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WO2016125382A1 - Dispositif amortisseur dynamique de vibrations pour véhicule automobile - Google Patents

Dispositif amortisseur dynamique de vibrations pour véhicule automobile Download PDF

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Publication number
WO2016125382A1
WO2016125382A1 PCT/JP2015/084125 JP2015084125W WO2016125382A1 WO 2016125382 A1 WO2016125382 A1 WO 2016125382A1 JP 2015084125 W JP2015084125 W JP 2015084125W WO 2016125382 A1 WO2016125382 A1 WO 2016125382A1
Authority
WO
WIPO (PCT)
Prior art keywords
mass
rotating
center
dynamic vibration
vibration absorber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/084125
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English (en)
Japanese (ja)
Inventor
祥行 萩原
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exedy Corp
Original Assignee
Exedy Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Exedy Corp filed Critical Exedy Corp
Priority to DE112015005848.6T priority Critical patent/DE112015005848T5/de
Publication of WO2016125382A1 publication Critical patent/WO2016125382A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
    • F16F15/1471—Masses connected to driveline by a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces

Definitions

  • the present invention relates to a dynamic vibration absorber for automobiles.
  • a conventional torque converter including a damper device and a dynamic vibration absorber has been disclosed (see Patent Document 1).
  • the damper device reduces torque fluctuations over a wide range of rotation speeds
  • the dynamic vibration absorber reduces torque fluctuations due to resonance or the like at specific rotation speeds.
  • the rotation of the engine includes a rotating member (10) and an inertial mass portion (9) that is swingably disposed on the rotating member via a rolling roller (27).
  • FIG. 1 and FIG. 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.
  • the inertial mass portion swings in a circular orbit with respect to the rotating member via the rolling roller.
  • 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.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a dynamic vibration absorber capable of operating a mass part stably.
  • a dynamic vibration absorber for an automobile 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.
  • 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.
  • 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.
  • each mass part is 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.
  • the dynamic vibration absorber can stably operate the mass portion.
  • the automobile dynamic vibration damping device 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 connecting portion is swung by the rotation of the rotating portion, and the mass portion is moved in the radial direction by the guide mechanism in conjunction with the swinging of the connecting portion.
  • 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.
  • the dynamic vibration absorber for automobiles 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.
  • the automobile dynamic vibration damping device 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.
  • 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.
  • the guide portion of the guide mechanism guides the mass portion in the radial direction.
  • the automobile dynamic vibration damping device 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 guide portion.
  • the automobile dynamic vibration damping device 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.
  • the moving range in which the mass portion moves in the radial direction is determined by the connecting portion and the guide mechanism.
  • the movement range of a mass part can be restrict
  • the automobile dynamic vibration damping device 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.
  • the position at which the mass portion is farthest 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.
  • the automobile dynamic vibration damping device 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.
  • 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.
  • the automobile dynamic vibration damping device 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.
  • the dynamic vibration absorber can be downsized in the axial direction by storing the connecting portion in the storage portion of the guide mechanism.
  • the mass part can be operated stably.
  • FIG. 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).
  • 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.
  • circumferential direction (rotation direction) 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) ".
  • first circumferential direction (first rotation direction) is denoted by reference numeral R1
  • second circumferential direction (second rotation direction) is denoted by reference numeral R2.
  • the torque converter 1 has 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 so as 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 arranged 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.
  • 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.
  • 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.
  • 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.
  • a seal ring 31b is provided on the outer peripheral surface of the turbine hub 16 on the engine side so as to come into contact with the inner peripheral surface of the inner peripheral side tubular portion 31a of the piston 31. Thereby, the inner peripheral edge of the piston 31 is sealed.
  • 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.
  • 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.
  • 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.
  • the intermediate plate 34 has 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.
  • Window portions 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
  • 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 torsion spring 40a on the outer peripheral side.
  • 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.
  • an outer peripheral torsion spring 40a is disposed between the engaging portions 45c adjacent to each other in the circumferential direction. The engaging portion 45c can be in contact with a circumferential end of the outer torsion spring 40a.
  • 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.
  • the float member 37 holds the outer side in the radial direction of the outer peripheral side torsion spring 40a.
  • 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.
  • the driven plate 39 is a substantially annular and disk-shaped member.
  • the driven plate 39 can rotate around the rotation center O.
  • the driven plate 39 is a substantially annular and disk-shaped member.
  • the driven plate 39 has a fixed portion 39a on the inner peripheral portion, and has a plurality of openings 39b on the outer peripheral side of the fixed 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 penetrating 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.
  • 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 the drive plate 33, the float member 37, and the intermediate plate 34.
  • 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.
  • 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.
  • 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.
  • 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 substantially in an 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.
  • 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.
  • 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 substantially annular.
  • 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 annular portion 63a on the inner peripheral side, an axially extending portion 63b, and an annular portion 63c on the outer peripheral side.
  • 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.
  • 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.
  • 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 part 67 is provided in the outer peripheral part of the second main body part 63, for example, the annular part 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.
  • 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 in a swingable manner.
  • 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.
  • 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 be moved relative to the rotating portion 41 when the rotating portion 41 rotates.
  • the plurality of inertia members 71 move relative to the rotating unit 41 to attenuate the vibration of the rotating unit 41.
  • 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.
  • 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.
  • the pair of inertia members 71 are arranged radially outward of the rotating portion 41 with the rotation center O as a reference.
  • 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 are arranged around the rotation center O.
  • 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.
  • this angle is, for example, 180 degrees.
  • 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.
  • a certain radial direction 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.
  • one certain radial direction 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.
  • sliding direction SL 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.
  • the third connection portion 75 is provided with a third connection hole 75 a penetrating in the axial direction.
  • the third connection hole portions 75a of the respective third connection portions 75 are disposed to face each other.
  • 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.
  • the shaft support portion 77 is provided in the third main body portion 73.
  • the shaft support portions 77 are arranged to face each other.
  • 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 85b (described later) of the guide mechanism 81 is attached to each shaft support portion 77.
  • each shaft support portion 77 is provided with a shaft hole 77a penetrating in the axial direction.
  • the shaft hole portions 77 a of the shaft support portions 77 are disposed to face each other.
  • 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.
  • the shaft member 85b of the guide mechanism 81 is attached to the pair of shaft holes 77a.
  • 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.
  • 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 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.
  • 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.
  • the outer peripheral portion of the fourth main body portion 83 is disposed between the pair of inertia members 71 (two inertia members 71) in the 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.
  • the axially extending portion 63b and the second fixing portion 65 of the second rotating member 61 are disposed on the inner peripheral side of the fourth main body portion 83.
  • 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.
  • the storage holes 89 are arranged at a predetermined interval in the circumferential direction.
  • each storage hole 89 is disposed at a position spaced apart from the circumferential direction by a predetermined angle.
  • 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.
  • each storage hole 89 and each protrusion 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.
  • 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.
  • 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.
  • a plurality of (for example, four) shaft members 85b are arranged in the respective long hole portions 85a and 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 projecting portion 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.
  • a plurality of protruding portions 87 are provided in the fourth main body portion 83.
  • Each protrusion 87 is provided so as to protrude in the axial direction from the fourth main body 83.
  • the plurality of protrusions 87 constitute a plurality of sets of protrusions 87, for example, two sets of protrusions 87.
  • the one set of protrusions 87 includes two protrusions 87.
  • the inertia member 71 comes into contact with the protruding portion 87.
  • the circumferential end of the inertia member 71 abuts on the protrusion 87.
  • Each protrusion part 87 is arrange
  • each protrusion 87 is disposed at a position spaced apart from the circumferential direction by a predetermined angle.
  • this angle is, for example, 180 degrees.
  • Each protrusion 87 has a shaft part 87a and an elastic part 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.
  • 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.
  • 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.
  • the axial thickness of the link member 91 is thinner than the axial thickness of the fourth main body portion 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).
  • 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.
  • 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.
  • 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. .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the center of gravity G of the inertia member 71 is arranged at a position farthest from the rotation center O.
  • the inertia member 71 is positioned at a position farthest from the rotation center O.
  • 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.
  • the inertia member 71 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.
  • the torque transmitted to the outer periphery side torsion spring 40 a is transmitted to the inner periphery 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.
  • the front cover 3 is mechanically connected 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.
  • the vibration is absorbed by the 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.
  • 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.
  • 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.
  • centrifugal force acts on the two sets of inertia members 71.
  • the rotational force which is a component of centrifugal force
  • the rotational force is a force that resists the rotational force of the rotating part 41 due to torque fluctuation.
  • the rotational force which is a component of centrifugal force
  • the rotating part 41 rotates in the second rotational direction R2.
  • the inner peripheral end 92 of the link member 91 moves in the second rotation direction R2.
  • 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.
  • two sets of inertia members 71 are guided by the guide mechanism 81, and the second straight line C2 Move away from.
  • the center of gravity G of the inertia member 71 is arranged at a position farthest from the rotation center O.
  • this position is a position where the two inertia members 71 are farthest from the rotation center O.
  • 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).
  • the rotational fluctuation of the rotating part 41 that is, the torque fluctuation of the turbine 13 hub is attenuated.
  • 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.
  • 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.
  • the inertia member 71 moves relative to the rotating portion 41 and attenuates the vibration of the rotating portion 41.
  • 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.
  • the pair of inertia members 71 are arranged at target positions with respect to the second straight line C2 passing through the rotation center O.
  • one center of gravity of the pair of inertia members 71 is located above the second straight line C2
  • the other center of gravity of the pair of inertia members 71 is located below the second straight line C2.
  • each inertia member 71 moves downward (drops) due to gravity.
  • the dynamic vibration absorber 9 can operate the inertia member 71 stably.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the inertia member 71 can be guided in the radial direction by the guide unit 85 even if the rotation unit 41 rotates. .
  • 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.
  • 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.
  • the inertia member 71 can be linearly operated by the link member 91 and the guide mechanism 81.
  • the inertia member 71 can be operated stably.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the dynamic vibration absorber 9 can be downsized in the axial direction.
  • 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.
  • 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.
  • the number of the long hole portions 85a may be at least one or more. 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

La présente invention concerne un dispositif amortisseur dynamique de vibrations permettant d'actionner de manière stable une partie masse. Le dispositif (9) amortisseur dynamique de vibrations sert à atténuer les vibrations transmises d'un moteur à une transmission. Ledit dispositif (9) amortisseur dynamique de vibrations est pourvu d'une section tournante (41), d'un élément inertiel (71), d'un élément de liaison (91) et d'un mécanisme de guidage (81). La section tournante (41) peut tourner autour d'un centre de rotation (O). L'élément inertiel (71) peut atténuer les vibrations de la section tournante (41) en se déplaçant par rapport à la section tournante (41) lorsque la section tournante (41) est en rotation. L'élément de liaison (91) relie la section tournante (41) à l'élément inertiel (71). Le mécanisme de guidage (81) guide l'élément inertiel (71) dans la direction radiale lors de la rotation de la section tournante (41).
PCT/JP2015/084125 2015-02-03 2015-12-04 Dispositif amortisseur dynamique de vibrations pour véhicule automobile Ceased WO2016125382A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015005848.6T DE112015005848T5 (de) 2015-02-03 2015-12-04 Dynamische Vibrationsabsorptionsvorrichtung für ein Fahrzeug

Applications Claiming Priority (2)

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JP2015019084A JP6425572B2 (ja) 2015-02-03 2015-02-03 自動車用の動吸振装置
JP2015-019084 2015-02-03

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WO2016125382A1 true WO2016125382A1 (fr) 2016-08-11

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CN113728179A (zh) * 2019-04-03 2021-11-30 法雷奥离合器公司 摆式阻尼装置

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
CN110691926B (zh) * 2017-03-10 2022-12-27 株式会社法雷奥凯佩科 具有居中的锁止离合器的液力扭矩耦合装置
US10352423B2 (en) * 2017-05-16 2019-07-16 Valeo Embrayages Hydrokinetic torque coupling device with centered friction disc
CN112392932B (zh) * 2019-08-19 2025-09-23 法雷奥凯佩科液力变矩器(南京)有限公司 液力变矩器

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JP2000046116A (ja) * 1998-07-11 2000-02-18 Carl Freudenberg:Fa 回転数適応式振動吸収装置
JP2011504986A (ja) * 2007-11-29 2011-02-17 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト 特に駆動機械と被駆動部との間の出力伝達のための動力伝達装置

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
JP2000046116A (ja) * 1998-07-11 2000-02-18 Carl Freudenberg:Fa 回転数適応式振動吸収装置
JP2011504986A (ja) * 2007-11-29 2011-02-17 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト 特に駆動機械と被駆動部との間の出力伝達のための動力伝達装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113728179A (zh) * 2019-04-03 2021-11-30 法雷奥离合器公司 摆式阻尼装置
CN113728179B (zh) * 2019-04-03 2023-10-20 法雷奥离合器公司 摆式阻尼装置
US12196286B2 (en) 2019-04-03 2025-01-14 Valeo Embrayages Pendulum damping device

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JP6425572B2 (ja) 2018-11-21
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