WO2016103890A1 - Dispositif de transmission de puissance et dispositif de verrouillage pour convertisseur de couple - Google Patents

Dispositif de transmission de puissance et dispositif de verrouillage pour convertisseur de couple Download PDF

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Publication number
WO2016103890A1
WO2016103890A1 PCT/JP2015/080070 JP2015080070W WO2016103890A1 WO 2016103890 A1 WO2016103890 A1 WO 2016103890A1 JP 2015080070 W JP2015080070 W JP 2015080070W WO 2016103890 A1 WO2016103890 A1 WO 2016103890A1
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WO
WIPO (PCT)
Prior art keywords
float member
float
power transmission
transmission device
outer peripheral
Prior art date
Application number
PCT/JP2015/080070
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English (en)
Japanese (ja)
Inventor
祥行 萩原
Original Assignee
株式会社エクセディ
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Filing date
Publication date
Application filed by 株式会社エクセディ filed Critical 株式会社エクセディ
Priority to DE112015005106.6T priority Critical patent/DE112015005106T5/de
Publication of WO2016103890A1 publication Critical patent/WO2016103890A1/fr

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    • 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
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of 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
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • 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 power transmission device, and more particularly to a power transmission device for transmitting power from an engine to a transmission. Further, the present invention is a lock-up device, particularly, disposed between a front cover connected to a member on the engine side and a torque converter main body, for directly transmitting power from the front cover to the turbine of the torque converter main body. The present invention relates to a lockup device.
  • the torque converter is equipped with a lock-up device to reduce fuel consumption.
  • the lockup device is disposed between the front cover and the turbine, and mechanically connects the front cover and the turbine to directly transmit torque therebetween.
  • the lock-up device has a piston and a damper mechanism as disclosed in Patent Document 1, for example.
  • the piston has a friction member, is pressed against the front cover by the action of hydraulic pressure, and torque is transmitted from the front cover.
  • Each of the damper mechanisms includes a plurality of outer peripheral torsion springs and inner peripheral torsion springs, and intermediate members that connect the outer peripheral torsion springs and the inner peripheral torsion springs.
  • the piston and the output side member connected to the turbine are elastically connected by a plurality of torsion springs.
  • Patent Document 2 there is also provided a lockup device in which a dynamic vibration absorber is provided between two dampers so as to suppress the rotational speed fluctuation transmitted to the output side.
  • a dynamic vibration absorber is disposed between two dampers.
  • rotation speed fluctuation amplification or resonance may occur. is there.
  • An object of the present invention is to more effectively suppress fluctuations in rotational speed transmitted to a transmission in a power transmission device such as a lockup device of a torque converter.
  • a power transmission device is a device for transmitting power from an engine to a transmission.
  • the power transmission device includes an input-side rotating member to which power from an engine is input, an output-side rotating member that outputs power to the transmission, a first elastic member, a float member, a rotational speed adaptive dynamic vibration absorber, It is equipped with.
  • the first elastic member connects the input side rotating member and the output side rotating member so as to be relatively rotatable.
  • the float member is rotatable relative to the input side rotation member, the output side rotation member, and the first elastic member, and slides relative to the first elastic member during rotation.
  • the dynamic vibration absorber has a mass body that is connected to the float member and moves relative to the float member when the float member rotates.
  • the power input to the input side rotating member is transmitted to the output side rotating member via the first elastic member.
  • the rotational speed fluctuation transmitted to the transmission side by the operation of the first elastic member is suppressed.
  • the mass body of the dynamic vibration absorber acts in a direction to suppress the rotation fluctuation by centrifugal force, and the rotation speed fluctuation is further suppressed.
  • a dynamic vibration absorber having a mass body is attached to a float member that freely rotates with respect to the first elastic member. That is, the float member is not engaged with the first elastic member. For this reason, the resonance of the damper device which has occurred in the conventional device does not occur, and the rotational speed fluctuation in the low rotational speed range can be further suppressed.
  • the first elastic member and the float member can be rotated relative to each other, the hysteresis torque is reduced as compared with the conventional device, and the damper function is more effectively exhibited.
  • the mass body of the dynamic vibration absorber is a plurality of pendulum members.
  • the first elastic member is a coil spring extending in the rotation direction.
  • the float member can come into contact with the outer peripheral portion of the coil spring and regulates the movement of the coil spring in the radial direction. Thereby, a frictional force is generated between the coil spring and the float member, and the damper device can be effectively operated.
  • the coil spring is an arc spring that extends in an arc shape in the rotational direction in a free state.
  • the second and / or third elastic member disposed in series with the first elastic member on at least one of the input side and the output side of the first elastic member. Is further provided. Thereby, the rotation speed range which can reduce vibration can be shifted to the low rotation side.
  • the power transmission device is disposed between at least one of the float member and the input-side rotating member and between the float member and the output-side rotating member, and friction is generated between the two.
  • a friction generating mechanism for generating resistance is further provided. Thereby, a dynamic vibration absorber can be made to act effectively.
  • the power transmission device further includes a stopper mechanism for restricting the movement of the float member in the rotational direction to a predetermined range. Thereby, the imbalance of an output member can be suppressed.
  • a torque converter lock-up device is disposed between a front cover coupled to a member on an engine side and a torque converter main body, and power from the front cover is transmitted to a turbine of the torque converter main body. It is a device for transmitting directly to.
  • the lockup device includes a clutch portion, an output flange, a plurality of elastic members, a float member, and a rotational speed adaptive dynamic vibration absorber.
  • the clutch part transmits power from the front cover.
  • the output flange is connected to the turbine.
  • the plurality of elastic members transmit power from the clutch portion to the output flange.
  • the float member is rotatable relative to the clutch portion, the output flange, and the plurality of elastic members, slides with the plurality of elastic members at the time of rotation, and restricts radial movement of the plurality of elastic members.
  • the dynamic vibration absorber is connected to the float member and has a mass body that moves relative to the float member when the float member rotates.
  • the rotational speed fluctuation transmitted to the transmission can be more effectively suppressed by providing the float member with the rotational speed adaptive dynamic vibration absorber.
  • FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation.
  • FIG. 1 is a partial sectional view of a torque converter 1 having a lockup device according to a first 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.
  • the torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5) and a lockup device 7 are included.
  • the front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission side is formed on the outer peripheral portion thereof.
  • the impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12.
  • the turbine 4 is disposed opposite to the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15.
  • the turbine hub 17 has a disk portion 17a, a flange portion 17b, and a cylindrical portion 17c.
  • the flange portion 17b is formed to extend further to the outer peripheral side from the end portion of the disc portion 17a on the turbine 4 side.
  • the inner peripheral portion of the turbine shell 15 is fixed to the flange portion 17 b by a plurality of rivets 18.
  • the cylindrical portion 17c is formed to extend from the inner peripheral end of the disc portion 17a to the front cover 2 side.
  • An input shaft of a transmission (not shown) can be spline-engaged with the inner peripheral portion of the cylindrical portion 17c.
  • the stator 5 is a mechanism for rectifying the hydraulic oil that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3.
  • the stator 5 mainly includes a stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof.
  • the stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22.
  • FIG. 2 shows the lock-up device 7 extracted from FIG.
  • the lockup device 7 is disposed in a space between the front cover 2 and the turbine 4.
  • the lock-up device 7 includes a piston 24, a drive plate 25, an outer peripheral side torsion spring (first elastic member) 26, a float member 27, an intermediate member 28, an inner peripheral side torsion spring 29, and an output side rotating member.
  • the piston 24 and the drive plate 25 constitute an input side rotating member.
  • the piston 24 is a disk-shaped plate and is disposed on the transmission side of the front cover 2.
  • a cylindrical portion 24 a extending toward the turbine 4 is formed at the inner peripheral end of the piston 24.
  • the tubular portion 24a is supported on the outer peripheral surface of the tubular portion 17c of the turbine hub 17 so as to be axially movable and relatively rotatable.
  • a flat portion 24 b is formed on the outer peripheral portion of the piston 24.
  • An annular friction material 33 is fixed to the surface of the flat portion 24b on the front cover 2 side. When the friction material 33 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 24. That is, the piston 24 and the friction material 33 constitute a clutch portion.
  • a seal member 35 is attached to the outer peripheral surface of the cylindrical portion 17 c of the turbine hub 17, thereby sealing between the inner peripheral surface of the piston 24 and the turbine hub 17. Further, the axial movement of the piston 24 toward the turbine 4 is restricted by the tip of the cylindrical portion 24 a coming into contact with the side surface of the disc portion 17 a of the turbine hub 17.
  • the drive plate 25 is fixed to the side surface on the turbine 4 side in the outer peripheral portion of the piston 24. Specifically, the drive plate 25 is formed in a disk shape, and the inner peripheral portion 25 a is fixed to the transmission side surface of the piston 24 by a rivet 37. A plurality of engaging portions 25 b are formed on the outer peripheral portion of the drive plate 25. The engaging portion 25b is formed by bending the outer peripheral end portion of the drive plate 25 to the transmission side. The engaging portion 25 b is engaged with both ends of the outer peripheral side torsion spring 26 in the circumferential direction.
  • a plurality of spring support portions 25c projecting toward the transmission side are formed at the radial intermediate portion of the drive plate 25.
  • the plurality of spring support portions 25c are formed at predetermined intervals in the circumferential direction.
  • Each spring support portion 25 c supports the inner peripheral side of the outer peripheral side torsion spring 26.
  • outer peripheral side torsion spring 26 and float member 27 The plurality of outer peripheral torsion springs 26 are arc springs formed in an arc shape that swells to the outer peripheral side in a free state, that is, in a single state before being assembled to the lockup device 7.
  • the float member 27 is an annular plate member as shown in an enlarged view in FIG.
  • the outer peripheral portion of the float member 27 is bent toward the front cover 2 to form a cylindrical portion 27a.
  • the tubular portion 27a is formed with a plurality of spring accommodating portions 27b at predetermined intervals in the circumferential direction.
  • the spring accommodating portion 27b is formed by bending the front end portion of the cylindrical portion 27a on the front cover 2 side toward the inner peripheral side.
  • the outer periphery side torsion spring 26 is accommodated in the spring accommodating portion 27b.
  • the float member 27 is freely rotatable with respect to other members, that is, the drive plate 25, the intermediate member 28, and the hub flange 30. Further, since the spring accommodating portion 27 b and the outer peripheral side torsion spring 26 are not engaged with each other, the float member 27 does not rotate in synchronization with the outer peripheral side torsion spring 26.
  • the intermediate member 28 is a member that connects both the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 so as to act in series.
  • the intermediate member 28 also has a function of holding the inner peripheral side torsion spring 29.
  • the intermediate member 28 includes a first plate 41 and a second plate 42, and is rotatable relative to the drive plate 25 and the hub flange 30.
  • the first and second plates 41 and 42 are annular and disk-shaped members disposed between the piston 24 and the turbine shell 15.
  • the first plate 41 and the second plate 42 are arranged with a space in the axial direction.
  • the first plate 41 is disposed on the front cover 2 side, and the second plate 42 is disposed on the turbine 4 side.
  • the outer peripheral portion of the first plate 41 and the radial intermediate portion of the second plate 42 are fixed to each other by a plurality of stop pins 43. Therefore, the 1st plate 41 and the 2nd plate 42 are connected so that relative rotation is impossible and it cannot move in the direction of an axis. Note that both end surfaces of the body portion of the stop pin 43 abut against the mutually opposing side surfaces of each play 41, 42, thereby setting a predetermined distance between the first plate 41 and the second plate 42. .
  • the outer peripheral portion of the second plate 42 has a plurality of protruding portions 42 a that protrude further to the outer peripheral side than the outer peripheral portion of the first plate 41.
  • the plurality of protrusions 42a are formed at predetermined intervals in the circumferential direction.
  • the front end (outer peripheral end) of the protruding portion 42 a is bent toward the front cover 2, and a plurality of locking portions 42 b that contact the end surface of the outer peripheral torsion spring 26 are formed.
  • One outer torsion spring 26 is arranged between the two locking portions 42b.
  • a stopper claw 25d formed at the tip of the spring support portion 25c of the drive plate 25 is disposed between two adjacent protruding portions 42a. Therefore, the drive plate 25 and the intermediate member 28 (second plate 42) can be rotated relative to each other within a range in which the stopper claw 25d can move in the rotational direction between two adjacent protruding portions 42a. In other words, relative rotation between the drive plate 25 and the intermediate member 28 is prohibited by the stopper claw 25d coming into contact with the protruding portion 42a.
  • first plate 41 and the second plate 42 are respectively formed with windows 41c and 42c penetrating in the axial direction.
  • the window portions 41c and 42c are formed to extend in the circumferential direction, and a cut-and-raised portion that is cut and raised in the axial direction is formed on the inner peripheral portion and the outer peripheral portion.
  • An inner peripheral side torsion spring 29 is arranged in the window portions 41c and 42c of both the plates 41 and 42.
  • the inner circumferential side torsion spring 29 is supported at both ends in the circumferential direction and both sides in the radial direction by the windows 41c and 42c. Further, the inner periphery side torsion spring 29 is restricted from projecting in the radial direction and the axial direction by the cut and raised portions of the window portions 41c and 42c.
  • the hub flange 30 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange portion 17 b of the turbine hub 17 by a rivet 18 together with the turbine shell 15.
  • the hub flange 30 is disposed between the first plate 41 and the second plate 42 so as to be rotatable relative to the plates 41 and 42 between the first plate 41 and the second plate 42.
  • a window hole 30 a is formed in the outer peripheral portion of the hub flange 30 corresponding to the window portions 41 c and 42 c of the first and second plates 41 and 42.
  • the window hole 30a is a hole penetrating in the axial direction, and an inner peripheral torsion spring 29 is disposed in the window hole 30a.
  • a plurality of notches 30 b are formed on the outer peripheral portion of the hub flange 30.
  • a stop pin 43 passes through the notch 30b in the axial direction. Therefore, the intermediate member 28 and the hub flange 30 can rotate relative to each other within a range in which the stop pin 43 can move in the rotation direction in the notch 30b. In other words, relative rotation between the intermediate member 28 and the hub flange 30 is prohibited by the stop pin 43 coming into contact with the end face of the notch 30b.
  • a regulating portion 30 c that extends linearly from the portion fixed to the turbine shell 15 to the outer circumferential side is formed on the inner circumferential portion of the hub flange 30.
  • a support member 45 that supports the float member 27 is provided between the inner peripheral portion of the hub flange 30 and the turbine shell 15. The support member 45 is fixed to the turbine shell 15 by the rivet 18 together with the hub flange 30.
  • the support member 45 is an annular and disk-shaped member, and has a radial support portion 45a and an axial support portion 45b on the outer peripheral portion.
  • the radial support portion 45a is formed in a cylindrical shape extending in the axial direction.
  • the axial support portion 45b is formed to extend from the end portion of the radial support portion 45a to the outer peripheral side.
  • the float member 27 is positioned in the radial direction by the radial support portion 45a of the support member 45, and is sandwiched between the restriction portion 30c of the hub flange 30 and the axial support portion 45b of the support member 45. Is positioned in the axial direction.
  • the dynamic vibration absorber 31 attenuates vibrations by moving relative to the float member 27 when the float member 27 rotates. As shown in FIGS. 2, 3, and 5, the dynamic vibration absorber 31 includes a plurality of pendulums 50, a holding plate 51, and a plurality of pins 52.
  • the pendulum 50 has a fan shape formed so that the outer peripheral surface swells to the outer peripheral side.
  • the pendulum 50 is formed with two grooves 50a arranged in the circumferential direction.
  • the two grooves 50a are formed in line symmetry. Further, the two grooves 50a are formed in a substantially arc shape whose central portion is recessed toward the inner peripheral side.
  • the holding plate 51 is an annular and disk-shaped member, and a radially intermediate portion and an inner peripheral portion are fixed to the float member 27 by a plurality of rivets 55 and 56, respectively.
  • the outer rivet 55 is disposed between the adjacent pendulums 50 in the circumferential direction.
  • a collar 58 made of an elastic member is attached to the outer peripheral surface of the rivet 55 on the outer peripheral side.
  • the float member 27 and the holding plate 51 are formed with a plurality of grooves 27c and 51c arranged in the circumferential direction.
  • FIG. 5 only the groove 27c of the float member 27 is shown, and the groove 51c of the holding plate 51 does not appear. However, since these grooves 27c and 51c have exactly the same shape, the groove 27c of the float member 27 will be described here.
  • the groove 27c is formed at a position corresponding to the position of the groove 50a of the pendulum 50 when the pendulum 50 is located at the neutral position.
  • the two grooves 27c formed corresponding to each pendulum 50 are formed in line symmetry.
  • channel 27c is formed in the substantially circular arc shape where a center part swells to the outer peripheral side contrary to the groove
  • the pin 52 has a large diameter part 52a and two small diameter parts 52b provided at both ends of the large diameter part 52a.
  • the large diameter portion 52a of the pin 52 is inserted into the groove 50a of the pendulum 50 so as to be movable along the groove 50a.
  • the small diameter portion 52b is inserted into the groove 27c of the float member 27 and the groove 51c of the holding plate 51 so as to be movable along the grooves 27c and 51c.
  • the axial distance between the float member 27 and the holding plate 51 is set by the axial length of the large diameter portion 52a of the pin 52.
  • the axial length of the large diameter portion 52a is set slightly larger than the thickness (axial length) of the pendulum 50.
  • the pendulum 50 can swing in the rotational direction with respect to the float member 27 and the holding plate 51.
  • the lockup device 7 transmits torque and absorbs and attenuates fluctuations in rotational speed input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 are compressed in series between the drive plate 25 and the hub flange 30. The rotation speed fluctuation is attenuated by the operation of these torsion springs 26 and 29 and the frictional resistance (hysteresis torque) of each part.
  • the pendulum 50 swings with respect to the float member 27 when the rotational speed fluctuates. At this time, since centrifugal force is acting on the pendulum 50, a force for returning to the center position in the circumferential direction acts on the pendulum 50. The action of the pendulum 50 can further suppress vibration.
  • FIG. 6 shows the effects of the above dynamic vibration absorber 31 in comparison with the conventional apparatus.
  • the horizontal axis represents the engine speed
  • the vertical axis represents the rotational speed fluctuation on the output side.
  • the characteristic C1 has shown the characteristic in the apparatus (for example, patent document 2) which attached the dynamic vibration absorber 31 to the intermediate member of the lockup apparatus
  • the characteristic C2 has shown the characteristic of this embodiment. Note that both are characteristics when an irregular order appears on the input side.
  • FIG. 7 shows a schematic diagram of the second embodiment of the present invention.
  • a float member 61 that supports the inner peripheral torsion spring 29 is provided, and the dynamic vibration absorber 31 is coupled to the float member 61.
  • the other configurations of the dynamic vibration absorber 31 and the second embodiment are basically the same as those of the first embodiment.
  • FIG. 8 shows a schematic diagram of the third embodiment of the present invention.
  • the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 are provided, but in the third embodiment, only one of the torsion springs 64 is provided.
  • one type of torsion spring 64 is provided between the piston 24 and the turbine 4 (specifically, the turbine hub 17).
  • the torsion spring 64 is provided with a float member 65 having the same configuration as that of the first embodiment. Although the float member 65 is not engaged with the torsion spring 64, the float member 65 can be rotated with respect to the torsion spring 64 within a predetermined range by the frictional resistance between them as in the first embodiment.
  • the dynamic vibration absorber 31 is mounted on the float member 65, and the configuration thereof is the same as that of the first embodiment.
  • FIG. 9 shows a schematic diagram of the fourth embodiment.
  • an intermediate torsion spring 67 is provided in addition to the outer periphery side torsion spring 26 and the inner periphery side torsion spring 29.
  • the float member 68 is provided so as to accommodate the intermediate torsion spring 67.
  • the float member 68 is not engaged with the intermediate torsion spring 67 but can be rotated with respect to the intermediate torsion spring 67 within a predetermined range by the frictional resistance between them.
  • the dynamic vibration absorber 31 is mounted on the float member 68, and the configuration thereof is the same as in the other embodiments.
  • FIG. 10 shows a schematic diagram of the fifth embodiment.
  • a hysteresis torque generating mechanism 70 is further provided between the float member 65 and the output-side rotating member.
  • hysteresis torque is generated by the hysteresis torque generating mechanism 70 when the float member 65 is rotated around the torsion spring 64.
  • the hysteresis torque generating mechanism may be provided between the float member 65 and the input side member instead of between the float member 65 and the output side rotation member.
  • FIG. 11 shows a schematic diagram of the sixth embodiment.
  • a stopper mechanism 72 is further provided between the float member 65 and the rotating member on the output side. The stopper mechanism 72 restricts the movement of the float member 65 in the rotation direction within a predetermined range.
  • stopper mechanism may be provided between the float member 65 and the input side rotating member.
  • the present invention is applied to the lock-up device of the torque converter, but can be similarly applied to other power transmission devices.
  • the configuration of the dynamic vibration absorber is not limited to the above-described embodiments, and various modifications are possible.
  • another mass body may be provided instead of the plurality of pendulums.
  • the rotational speed fluctuation transmitted to the transmission can be more effectively suppressed by providing the float member with a rotational speed adaptive dynamic vibration absorber.

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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 supprime plus efficacement la fluctuation de la vitesse de rotation qui est transmise par une transmission dans un dispositif de transmission de puissance pour un dispositif de verrouillage et similaire, d'un convertisseur de couple. Ce dispositif de transmission de puissance est pourvu : d'une plaque d'entraînement (25) à laquelle la puissance est transmise, d'une bride de moyeu (30) qui délivre de la puissance ; d'un ressort de torsion périphérique externe (26) ; d'un élément de flotteur (27) ; et d'un amortisseur de vibrations dynamique (31). Le ressort de torsion périphérique externe (26) raccorde la plaque d'entraînement (25) et la bride de moyeu (30) de manière à être rotatifs l'un par rapport à l'autre. L'élément de flotteur (27) est capable de se mettre en rotation par rapport à la plaque d'entraînement (25), à la bride de moyeu (30), et au ressort de torsion périphérique externe (26) et se déplace d'une manière coulissante par rapport au ressort de torsion périphérique externe (26) pendant la rotation. L'absorbeur de vibrations dynamique (31) comprend une pluralité de balanciers (50) qui sont raccordés à l'élément de flotteur (27) et qui se déplacent par rapport à l'élément de flotteur (27) pendant la rotation de l'élément de flotteur (27).
PCT/JP2015/080070 2014-12-26 2015-10-26 Dispositif de transmission de puissance et dispositif de verrouillage pour convertisseur de couple WO2016103890A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015005106.6T DE112015005106T5 (de) 2014-12-26 2015-10-26 Kraftübertragungsvorrichtung und Überbrückungsvorrichtung für einen Drehmomentwandler

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JP2014264116A JP6541969B2 (ja) 2014-12-26 2014-12-26 動力伝達装置及びトルクコンバータのロックアップ装置
JP2014-264116 2014-12-26

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109154375A (zh) * 2016-07-20 2019-01-04 株式会社艾科赛迪 转矩变动抑制装置、液力变矩器以及动力传递装置
US11015674B2 (en) 2017-02-17 2021-05-25 Exedy Corporation Torque fluctuation inhibiting device, torque converter and power transmission device
JP7455970B2 (ja) 2019-11-05 2024-03-26 ヴァレオ、カペック、トルク、コンバーターズ、（ナンジン）、カンパニー、リミテッド 油圧カップリングデバイス用ダンピングシステム、油圧カップリングデバイスおよび自動車

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018031425A (ja) * 2016-08-24 2018-03-01 株式会社エクセディ 振動低減装置
JP2018031423A (ja) * 2016-08-24 2018-03-01 株式会社エクセディ 振動低減装置
JP7021890B2 (ja) * 2017-09-27 2022-02-17 株式会社Subaru 変速機
US11578779B2 (en) * 2020-04-07 2023-02-14 Valeo Kapec Co., Ltd. Intermediate plate apparatus and related damper assemblies for use with vehicles

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008224007A (ja) * 2007-03-15 2008-09-25 Aisin Aw Co Ltd スプリングダンパ
US20140044523A1 (en) * 2011-04-21 2014-02-13 Schaeffler Technologies AG & Co. KG Torque converter
JP2014145441A (ja) * 2013-01-30 2014-08-14 Toyota Motor Corp 遠心振り子式ダイナミックダンパ
WO2014196340A1 (fr) * 2013-06-04 2014-12-11 株式会社エクセディ Dispositif de verrouillage de convertisseur de couple

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112011100860A5 (de) * 2010-03-11 2013-02-07 Schaeffler Technologies AG & Co. KG Dämpfereinheit und Kraftübertragungsvorrichtung mit einer derartigen Dämpfereinheit
JP5609820B2 (ja) * 2011-08-23 2014-10-22 アイシン・エィ・ダブリュ株式会社 ダンパ装置
DE102012212125A1 (de) * 2012-07-11 2014-01-16 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008224007A (ja) * 2007-03-15 2008-09-25 Aisin Aw Co Ltd スプリングダンパ
US20140044523A1 (en) * 2011-04-21 2014-02-13 Schaeffler Technologies AG & Co. KG Torque converter
JP2014145441A (ja) * 2013-01-30 2014-08-14 Toyota Motor Corp 遠心振り子式ダイナミックダンパ
WO2014196340A1 (fr) * 2013-06-04 2014-12-11 株式会社エクセディ Dispositif de verrouillage de convertisseur de couple

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109154375A (zh) * 2016-07-20 2019-01-04 株式会社艾科赛迪 转矩变动抑制装置、液力变矩器以及动力传递装置
US11015674B2 (en) 2017-02-17 2021-05-25 Exedy Corporation Torque fluctuation inhibiting device, torque converter and power transmission device
JP7455970B2 (ja) 2019-11-05 2024-03-26 ヴァレオ、カペック、トルク、コンバーターズ、（ナンジン）、カンパニー、リミテッド 油圧カップリングデバイス用ダンピングシステム、油圧カップリングデバイスおよび自動車

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JP6541969B2 (ja) 2019-07-10
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