rotating part becomes low in the state of being positioned below, each mass part moves downward (drops) due to gravity.

At this time, when one mass part is about to fall in a state where each mass part is connected to the rotating part by each connecting part, the rotating part is in the first rotating direction and the second rotating direction (what is the first rotating direction? Try to rotate in either one of the opposite rotation directions). On the other hand, when the other mass portion is about to fall, the rotating portion tends to rotate in either one of the first rotation direction and the second rotation direction. That is, when both of the pair of mass parts are about to fall downward, the rotation of the rotating part is canceled out.

  For this reason, even if rotation of a rotation part becomes low rotation (even if centrifugal force is insufficient), a mass part is hard to fall in the direction of gravity, and is hard to be influenced by rotation of a rotation part. Thus, compared with the prior art in which the mass portion can freely operate with respect to the rotating member, the dynamic vibration absorber can stably operate the mass portion.

  (2) The dynamic vibration absorber for automobiles according to another aspect of the present invention is preferably configured as follows. One end of the connecting portion is swingably attached to the rotating portion. The other end of the connecting portion is swingably attached to the mass portion.

  In this case, the connecting portion swings by the rotation of the rotating portion, and the mass portion moves in the radial direction by the guide mechanism in conjunction with the swinging of the connecting portion. Thus, the rotational motion of the rotating portion can be changed to the linear motion of the mass portion by the connecting portion and the guide mechanism. Thereby, compared with the prior art in which a mass part can operate | move freely with respect to a rotating member, in this dynamic vibration absorber, a mass part can be operated stably.

  (3) The automobile dynamic vibration damping device according to another aspect of the present invention is preferably configured as follows. Each of the plurality of mass parts is arranged around the rotation center. The angle formed by the line segment connecting the center of gravity of the adjacent mass portion and the rotation center around the rotation center is the same.

  In this case, since the plurality of mass parts are evenly arranged around the rotation center, it is possible to appropriately maintain the balance when the mass part is moved.

  (4) The automobile dynamic vibration absorber according to another aspect of the present invention is preferably configured as follows. The guide mechanism includes a main body portion that can rotate relative to the rotation portion, and a guide portion that guides the mass portion in the radial direction.

  In this case, the main body portion of the guide mechanism operates as a float body with respect to the rotating portion, and the guide portion of the guide mechanism guides the mass portion in the radial direction. Thus, by operating the main body part independently of the rotation of the rotating part, even if the rotating part rotates, the mass part can be guided in the radial direction by the guide part.

(5) The automobile dynamic vibration damping device according to another aspect of the present invention is preferably configured as follows. The guide part has a long hole part and a shaft member. The long hole portion is provided in one of the mass portion and the main body portion, and extends in a direction along a straight line passing through the center of gravity and the rotation center of the mass portion. The shaft member is disposed in the long hole portion and is fixed to either the mass portion or the main body portion .

  In this case, when the rotating portion rotates, the mass portion moves in the radial direction via the connecting portion by the shaft member and the long hole portion of the guide mechanism. Thus, even if the rotating part rotates, the mass part can be operated linearly by the connecting part and the guide mechanism. Thereby, compared with the prior art in which a mass part can operate | move freely with respect to a rotating member, in this dynamic vibration absorber, a mass part can be operated stably.

  (6) The dynamic vibration absorber for automobiles according to another aspect of the present invention is preferably configured as follows. The mass portion is positioned by the connecting portion at a position where the center of gravity of the mass portion is farthest from the rotation center. The mass part is positioned by the guide mechanism at a position where the center of gravity of the mass part is closest to the center of rotation.

  In this case, the moving range in which the mass portion moves in the radial direction is determined by the connecting portion and the guide mechanism. Thereby, the movement range of a mass part can be restrict | limited without preparing a special member.

  (7) The dynamic vibration absorber for automobiles according to another aspect of the present invention is preferably configured as follows. One end of the connecting portion is swingably attached to the rotating portion. The other end of the connecting portion is swingably attached to the mass portion. The mass portion is positioned at a position where the center of gravity of the mass portion is farthest from the rotation center by the length from the swing center of one end portion of the connecting portion to the swing center of the other end portion of the connecting portion.

  In this case, by adjusting the length of the connecting portion, the position where the mass portion is most distant from the rotation center can be set. That is, this position can be easily changed. That is, the moving range of the mass part can be easily adjusted.

  (8) The automobile dynamic vibration damping device according to another aspect of the present invention is preferably configured as follows. The guide mechanism has a main body portion and a positioning portion. The main body is rotatable relative to the rotating part. The positioning part is provided in the main body part. The positioning unit positions the mass unit at a position where the center of gravity of the mass unit is closest to the rotation center.

  In this case, by adjusting the position and size of the positioning portion, the position where the mass portion is closest to the rotation center can be set. That is, this position can be easily changed. That is, the moving range of the mass part can be easily adjusted.

  (9) The automobile dynamic vibration damping device according to another aspect of the present invention is preferably configured as follows. The guide mechanism has a main body portion and a storage portion. The main body is rotatable relative to the rotating part. The storage portion is provided in the main body portion and stores the connecting portion.

  In this case, the dynamic vibration absorber can be reduced in size in the axial direction by storing the connecting portion in the storage portion of the guide mechanism.

  In the dynamic vibration damping device for automobiles of the present invention, the mass part can be stably operated.

1 is a cross-sectional view of a torque converter according to an embodiment of the present invention. The expanded sectional view of the part corresponding to a dynamic vibration damper in FIG. The front view of a dynamic vibration damper (when a link member is in a neutral state). The front view of a dynamic vibration damping device (when a link member swings).

[Overall configuration of torque converter]
FIG. 1 is a cross-sectional view of a torque converter 1 that employs a lock-up device as an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. OO shown in FIG. 1 is a rotation center line of the torque converter and the lockup device.

  Further, the term “circumferential direction (rotation direction)” used in the present embodiment refers to a “first circumferential direction (first rotation direction)” that is a counterclockwise direction and a “first direction” that is a clockwise direction. 2 circumferential directions (second rotational direction) ". As shown in FIGS. 3 and 4, the first circumferential direction (first rotation direction) is denoted by reference numeral R1, and the second circumferential direction (second rotation direction) is denoted by reference numeral R2.

  The torque converter 1 includes a front cover 3, a torque converter body 5, a lockup device 7, and a dynamic vibration absorber 9. The torque converter main body 5 has a torus-shaped fluid working chamber, and the fluid working chamber includes an impeller 11, a turbine 13, and a stator 17.

  The front cover 3 is a substantially disk-shaped member. The front cover 3 is connected to a crankshaft (not shown).

  The impeller 11 includes an impeller shell 11a, a plurality of impeller blades 11b fixed to the inside thereof, and an impeller hub 11c fixed to the inner peripheral portion of the impeller shell 11a. The outer peripheral edge of the impeller shell 11 a is welded to the outer peripheral portion of the front cover 3. The inner peripheral edge of the impeller shell 11a is welded to the impeller hub 11c.

  The turbine 13 is disposed to face the impeller 11 in the axial direction. The turbine 13 includes a turbine shell 14, a plurality of turbine blades 15 fixed inside the turbine shell 14, and a turbine hub 16 fixed to the inner peripheral edge of the turbine shell 14. An inner peripheral end portion of the turbine shell 14 is fixed to the turbine hub 16 by a rivet 20. A spline 16 a that engages with an input shaft (not shown) of the transmission is formed on the inner peripheral surface of the turbine hub 16. Thereby, the turbine hub 16 rotates integrally with the input shaft.

  The stator 17 is disposed between the inner periphery of the impeller 11 and the inner periphery of the turbine 13. The stator 17 rectifies the flow of hydraulic oil that returns from the turbine 13 to the impeller 11. The stator 17 has an annular stator shell 18 and a plurality of stator blades 19 provided on the outer peripheral surface of the stator shell 18. The stator shell 18 is supported by a cylindrical fixed shaft (not shown) via a one-way clutch 21.

  Thrust bearings 22 and 23 are disposed separately between the turbine hub 16 and the one-way clutch 21 and between the stator 17 and the impeller 11 in the axial direction.

[Structure of lock-up device 7]
The lock-up device 7 is for damping vibrations transmitted from the engine to the transmission. As shown in FIG. 1, the lock-up device 7 is disposed between the turbine 13 and the front cover 3 and is a mechanism for mechanically connecting the two. The lockup device 7 includes a piston 31, a drive plate 33, an intermediate plate 34, a float member 37, a driven plate 39, and a plurality of torsion springs 40.

<Piston>
The piston 31 is a member for connecting and disconnecting the clutch. The piston 31 is formed in a substantially disk shape having a hole. As shown in FIG. 1, an inner peripheral cylindrical portion 31 a extending toward the axial transmission side is formed on the inner peripheral portion of the piston 31. The inner peripheral cylindrical portion 31a is supported by the outer peripheral surface of the turbine hub 16 on the engine side so as to be movable in the circumferential direction and the axial direction. The piston 31 is in contact with the transmission-side surface of the turbine hub 16 so that the movement toward the axial transmission side is restricted.

  In addition, a seal ring 31 b is provided on the outer peripheral surface of the turbine hub 16 on the engine side so as to contact the inner peripheral surface of the inner peripheral side tubular portion 31 a of the piston 31. Thereby, the inner peripheral edge of the piston 31 is sealed. Further, an annular friction coupling portion 31 c is formed on the outer peripheral side of the piston 31. An annular friction facing 32 is fixed on the engine side of the friction coupling portion 31c.

<Drive plate>
The drive plate 33 is a substantially annular and disk-shaped member. The drive plate 33 can rotate around the rotation center O. The drive plate 33 has a fixed portion 33a on the inner peripheral portion, and has a plurality of engaging portions 33b on the outer peripheral side of the fixed portion 33a. The fixing portion 33 a is fixed to the piston 31 by the rivet 12. Each of the plurality of engaging portions 33b is formed on the outer peripheral portion of the drive plate 33 at a predetermined interval in the circumferential direction. An outer peripheral torsion spring 40a (described later) is disposed between the engaging portions 33b adjacent in the circumferential direction. The engaging portion 33b can contact the end portion of the outer peripheral side torsion spring 40a.

<Intermediate plate>
The intermediate plate 34 connects an outer periphery side torsion spring 40a and an inner periphery side torsion spring 40b (described later) in series. The intermediate plate 34 is a substantially annular and disk-shaped plate member. The intermediate plate 34 can rotate relative to the drive plate 33.

  As shown in FIG. 1, the intermediate plate 34 includes a first intermediate plate 34a and a second intermediate plate 34b. The first intermediate plate 34a is disposed on the axial direction engine side. The second intermediate plate 34b is disposed on the axial transmission side. The first intermediate plate 34a and the second intermediate plate 34b are arranged at a predetermined interval in the axial direction. A driven plate 39 is disposed between the first intermediate plate 34a and the second intermediate plate 34b. The first intermediate plate 34a and the second intermediate plate 34b are connected to each other by a plurality of fixing members such as a plurality of rivets (not shown) so that they cannot rotate relative to each other and cannot move in the axial direction.

  Windows 44a and 45a are formed in the first intermediate plate 34a and the second intermediate plate 34b, respectively. Between the axial direction of the window part 44a and the window part 45a, the torsion spring 40b of the inner peripheral side is arrange | positioned. The wall portions 44b and 45b facing each other in the circumferential direction in the window portions 44a and 45a are formed so as to be able to contact both end portions of the inner peripheral side torsion spring 40b. Cut and raised portions cut and raised in the axial direction are formed on the inner and outer peripheral portions of the window portions 44a and 45a.

  The second intermediate plate 34b has a plurality of engaging portions 45c that can be engaged with the outer peripheral side torsion spring 40a. Each of the plurality of engaging portions 45c is formed on the outer peripheral portion of the second intermediate plate 34b at a predetermined interval in the circumferential direction. Between the engaging portions 45c adjacent to each other in the circumferential direction, an outer peripheral torsion spring 40a is disposed. The engaging portion 45c can be in contact with a circumferential end of the outer torsion spring 40a.

<Float member>
The float member 37 is a member for operating adjacent torsion springs 40a on the outer peripheral side in series. The float member 37 is formed in a substantially annular shape. The float member 37 is supported by the drive plate 33 so as to be rotatable relative to the intermediate plate 34 (second intermediate plate 34 b) and the drive plate 33.

  As shown in FIG. 1, the float member 37 holds the radially outer side of the outer peripheral side torsion spring 40 a. In the float member 37, connecting portions 47a are formed at intervals in the circumferential direction. The connecting portion 47a is disposed between two adjacent outer peripheral torsion springs 40a, and is in contact with the end of the outer peripheral torsion spring 40a. Thereby, the two adjacent torsion springs 40a on the outer peripheral side operate in series.

<Driven plate>
The driven plate 39 is a substantially annular and disk-shaped member. Driven plate 39, Ru rotatable der around a rotation center O. -Driven plate 39 has a fixed portion 39a on the inner periphery, has a plurality of openings 39b on the outer peripheral side of the fixing portion 39a. The fixed portion 39 a is fixed to the turbine hub 16. The inner peripheral portion of the fixed portion 39a is fixed to the turbine hub 16 by a fixing member such as a bolt 39d.

  The opening 39b is a hole that penetrates in the axial direction. An inner periphery side torsion spring 40b is disposed in the opening 39b. Wall portions 39f facing each other in the circumferential direction in the opening portion 39b are formed so as to be able to contact both end portions of the inner peripheral side torsion spring 40b.

<Torsion spring>
The plurality of torsion springs 40 are composed of a plurality (for example, eight) of outer peripheral side torsion springs 40a and a plurality (for example, eight) of inner peripheral side torsion springs 40b.

  Each of the plurality of torsion springs 40a on the outer peripheral side is supported in the circumferential direction by a drive plate 33, a float member 37, and an intermediate plate 34.

  Specifically, each of the plurality of torsion springs 40a on the outer peripheral side is arranged in the circumferential direction by an engaging portion 33b of the drive plate 33, a connecting portion 47a of the float member 37, and an engaging portion 45c of the second intermediate plate 34b. It is supported by. In this state, the plurality of outer peripheral torsion springs 40a can be compressed by the drive plate 33 and the intermediate plate 34 (second intermediate plate 34b).

  Each of the plurality of torsion springs 40b on the inner peripheral side is supported in the circumferential direction by an intermediate plate 34 and a driven plate 39.

  Specifically, each of the plurality of inner peripheral torsion springs 40b is circumferentially formed by the window portion 44a of the first intermediate plate 34a, the window portion 45a of the second intermediate plate 34b, and the opening portion 39b of the driven plate 39. It is supported by. In this state, the plurality of torsion springs 40 b on the inner peripheral side can be compressed by the wall portions 44 b and 45 b of the window portions 44 a and 45 a of the intermediate plate 34 and the wall portion 39 f of the opening 39 b of the driven plate 39.

<Dynamic vibration absorber>
The dynamic vibration absorber 9 is for attenuating vibration transmitted from the engine to the transmission. As shown in FIGS. 1 and 2, the dynamic vibration absorber 9 is fixed to the turbine hub 16. Specifically, the dynamic vibration absorber 9 is fixed to the turbine hub 16 together with the turbine shell 14 by a fixing member such as a rivet 20.

  The dynamic vibration absorber 9 includes a rotating part 41, a plurality of inertia members 71 (an example of a mass body), a guide mechanism 81, and a link member 91 (an example of a connecting part).

  The rotating part 41 can rotate around the rotation center O. As illustrated in FIG. 2, the rotating unit 41 includes a first rotating member 51 and a second rotating member 61. The first rotating member 51 and the second rotating member 61 are arranged to face each other in the axial direction.

  The first rotating member 51 is formed in a substantially annular shape. The first rotating member 51 includes a first main body portion 53, a first fixing portion 55, and a first connection portion 57.

  The first main body 53 is formed in a substantially annular shape. The first fixing portion 55 is provided on the inner peripheral portion of the first main body portion 53. The first fixing portion 55 is fixed to the turbine shell 14. Specifically, the first fixing portion 55 has a first fixing hole portion 55a. The first fixing portion 55 is fixed to the turbine shell 14 by a fixing member such as the rivet 20 through the first fixing hole portion 55a.

  The first connection portion 57 is provided on the outer peripheral portion of the first main body portion 53. A link member 91 is swingably attached to the first connection portion 57. Specifically, the first connection portion 57 is provided with a first connection hole portion 57a penetrating in the axial direction. More specifically, a link member 91 is swingably attached to the first connection hole 57a via a connection member such as a rivet 58 and a collar member 59.

  The second rotating member 61 is formed in a substantially annular shape. The second rotating member 61 has a second main body portion 63, a second fixing portion 65, and a second connection portion 67.

  The second main body 63 has an inner circumferential side annular portion 63a, an axially extending portion 63b, and an outer circumferential side annular portion 63c. The annular portion 63a on the inner peripheral side is substantially annular. The axially extending portion 63b is integrally formed with the inner peripheral annular portion 63a so as to extend in the axial direction from the outer peripheral portion of the inner peripheral annular portion 63a. Specifically, the axially extending portion 63b is formed in a substantially cylindrical shape. The annular portion 63c on the outer peripheral side is substantially annular. The outer peripheral side annular portion 63c is formed integrally with the axially extending portion 63b so as to extend radially outward from the axially extending portion 63b.

  The second fixing portion 65 is provided in an inner peripheral portion of the second main body portion 63, for example, an annular portion 63a on the inner peripheral side. The second fixing portion 65 is disposed between the first fixing portion 55 of the first rotating member 51 and the turbine shell 14. The second fixing portion 65 is fixed to the turbine shell 14. Specifically, the second fixing portion 65 has a second fixing hole portion 65a. The second fixing portion 65 is fixed to the turbine shell 14 together with the first fixing portion 55 of the first rotating member 51 by the fixing member, for example, the rivet 20, through the second fixing hole portion 65a.

  The second connection portion 67 is provided on the outer peripheral portion of the second main body portion 63, for example, the annular portion 63c on the outer peripheral side. The second connection portion 67 is disposed to face the first connection portion 57. A link member 91 is swingably attached to the second connection portion 67. Specifically, the second connection portion 67 is provided with a second connection hole portion 67a penetrating in the axial direction. More specifically, a link member 91 is swingably attached to the second connection hole 67a via a connection member such as a rivet 58 and a collar member 59.

The connecting member, for example, the collar member 59 is disposed between the first connecting portion 57 and the second connecting portion 67. Specifically, the collar member 59 is disposed between the first connection portion 57 and the second connection portion 67 outside the axially extending portion 63b. The collar member 59 is formed in a substantially cylindrical shape. The collar member 59 has a small diameter cylindrical portion 59a and a large diameter cylindrical portion 59b. The small diameter cylindrical portion 59a engages with the link member 91 so that the link member 91 can swing around the small diameter cylindrical portion 59a. The large diameter cylindrical portion 59b is formed to have a larger diameter than the small diameter cylindrical portion 59a. The large diameter cylindrical portion 59b is disposed between the first rotating member 51 and the link member 91 in the axial direction. The link member 91 can swing with respect to the large-diameter cylindrical portion 59b.

  The connecting member, for example, the rivet 58 is disposed on the inner peripheral portion of the collar member 59. Specifically, the shaft portion of the rivet 58 is disposed on the inner peripheral portion of the collar member 59 (small diameter cylindrical portion 59a and large diameter cylindrical portion 59b), and the first connection hole portion 57a and the second connection hole portion 67a. Is done. The flange portions of the rivet 58 are provided at both end portions of the shaft portion, and engage with the lock-up device 7 side of the first connection portion 57 and the turbine 13 side of the second connection portion 67. As a result, the rivet 58 is attached to the first connecting portion 57 and the second connecting portion 67 so as not to move in the axial direction.

  The plurality of inertia members 71 can move relative to the rotation unit 41 when the rotation unit 41 rotates. The plurality of inertia members 71 move relative to the rotating unit 41 to attenuate the vibration of the rotating unit 41.

  Here, a plurality of sets of inertia members 71, for example, two sets of inertia members 71 can be moved relative to the rotating portion 41. In addition, the two sets of inertia members 71 can move relative to a fourth main body portion 83 (described later) of the guide mechanism 81. One set of inertia members 71 (a pair of inertia members 71) is composed of two inertia members 71.

  Specifically, as shown in FIGS. 2 to 4, the pair of inertia members 71 are disposed radially outward of the rotating portion 41 with the rotation center O as a reference. Here, each inertia member 71 is arranged so that the center of gravity G of the pair of inertia members 71 is located at a position spaced apart from the rotation center O in the radial direction.

  The pair of inertia members 71 (two inertia members 71) are arranged around the rotation center O. Here, the angles formed by the line segment A1 connecting the center of gravity G of each inertia member 71 adjacent around the rotation center O and the rotation center O are all the same. Further, this angle is the same in all systems in which the fourth main body 83 of the guide mechanism 81 is stationary. Here, this angle is, for example, 180 degrees.

  As shown in FIG. 2, the pair of inertia members 71 are arranged to face each other in the axial direction. Between the axial directions of the pair of inertia members 71, a fourth main body portion 83 of the guide mechanism 81 is disposed. As shown in FIGS. 3 and 4, the pair of inertia members 71 (two inertia members 71) are arranged in a certain radial direction (sliding direction SL), with the rotating portion 41 and the fourth main body portion 83 of the guide mechanism 81. Relative movement is possible.

  Here, a certain radial direction (sliding direction SL) indicates a direction along the first straight line C1 passing through the center of gravity G and the rotation center O of the inertia member 71. Here, one certain radial direction (sliding direction SL) corresponds to a direction along the first straight line C <b> 1 that passes through the center of gravity G and the rotation center O of each pair of inertia members 71. Hereinafter, in order to distinguish one radial direction from a radial direction extending radially from the rotation center O, it is referred to as a “sliding direction SL”.

  Each inertia member 71 has a third main body portion 73, a third connection portion 75, and a shaft support portion 77. The 3rd main-body part 73 is formed in the circular arc plate shape substantially. The third connection part 75 is provided in the third main body part 73. A link member 91 is swingably attached to the third connection portion 75.

  Specifically, as shown in FIG. 2, the third connection portion 75 is provided with a third connection hole 75 a penetrating in the axial direction. In the pair of third main body portions 73, the third connection hole portions 75a of the respective third connection portions 75 are disposed to face each other. As shown in FIGS. 3 and 4, the pair of third connection holes 75 a are formed on a first straight line C <b> 1 that passes through the center of gravity G and the rotation center O of each inertia member 71. A link member 91 is swingably attached to the pair of third connection holes 75a via a connection member, for example, a rivet 58.

  As shown in FIGS. 3 and 4, the shaft support portion 77 is provided in the third main body portion 73. In the pair of third main body portions 73, the shaft support portions 77 are arranged to face each other. Here, a plurality of (for example, four) shaft support portions 77 are provided in the third main body portion 73. 3 and 4, only one shaft support portion 77 is denoted by a reference numeral.

  A shaft member 85 b (described later) of the guide mechanism 81 is attached to each shaft support portion 77. Specifically, each shaft support portion 77 is provided with a shaft hole 77a penetrating in the axial direction. In the pair of third main body portions 73, the shaft hole portions 77 a of the shaft support portions 77 are disposed to face each other. Further, the two left shaft hole portions 77a in FIGS. 3 and 4 and the two right shaft hole portions 77a in FIGS. 3 and 4 have a center of gravity G and a rotation center O of each inertia member 71. Are arranged symmetrically with respect to the first straight line C1 passing through The shaft member 85b of the guide mechanism 81 is attached to the pair of shaft holes 77a.

  As shown in FIGS. 3 and 4, the guide mechanism 81 guides the inertia member 71 so that the inertia member 71 can be moved relative to the rotation unit 41 when the rotation unit 41 rotates. Specifically, the guide mechanism 81 guides the inertia member 71 in the slide direction SL when the rotating unit 41 rotates. More specifically, the guide mechanism 81 guides the inertia member 71 along the first straight line C <b> 1 that passes through the center of gravity G and the rotation center O of each pair of inertia members 71 when the rotating portion 41 rotates. In other words, the guide mechanism 81 is an inertia member in a direction approaching the second straight line C2 orthogonal to the first straight line C1 and passing through the rotation center O and a direction away from the second straight line C2 when the rotating unit 41 rotates. Guide 71.

  The guide mechanism 81 includes a fourth main body portion 83 (an example of a main body portion), a guide portion 85, and a protruding portion 87 (an example of a positioning portion). The fourth main body 83 is formed in a substantially annular shape. The fourth main body 83 is rotatable relative to the rotating portion 41 (the first rotating member 51 and the second rotating member 61). The fourth main body portion 83 engages with the inertia member 71 through the long hole portion 85a and the shaft member 85b. The fourth body portion 83 is disposed adjacent to the inertia member 71 and the rotating portion 41 in the axial direction.

  As shown in FIG. 2, specifically, the outer peripheral part of the 4th main-body part 83 is arrange | positioned between a pair of inertia members 71 (two inertia members 71) in an axial direction. An inner peripheral portion of the fourth main body portion 83 is disposed between the first rotating member 51 and the second rotating member 61 in the axial direction. On the inner peripheral side of the fourth main body portion 83, the axially extending portion 63b and the second fixing portion 65 of the second rotating member 61 are disposed. The inner peripheral part of the fourth main body part 83 is rotatable relative to the outer peripheral surface of the axially extending part 63 b of the second rotating member 61.

  The fourth body 83 is provided with a storage hole 89 (an example of a storage). The storage hole 89 is a hole for storing the link member 91. A plurality of (for example, two) storage hole portions 89 are provided in the fourth main body portion 83. Each storage hole 89 is substantially formed in a triangular shape. The shape of the storage hole 89 is formed so as not to contact the link member 91 when the link member 91 swings.

  Each storage hole 89 is arranged at a predetermined interval in the circumferential direction. In other words, each storage hole 89 is disposed at a position spaced apart from the circumferential direction by a predetermined angle. Here, this angle is, for example, 180 degrees. Each storage hole 89 is arranged between a plurality of protrusions 87, for example, two sets of protrusions 87 in the circumferential direction. Specifically, each storage hole 89 and each protrusion 87 (one set of protrusions 87) are arranged at intervals of 90 degrees in the circumferential direction.

  The guide portion 85 has a long hole portion 85a and a shaft member 85b. The long hole portion 85 a is provided in the fourth main body portion 83. Here, a plurality of (for example, four) long hole portions 85 a are provided in the fourth main body portion 83. Each elongated hole portion 85a extends in a direction along the first straight line C1 that passes through the center of gravity G and the rotation center O of the inertia member 71. Also, the two long hole portions 85a on the left side in FIGS. 3 and 4 and the two long hole portions 85a on the right side in FIGS. 3 and 4 have a center of gravity G and a rotation center O of each inertia member 71. The first straight line C1 passing therethrough is used as a reference and is arranged line-symmetrically. A shaft member 85b of the guide mechanism 81 is disposed in each long hole portion 85a.

  Each of a plurality (for example, four) of shaft members 85 b is disposed in each long hole portion 85 a and is attached to the inertia member 71. Specifically, the shaft portion of each shaft member 85 b is disposed in each long hole portion 85 a, and both end portions of each shaft member 85 b are attached to the pair of inertia members 71. As each shaft member 85b moves along each long hole portion 85a, the pair of inertia members 71 move in the slide direction SL.

  The protrusion 87 is for positioning the inertia member 71. Specifically, the protrusion 87 positions the inertia member 71 at a position where the center of gravity G of the inertia member 71 is closest to the rotation center O.

  Here, a plurality of protrusions 87 are provided on the fourth main body 83. Each protrusion 87 is provided so as to protrude in the axial direction from the fourth main body 83. Specifically, the plurality of protrusions 87 constitute a plurality of sets of protrusions 87, for example, two sets of protrusions 87. Here, the one set of protrusions 87 includes two protrusions 87.

  The inertia member 71 abuts on the protruding portion 87. For example, the circumferential end of the inertia member 71 abuts on the protrusion 87. Each protrusion part 87 is arrange | positioned at predetermined intervals in the circumferential direction. In other words, each protrusion 87 is disposed at a position spaced apart from the circumferential direction by a predetermined angle. Here, this angle is, for example, 180 degrees.

  Each projecting portion 87 has a shaft portion 87a and an elastic portion 87b. The shaft portion 87 a is formed integrally with the fourth main body portion 83. The elastic portion 87b is for alleviating the collision with the inertia member 71, and is provided on the outer periphery of the shaft portion 87a.

As shown in FIGS. 3 and 4, the link member 91 is connected to the rotating portion 41 and the inertia member 71. The link member 91 is swingable with respect to the rotating part 41 and the inertia member 71. Specifically, the link member 91 is disposed in the storage hole 89 of the fourth main body portion of the guide mechanism 81, and can swing with respect to the rotating portion 41 and the inertia member 71 inside the storage hole 89. Further, the axial thickness of the link member 91 is thicker than the axial thickness of the fourth main body 83 of the guide mechanism 81.

  The link member 91 is formed in a plate shape that is long in one direction. An inner peripheral side end portion 92 (an example of one end portion of the connecting portion) of the link member 91 is swingably attached to the rotating portion 41 (the first rotating member 51 and the second rotating member 61). Specifically, the inner peripheral end 92 of the link member 91 is disposed between the first connecting portion 57 of the first rotating member 51 and the second connecting portion 67 of the second rotating member 61 in the axial direction.

  Further, as shown in FIG. 2, a large-diameter cylindrical portion 59 b of the collar member 59 is arranged between the inner peripheral side end portion 92 of the link member 91 and the first connection portion 57 of the first rotating member 51. Is done. Furthermore, a fourth connection hole 92 a is provided at the inner peripheral side end 92 of the link member 91. The fourth connection hole 92 a engages with a connection member, for example, a collar member 59. The fourth connection hole 92 a is rotatable with respect to the collar member 59. Specifically, the small diameter cylindrical portion 59a of the collar member 59 is disposed in the fourth connection hole 92a, and the fourth connection hole 92a is rotatable with respect to the outer peripheral portion of the small diameter cylindrical portion 59a of the collar member 59. .

  As shown in FIG. 2, a connecting member, for example, a shaft portion of a rivet 58 is disposed on the inner peripheral portion of the collar member 59 (small diameter cylindrical portion 59a and large diameter cylindrical portion 59b). The flange portion of the rivet 58 is engaged with the lockup device 7 side of the first connection portion 57 of the first rotation member 51 and the turbine 13 side of the second connection portion 67 of the second rotation member 61. In this way, the link member 91 is in the inner peripheral side end portion 92 of the link member 91 with respect to the first rotating member 51 (first connecting portion 57) and the second rotating member 61 (second connecting portion 67). , Swingably mounted.

  As shown in FIGS. 3 and 4, the outer peripheral side end portion 93 (an example of the other end portion of the connecting portion) of the link member 91 is swingably attached to the inertia member 71 (a pair of inertia members 71). Specifically, the outer peripheral side end portion 93 of the link member 91 is disposed between the axial directions of the pair of inertia members 71.

  As shown in FIG. 2, the outer peripheral side end portion 93 of the link member 91 is provided with a fifth connection hole portion 93 a. The fifth connection hole 93 a engages with a connection member, for example, the collar member 60. The fifth connection hole 93 a is rotatable with respect to the collar member 60. A connecting member, for example, a shaft portion of the rivet 58 is disposed on the inner peripheral portion of the collar member 60. The flange portion of the rivet 58 is engaged with the lock-up device 7 side of one inertia member 71 and the turbine 13 side of the other inertia member 71. In this way, the link member 91 is swingably attached to the pair of inertia members 71 (the pair of third connection portions 75) at the outer peripheral side end portion 93 of the link member 91.

  Further, as shown in FIG. 3, the link member 91 positions the inertia member 71. Specifically, the link member 91 positions the inertia member 71 at a position where the center of gravity G of the inertia member 71 is farthest from the rotation center O. When the two swing centers of the link member 91 are arranged on the first straight line C1 passing through the center of gravity G and the rotation center O of the inertia member 71, the center of gravity G of the inertia member 71 is separated from the rotation center O. It is arranged at the most distant position.

  Specifically, the third straight line C3 passing through the center of the fourth connection hole 92a and the center of the fifth connection hole 93a in the link member 91 passes through the center of gravity G and the rotation center O of the inertia member 71. When arranged on one straight line C1, the center of gravity G of the inertia member 71 is arranged at a position farthest from the rotation center O. As a result, the inertia member 71 is positioned at a position farthest from the rotation center O.

  Here, the position where the center of gravity G of the inertia member 71 is farthest from the rotation center O is from the swing center of the inner peripheral side end portion 92 of the link member 91 to the swing center of the outer peripheral side end portion 93 of the link member 91. It is determined by the length L.

  As described above, when the center of gravity G of the inertia member 71 is closest to the rotation center O, the inertia member 71 is in contact with the protruding portion 87. The position where the center of gravity G of the inertia member 71 is closest to the rotation center O corresponds to the position where the swing center of the outer peripheral side end portion 93 of the link member 91 is closest to the rotation center O.

[Operation]
<Operation of torque converter body and lock-up device>
In the low engine speed range, the piston 31 moves to the transmission side due to the pressure difference between the hydraulic oils on both sides of the piston 31 in the axial direction. That is, the friction facing 32 is separated from the front cover 3 and the lock-up is released. When the lockup is released, torque from the front cover 3 is transmitted from the impeller 11 to the turbine 13 via hydraulic oil.

  When the speed ratio of the torque converter 1 increases and the engine speed reaches a constant speed, the hydraulic oil on the engine side of the piston 31 is discharged. As a result, the piston 31 is moved to the front cover 3 side, and the friction facing 32 is pressed against the friction surface of the front cover 3. As a result, the torque of the front cover 3 is transmitted to the outer peripheral torsion spring 40a via the piston 31 and the drive plate 33.

  Further, the torque transmitted to the outer peripheral side torsion spring 40 a is transmitted to the inner peripheral side torsion spring 40 b via the intermediate plate 34. The torque output from the inner peripheral side torsion spring 40 b is transmitted to the turbine hub 16 via the driven plate 39.

  The two torsion springs 40 a on the outer peripheral side are connected by a float member 37. For this reason, these outer peripheral side torsion springs 40 a are operated in series by the float member 37.

  Thus, the front cover 3 is mechanically coupled to the turbine hub 16 by the operation of the lockup device 7. That is, the torque of the front cover 3 is directly output to the input shaft of the transmission via the turbine hub 16.

  Here, when the engine torque fluctuates, vibrations are absorbed by expansion and contraction of the torsion spring 40 (the outer peripheral side torsion spring 40a and the inner peripheral side torsion spring 40b) and the hysteresis torque of each part. In this way, the torque fluctuation is attenuated by the lockup device 7.

<Operation of dynamic vibration absorber>
The dynamic vibration absorber 9 is attached to the turbine hub 16. For this reason, when torque fluctuation is transmitted from the driven plate 39 of the lockup device 7 to the turbine hub 16, the dynamic vibration absorber 9 is activated by this torque fluctuation.

  In the state of FIG. 3, when torque fluctuation occurs in the turbine hub 16, the rotating portion 41 (the first rotating member 51 and the second rotating member 61) rotates. Then, as shown in FIG. 4, the link member 91 attached to the rotating portion 41 swings.

  For example, in the state of FIG. 3, when the rotating part 41 rotates in the first rotation direction R1, the inner peripheral side end 92 of the link member 91 moves in the first rotation direction R1. Then, as shown in FIG. 4, the outer peripheral side end portion 93 of the link member 91 moves along the first straight line C1 in a direction approaching the second straight line C2. Then, by the movement of the outer peripheral side end portion 93 of the link member 91, two sets of inertia members 71 (only one set of inertia members 71 are shown in FIGS. 3 and 4) are guided by the guide mechanism 81, and the second straight line Move in a direction approaching C2.

  As shown in FIG. 4, when the two sets of mass bodies come into contact with the two sets of protrusions 87, the movement of the two sets of mass bodies stops. The position where the two mass bodies stop moving is the position where the center of gravity G of the inertia member 71 is closest to the rotation center O.

  Thus, when the rotating part 41 rotates in the first rotation direction R1 and the two sets of inertia members 71 move toward the second straight line C2, centrifugal force acts on the two sets of inertia members 71. ing. Here, the rotational force, which is a component of centrifugal force, is a force that resists the rotational force of the rotating part 41 due to torque fluctuation. When the rotational force, which is a component of centrifugal force, is greater than the rotational force of the rotating part 41 due to torque fluctuation, the rotating part 41 rotates in the second rotational direction R2.

  In this case, the inner peripheral end 92 of the link member 91 moves in the second rotation direction R2. Then, the outer peripheral side end 93 of the link member 91 moves along the first straight line C1 in a direction away from the second straight line C2. Then, by the movement of the outer peripheral side end portion 93 of the link member 91, two sets of inertia members 71 (only the pair of inertia members 71 are shown in FIGS. 3 and 4) are guided by the guide mechanism 81, and the second straight line C2 Move away from.

  Here, when the two swing centers of the link member 91 are disposed on the first straight line C1, the center of gravity G of the inertia member 71 is disposed at a position farthest from the rotation center O. In other words, this position is a position where the two inertia members 71 are farthest from the rotation center O.

  In the state shown in FIG. 3, when the rotating part 41 rotates in the second rotating direction R2, the basic operation and action of the dynamic vibration absorber 9 is different from that of the dynamic vibration absorber 9 although the swinging direction of the link member 91 is different. This is the same as when rotating in the first rotation direction R1. For this reason, the description in the case where the rotating unit 41 rotates in the second rotation direction R2 is omitted here.

  As described above, the two sets of inertia members 71 reciprocate with respect to the rotating portion 41. Further, when this reciprocating motion is performed, centrifugal force acts on the two sets of inertia members 71. The centrifugal force acting on the two sets of inertia members 71 causes the rotation unit 41 to rotate in the second rotation direction R2 (or when the rotation unit 41 rotates in the first rotation direction R1 (or the second rotation direction R2). It acts as a force for rotating in the first rotation direction R1). By the action of this centrifugal force, the rotational fluctuation of the rotating part 41, that is, the torque fluctuation of the turbine 13 hub is attenuated.

[Feature]
(1) The dynamic vibration absorber 9 is for attenuating vibration transmitted from the engine to the transmission. The dynamic vibration absorber 9 includes a rotating portion 41, a pair of inertia members 71, a link member 91, and a guide mechanism 81.

  The rotating part 41 can rotate around the rotation center O. Each of the pair of inertia members 71 can attenuate the vibration of the rotating portion 41 by moving relative to the rotating portion 41 when the rotating portion 41 rotates. The link member 91 connects the rotating part 41 and the inertia member 71. The guide mechanism 81 guides the inertia member 71 in the radial direction when the rotating unit 41 rotates.

  In the dynamic vibration absorber 9, when the rotating portion 41 rotates around the rotation center O, the inertia member 71 connected to the rotating portion 41 by the link member 91 is guided in the radial direction by the guide mechanism 81. As a result, the inertia member 71 moves relative to the rotating portion 41 and attenuates the vibration of the rotating portion 41.

  Thus, in the dynamic vibration absorber 9, the rotating portion 41 and each inertia member 71 are connected by the link member 91, and the movement of each inertia member 71 is restricted in the radial direction by the guide mechanism 81. That is, each inertia member 71 moves in a direction different from the rotation direction of the rotation unit 41, for example, in the slide direction SL while being supported by the rotation unit 41 by the link member 91.

  Specifically, in the embodiment, the pair of inertia members 71 are arranged at the target position with respect to the second straight line C <b> 2 passing through the rotation center O. Here, consider a case where one center of gravity of the pair of inertia members 71 is located above the second straight line C2, and the other center of gravity of the pair of inertia members 71 is located below the second straight line C2. In this state, when the rotation of the rotating unit 41 becomes low, each inertia member 71 moves downward (drops) due to gravity.

  At this time, in a state where each inertia member 71 is connected to the rotation portion 41 by each link member 91, the rotation portion 41 is moved in the first rotation direction R1 and the second rotation direction R2 when one inertia member 71 is about to fall. Try to rotate to either one. On the other hand, when the other inertia member 71 is about to fall, the rotating portion 41 tries to rotate in either one of the first rotation direction R1 and the second rotation direction R2. That is, when both of the pair of inertia members 71 are about to fall, the rotation of the rotating portion 41 is canceled.

  For this reason, even if the rotation part 41 becomes a low rotation (even if the centrifugal force is insufficient), the inertia member 71 is not easily dropped in the direction of gravity and is not easily affected by the rotation of the rotation part 41. Thus, compared with the prior art in which the inertia member 71 can freely operate with respect to the rotating member, the dynamic vibration absorber 9 can operate the inertia member 71 stably.

  (2) The dynamic vibration absorber 9 is preferably configured as follows. An inner peripheral end 92 of the link member 91 is swingably attached to the rotating part 41. The outer peripheral side end portion 93 of the link member 91 is swingably attached to the inertia member 71.

  In this case, the link member 91 is swung by the rotation of the rotating portion 41, and the inertia member 71 is moved in the radial direction by the guide mechanism 81 in conjunction with the swing of the link member 91. As described above, the rotational motion of the rotating portion 41 can be changed to the linear motion of the inertia member 71 by the link member 91 and the guide mechanism 81. Thereby, compared with the prior art in which the inertia member 71 can operate | move freely with respect to a rotation member, in this dynamic vibration absorber 9, the inertia member 71 can be operated stably.

  (3) The dynamic vibration absorber 9 is preferably configured as follows. There are a plurality of inertia members 71. Each of the plurality of inertia members 71 is arranged around the rotation center O. The angle formed by the line segment A1 connecting the center of gravity G of the inertia member 71 adjacent to the rotation center O and the rotation center O is the same.

  In this case, since the plurality of inertia members 71 are evenly arranged around the rotation center O, the balance during the movement of the inertia member 71 can be appropriately maintained.

  (4) The dynamic vibration absorber 9 is preferably configured as follows. The guide mechanism 81 includes a fourth main body portion 83 that can rotate relative to the rotating portion 41 and a guide portion 85 that guides the inertia member 71 in the radial direction.

  In this case, the fourth main body portion 83 of the guide mechanism 81 operates as a float body with respect to the rotating portion 41, and the guide portion 85 of the guide mechanism 81 guides the inertia member 71 in the radial direction. As described above, by operating the fourth main body 83 independently of the rotation of the rotation unit 41, the inertia member 71 can be guided in the radial direction by the guide unit 85 even if the rotation unit 41 rotates. .

  (5) The dynamic vibration absorber 9 is preferably configured as follows. The guide portion 85 has a long hole portion 85a and a shaft member 85b. The long hole portion 85a is provided in the fourth main body portion 83 of the guide mechanism 81 and extends in a direction along the first straight line C1 that passes through the center of gravity G and the rotation center O of the inertia member 71. The shaft member 85 b is disposed in the long hole portion 85 a and is fixed to the inertia member 71.

  In this case, when the rotating portion 41 rotates, the inertia member 71 moves in the radial direction via the link member 91 by the shaft member 85b and the long hole portion 85a. Thus, even if the rotating part 41 rotates, the inertia member 71 can be linearly operated by the link member 91 and the guide mechanism 81. Thereby, compared with the prior art in which the inertia member 71 can operate | move freely with respect to a rotation member, in this dynamic vibration absorber 9, the inertia member 71 can be operated stably.

  (6) The dynamic vibration absorber 9 is preferably configured as follows. The inertia member 71 is positioned by the link member 91 at a position where the center of gravity G of the inertia member 71 is farthest from the rotation center O. The inertia member 71 is positioned by the guide mechanism 81 at a position where the center of gravity G of the inertia member 71 is closest to the rotation center O.

  In this case, the moving range in which the inertia member 71 moves in the radial direction is determined by the link member 91 and the guide mechanism 81. Thereby, the movement range of the inertia member 71 can be restrict | limited without preparing a special member.

  (7) The dynamic vibration absorber 9 is preferably configured as follows. An inner peripheral end 92 of the link member 91 is swingably attached to the rotating part 41. The outer peripheral side end portion 93 of the link member 91 is swingably attached to the inertia member 71. Depending on the length from the swing center of the inner peripheral end 92 of the link member 91 to the swing center of the outer peripheral end 93 of the link member 91, the inertia member 71 has the center of gravity G of the inertia member 71 at the rotation center O. Is positioned at a position farthest from the center.

  In this case, the position where the inertia member 71 is farthest from the rotation center O can be set by adjusting the length of the link member 91. That is, this position can be easily changed. That is, the movement range of the inertia member 71 can be easily adjusted.

  (8) The dynamic vibration absorber 9 is preferably configured as follows. The guide mechanism 81 has a fourth main body portion 83 and a protruding portion 87. The fourth main body portion 83 can rotate relative to the rotating portion 41. The protruding portion 87 is provided on the fourth main body portion 83. The protrusion 87 positions the inertia member 71 at a position where the center of gravity G of the inertia member 71 is closest to the rotation center O.

  In this case, the position where the inertia member 71 is closest to the rotation center O can be set by adjusting the position and size of the protrusion 87. That is, this position can be easily changed. That is, the movement range of the inertia member 71 can be easily adjusted.

  (9) The dynamic vibration absorber 9 is preferably configured as follows. The guide mechanism 81 has a fourth main body 83 and a storage hole 89. The fourth main body portion 83 can rotate relative to the rotating portion 41. The storage hole 89 is provided in the fourth main body 83 and stores the link member 91.

  In this case, by storing the link member 91 in the storage hole 89 of the guide mechanism 81, the dynamic vibration absorber 9 can be reduced in size in the axial direction.

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

  (A) In the above-described embodiment, an example in which the dynamic vibration absorber 9 is mounted on the turbine 13 hub has been described. However, the dynamic vibration absorber 9 may be mounted on the intermediate plate 34 and / or the driven plate 39.

  (B) In the above embodiment, an example in which the long hole portion 85a of the guide portion 85 is formed in the fourth main body portion 83 of the guide mechanism 81 and the shaft member 85b of the guide portion 85 is attached to the inertia member 71 is shown. It was. Instead, the elongated hole portion 85 a of the guide portion 85 may be formed in the inertia member 71, and the shaft member 85 b of the guide portion 85 may be attached to the fourth main body portion 83 of the guide mechanism 81.

  (C) In the said embodiment, although the example in case the dynamic vibration absorber 9 has two sets of inertia members 71 (a pair of inertia members 71x2 sets) was shown, the number of sets of the inertia members 71 is two or more sets. Any number of pairs is possible. Moreover, although the example in the case of comprising each pair of inertia members 71 from a pair of inertia members 71 was shown, you may comprise by one inertia member 71.

  (D) In the above embodiment, an example in which the protrusion 87 positions the inertia member 71 at a position where the center of gravity G of the inertia member 71 is closest to the rotation center O has been described. Instead of this, the inertia member 71 may be positioned by the end portion of the long hole portion 85a close to the second straight line C2. The first straight line C1 is a first straight line C1 that passes through the center of gravity G and the rotation center O of the inertia member 71. The second straight line C2 is a straight line that is orthogonal to the first straight line C1 and passes through the rotation center O.

  (E) In the above embodiment, an example in which each protrusion 87 protrudes from the fourth main body 83 to the turbine 13 side is shown, but each protrusion 87 is locked up from the fourth main body 83. You may protrude to the apparatus 7 side. Further, the number of the protrusions 87 may be any number as long as it is at least one.

  (F) In the above-described embodiment, an example in which the plurality of long hole portions 85a are provided in the fourth main body portion 83 of the guide mechanism 81 has been described. Any number is acceptable. Further, the number of shaft holes 77a and the number of shaft members 85b engaged with the long holes 85a may be any number as long as the number of the long holes 85a is the same.

9 Dynamic vibration absorber
41 Rotating part 51 First rotating member 71 Inertia member 81 Guide mechanism 83 Fourth main body part 85 Guide part 85a Long hole part 85b Shaft member 87 Projection part 89 Storage hole part 91 Link member 92 Inner peripheral side end part of link member 93 Link Outer peripheral end C1 First straight line G Center of gravity of inertia member O Center of rotation

Claims (9)

A vibration absorber for an automobile for attenuating vibration transmitted from an engine to a transmission,
A rotating part rotatable around the center of rotation;
A plurality of mass parts capable of attenuating vibration of the rotating part by moving relative to the rotating part during rotation of the rotating part;
A connecting part for connecting the rotating part and the mass part;
A guide mechanism for guiding the mass part in a radial direction when the rotary part rotates;
A vibration absorber for automobiles comprising: One end of the connecting portion is swingably attached to the rotating portion, and the other end of the connecting portion is swingably attached to the mass portion.
The dynamic vibration absorber for automobiles according to claim 1. Each of the plurality of mass parts is arranged around the rotation center,
The angle formed by the line segment connecting the center of gravity of the mass part adjacent to the rotation center and the rotation center is the same.
The dynamic vibration absorber for automobiles according to claim 1 or 2. The guide mechanism includes a main body portion that is rotatable relative to the rotating portion, and a guide portion that guides the mass portion in the radial direction.
The dynamic vibration absorber for automobiles according to any one of claims 1 to 3. The guide part is provided in one of the mass part and the main body part, and is disposed in the elongated hole part extending in a direction along a straight line passing through the center of gravity of the mass part and the rotation center. And a shaft member fixed to the other of the mass part and the main body part ,
The dynamic vibration absorber for automobiles according to claim 4. The mass portion is positioned by the connecting portion at a position where the center of gravity of the mass portion is farthest from the rotation center,
The mass portion is positioned by the guide mechanism at a position where the center of gravity of the mass portion is closest to the rotation center.
The dynamic vibration absorber for automobiles according to any one of claims 1 to 5. One end of the connecting part is swingably attached to the rotating part, and the other end of the connecting part is swingably attached to the mass part.
According to the length from the swing center of the one end to the swing center of the other end, the mass unit is positioned at a position where the center of gravity of the mass unit is farthest from the rotation center.
The dynamic vibration absorber for automobiles according to claim 6. The guide mechanism includes a main body that is rotatable relative to the rotating unit, a positioning unit that is provided in the main body and that positions the mass unit at a position where the center of gravity of the mass unit is closest to the rotation center Having
The dynamic vibration absorber for automobiles according to claim 6 or 7. The guide mechanism includes a main body that is rotatable relative to the rotating part, and a storage part that is provided in the main body part and stores the coupling part.
The dynamic vibration absorber for automobiles according to any one of claims 1 to 8.