JP2018031425A - Vibration reduction device - Google Patents

Vibration reduction device Download PDF

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Publication number
JP2018031425A
JP2018031425A JP2016163973A JP2016163973A JP2018031425A JP 2018031425 A JP2018031425 A JP 2018031425A JP 2016163973 A JP2016163973 A JP 2016163973A JP 2016163973 A JP2016163973 A JP 2016163973A JP 2018031425 A JP2018031425 A JP 2018031425A
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JP
Japan
Prior art keywords
damper
input
vibration
piston
housing
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.)
Pending
Application number
JP2016163973A
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Japanese (ja)
Inventor
雄亮 冨田
Yusuke Tomita
雄亮 冨田
裕樹 河原
Hiroki Kawahara
裕樹 河原
悠祐 岡本
Yusuke Okamoto
悠祐 岡本
Original Assignee
株式会社エクセディ
Exedy Corp
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Application filed by 株式会社エクセディ, Exedy Corp filed Critical 株式会社エクセディ
Priority to JP2016163973A priority Critical patent/JP2018031425A/en
Publication of JP2018031425A publication Critical patent/JP2018031425A/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00Fluid-actuated clutches
    • F16D25/06Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/131Suppression 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
    • F16F15/133Suppression 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
    • F16F15/134Wound springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression 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

Abstract

Disclosed is a vibration reducing device that can effectively absorb torsional vibration in a dynamic vibration absorber and can improve the degree of freedom of the configuration of the dynamic vibration absorber. A vibration reducing device includes a housing, an output hub, a main damper device, a dynamic damper device, and a clutch portion. Torsional vibration is input to the housing 2. The output hub 3 is disposed so as to be rotatable relative to the housing 2. The main damper device 4 is disposed between the housing 2 and the output hub 3, and attenuates torsional vibration input to the housing 2. The dynamic damper device 5 absorbs torsional vibration output from the main damper device 4. The clutch portion 8 is disposed between the housing 2 and the main damper device 4. The clutch unit 8 is configured to be able to connect the housing 2 and the main damper device 4 and to be able to release the connection between the housing 2 and the main damper device 4. [Selection] Figure 1

Description

  The present invention relates to a vibration reducing device.

  The conventional vibration reducing device is disposed between the engine and the transmission and reduces torsional vibration from the engine. A conventional vibration reduction device includes a housing (flywheel element 3), an output member (flywheel element 4), a damper portion (energy storage device 10) disposed radially outward, and radially inward of the damper portion. And a dynamic vibration absorber (vibration attenuator 10) arranged.

Japanese Patent Laid-Open No. 2003-4101

  In the conventional vibration reducing device, when the torsional vibration from the engine is input to the housing, the torsional vibration is attenuated in the damper portion. The dynamic vibration absorber additionally attenuates torsional vibration.

  In this case, if the engine speed changes during operation of the vibration reducing device (damper unit and dynamic vibration absorber), the vibration reducing device system may resonate. Then, an excessive torsional vibration is generated in the vibration reducing device, and this torsional vibration may be transmitted from the vibration reducing device to a member on the transmission side.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a vibration reduction device that can operate properly and can appropriately attenuate torsional vibration.

  (1) A vibration reducing device according to one aspect of the present invention is for reducing torsional vibration from an engine. The vibration reducing device includes an input rotating unit, an output rotating unit, a damper unit, a dynamic vibration absorber, and a clutch unit. Torsional vibration is input to the input rotating unit. The output rotation unit is disposed so as to be rotatable relative to the input rotation unit. The damper unit is disposed between the input rotating unit and the output rotating unit, and attenuates torsional vibration input to the input rotating unit. The dynamic vibration absorber absorbs torsional vibration output from the damper portion. The clutch part is disposed between the input rotating part and the damper part. The clutch unit is configured to be able to connect the input rotating unit and the damper unit and to be able to release the connection of the input rotating unit and the damper unit.

  In this vibration reducing device, when the system of the vibration reducing device approaches the resonance point in a state where the clutch portion connects the input rotating portion and the damper portion, the clutch portion connects the input rotating portion and the damper portion. To release. Thereby, it is possible to prevent transmission of excessive torsional vibration from the vibration reducing device to the member on the transmission side. That is, the vibration reducing device can be appropriately operated, and torsional vibration can be appropriately damped in the vibration reducing device.

  (2) In the vibration reducing device according to another aspect of the present invention, the input rotating portion constitutes an internal space in which lubricating oil can be accommodated. The damper part, the dynamic vibration absorber, and the clutch part are disposed in the internal space.

  In this case, since the damper portion, the dynamic vibration absorber, and the clutch portion are disposed in the internal space of the input rotation portion in a state where the lubricating oil is accommodated in the internal space of the input rotation portion, the damper portion, the dynamic vibration absorption device, And the clutch part can be operated stably.

  (3) In the vibration reducing device according to another aspect of the present invention, the clutch unit includes a piston and a friction member. The piston engages with the damper portion so as to be movable in a direction along the rotation axis of the input rotation portion. The friction member is provided on the piston so as to be in contact with the input rotating portion.

  By configuring the clutch portion in this manner, it is possible to suitably prevent transmission of excessive torsional vibration from the vibration reducing device to the member on the transmission side.

  (4) In the vibration reducing device according to another aspect of the present invention, the piston can rotate integrally with the input rotation unit in a state where the friction member is in contact with the input rotation unit. Further, the piston can be rotated relative to the input rotation unit in a state where the friction member is in contact with the input rotation unit.

  In this case, torque can be transmitted from the housing to the main damper device by integrally rotating the piston and the input rotating portion via the friction member. Thereby, torsional vibration can be suitably damped.

  (5) In the vibration reducing device according to another aspect of the present invention, the input rotating portion constitutes an internal space in which lubricating oil can be accommodated. The friction member comes into contact with or separates from the input rotating portion due to a hydraulic pressure difference between the hydraulic pressure between the input rotating portion and the piston and the hydraulic pressure between the damper portion and the piston.

  By configuring the clutch portion in this manner, it is possible to suitably prevent transmission of excessive torsional vibration from the vibration reducing device to the member on the transmission side.

  (6) In the vibration reducing device according to another aspect of the present invention, the input rotating portion constitutes an internal space in which lubricating oil can be accommodated. The clutch part further has a biasing member that biases the piston. The piston moves toward the input rotating portion by the biasing force of the biasing member, and the friction member contacts the input rotating portion. On the other hand, the piston separates from the input rotating portion and the friction member separates from the input rotating portion due to the hydraulic pressure difference between the hydraulic pressure between the input rotating portion and the piston and the hydraulic pressure between the damper portion and the piston.

  By configuring the clutch portion in this manner, it is possible to suitably prevent transmission of excessive torsional vibration from the vibration reducing device to the member on the transmission side.

  (7) In the vibration reducing device according to another aspect of the present invention, the dynamic vibration absorber is arranged side by side with the damper portion in a direction along the rotation axis of the input rotation portion.

  In this case, since the dynamic vibration absorber is not restricted in arrangement by the damper portion, the dynamic vibration absorber can be effectively operated. For example, since the dynamic vibration absorber can be arranged on the radially outer side, the dynamic vibration absorber can be effectively operated.

  (8) In the vibration reducing device according to another aspect of the present invention, the damper portion includes a first rotating member, a second rotating member, and a first elastic member. The first rotating member is coupled to the input rotating unit. The second rotating member is disposed to be rotatable relative to the first rotating member. The second rotating member is connected to the output rotating unit. The first elastic member elastically connects the first rotating member and the second rotating member.

  Even if the damper portion is configured in this manner, the vibration reduction device can be operated appropriately, and torsional vibration can be stably damped in the vibration reduction device.

  (9) In the vibration reducing device according to another aspect of the present invention, the dynamic vibration absorber includes an input member and an inertia mass body. Torsional vibration output from the damper portion is input to the input member. The inertia mass body is configured to be movable relative to the input member.

  Even if the dynamic vibration absorber is configured in this manner, the vibration reducing device can be operated appropriately, and torsional vibration can be stably damped in the vibration reducing device.

  (10) In the vibration reducing device according to another aspect of the present invention, the dynamic vibration absorber further includes a second elastic member that elastically connects the input member and the inertia mass body.

  In this case, the inertia mass body is configured to be movable relative to the input member via the second elastic member. Even if comprised in this way, a torsional vibration can be effectively absorbed in a dynamic vibration damper.

  (11) In the vibration reducing device according to another aspect of the present invention, each of the plurality of inertial mass bodies is capable of swinging with respect to a swing center radially outward from the rotational axis of the input rotating unit. It is supported.

  In this case, torsional vibration can be effectively absorbed in the dynamic vibration absorber by swinging the inertial mass body with respect to the input member.

  (12) In the vibration reducing device according to another aspect of the present invention, the dynamic vibration absorber further includes a centrifuge. The centrifuge engages the inertial mass body by centrifugal force. The centrifuge guides the inertial mass body so that the relative displacement between the input member and the inertial mass body is small. Even if comprised in this way, a torsional vibration can be effectively absorbed in a dynamic vibration damper.

  In the present invention, the vibration reducing device can be appropriately operated, and the torsional vibration can be appropriately damped in the vibration reducing device.

The cross-sectional block diagram of the vibration reduction apparatus by one Embodiment of this invention. The figure which extracted the main damper apparatus from the vibration reduction apparatus of FIG. The figure which extracted the dynamic damper apparatus from the vibration reduction apparatus of FIG. The partial side view of the damper plate part of a dynamic damper apparatus. The partial side view of the inertia part of a dynamic damper apparatus. The partial side view of the cover member of a dynamic damper apparatus. The fragmentary sectional view of a dynamic damper device. The cross-sectional block diagram of the vibration reduction apparatus by other embodiment of this invention. The partial side view of the dynamic damper apparatus by other embodiment of this invention The partial side view of the dynamic damper apparatus by other embodiment of this invention

  FIG. 1 is a partial cross-sectional view of a vibration reducing device according to 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. Note that OO shown in FIG. 1 is a rotation axis of the vibration reducing device 1. Hereinafter, a direction away from the rotation axis O is referred to as a radial direction, a direction along the rotation axis O is referred to as an axial direction, and a direction around the rotation axis O is sometimes referred to as a circumferential direction.

[Overall configuration of vibration reduction device]
The vibration reducing device 1 is a device for transmitting torque from a member on the engine side to a member on the transmission side. The vibration reducing device 1 is configured to be able to reduce torsional vibration from the engine. Torsional vibration is torsional vibration generated in the vibration reducing apparatus 1 due to torque fluctuation (rotational speed fluctuation) input from the engine to the vibration reducing apparatus 1.

  As shown in FIG. 1, the vibration reducing device 1 includes a housing 2 (an example of an input rotating part), an output hub 3 (an example of an output rotating part), a main damper device 4 (an example of a damper part), a clutch part. 8 and a dynamic damper device 5 (an example of a dynamic vibration absorber).

<Housing>
A member on the engine side is attached to the housing 2 and engine torque is input. As shown in FIG. 1, the housing 2 is configured to be rotatable around the rotation axis O.

  The housing 2 has a cover portion 6 and a hub for cover. The housing 2 constitutes an internal space S. The internal space S is configured to be able to accommodate lubricating oil. Here, an internal space S is formed by the cover 6. The internal space S may be interpreted as being formed by the cover portion 6 and the cover hub. Further, the internal space S may be interpreted as being formed by the housing 2 and the output hub 3.

(Cover part)
The cover unit 6 includes a first cover 9 and a second cover 10. The first cover 9 is a cover member on the engine side. The first cover 9 includes a first main body portion 9a, a boss portion 9b, and a first outer peripheral cylindrical portion 9c.

  The 1st main-body part 9a is formed in the disk shape substantially. The boss portion 9b is provided on the inner peripheral portion of the first main body portion 9a. The boss part 9b protrudes from the inner peripheral part of the first main body part 9a to the engine side. The boss 9b is inserted into a crankshaft (not shown). The first outer cylindrical portion 9c is provided on the outer peripheral portion of the first main body portion 9a. The first outer cylindrical portion 9c protrudes from the outer peripheral portion of the first main body portion 9a to the transmission side.

  The second cover 10 is a transmission-side cover member. The 2nd cover 10 has the 2nd main-body part 10a and the 2nd outer periphery cylindrical part 10b. The 2nd main-body part 10a is formed substantially cyclic | annular. The inner peripheral portion of the second main body portion 10a is fixed to the cover hub by welding. The second outer cylindrical part 10b is provided on the outer peripheral part of the second main body part 10a. The second outer cylindrical portion 10b protrudes from the outer peripheral portion of the second main body portion 10a to the engine side. The second outer peripheral cylindrical portion 10b is fixed to the first outer peripheral cylindrical portion 9c of the first cover 9 by welding.

(Hub for cover)
The cover hub 7 is supported so as to be rotatable relative to the output hub 3. For example, the cover hub 7 is supported by the output hub 3 via bearings or thrust washers 11. The cover hub 7 may be interpreted as a member constituting the internal space S of the housing 2.

  Specifically, the cover hub 7 includes a first hub body 7a and a first hub flange 7b. The first hub body 7a is formed in a substantially cylindrical shape. The first hub flange 7b is formed integrally with the first hub body 7a. The first hub flange 7b protrudes radially outward from the outer peripheral portion of the first hub body 7a. The inner peripheral portion of the second main body portion 10a of the second cover 10 is fixed to the first hub flange 7b by welding.

<Output hub>
The output hub 3 is disposed so as to be rotatable relative to the housing 2. As shown in FIG. 1, the output hub 3 is disposed in the internal space S of the housing 2. Note that the output hub 3 may be interpreted as a member constituting the internal space S of the housing 2.

  A member on the transmission side is attached to the output hub 3. The output hub 3 is attached to a shaft (not shown) on the transmission side so as to be integrally rotatable.

  Specifically, the output hub 3 has a second hub body 3a and a second hub flange 3b. The second hub body 3a is formed in a substantially cylindrical shape. The inner peripheral portion of the second hub body 3a is engaged with a transmission-side shaft so as to be integrally rotatable. Here, the inner peripheral portion of the second hub body 3a is spline-engaged with the outer peripheral portion of the transmission-side shaft.

  The second hub flange 3b is formed integrally with the second hub body 3a. The second hub flange 3b protrudes radially outward from the outer peripheral portion of the second hub body 3a. The main damper device 4 and the dynamic damper device 5 are fixed to the second hub flange 3b by fixing means such as rivets 12. Between the second hub flange 3b and the first hub flange 7b of the cover hub 7, the above-described bearing or thrust washer 11 is disposed.

<Main damper device>
The main damper device 4 attenuates torsional vibration input to the housing 2. As shown in FIG. 1, the main damper device 4 is disposed in the internal space S of the housing 2.

  The main damper device 4 is disposed on the engine side with respect to the dynamic damper device 5 in the axial direction. In other words, the main damper device 4 is disposed between the engine and the dynamic vibration absorber in the axial direction. Specifically, the main damper device 4 is disposed between the housing 2 on the engine side and the dynamic vibration absorber in the axial direction. More specifically, the main damper device 4 is disposed between the first cover 9 of the housing 2 and the dynamic vibration absorber in the axial direction.

  The main damper device 4 connects the housing 2 and the output hub 3. The main damper device 4 is connected to the housing 2 via the clutch portion 8. Here, the main damper device 4 is connected to the housing 2 via the clutch portion 8 so as to be integrally rotatable. The main damper device 4 is connected to the output hub 3. Here, for example, the main damper device 4 is fixed to the output hub 3 by fixing means such as a plurality of rivets 12.

  Specifically, as shown in FIG. 2, the main damper device 4 includes a drive plate 13 (an example of a first rotating member), a driven plate 14 (an example of a second rotating member), and a plurality of coil springs 15 ( An example of a first elastic member).

(Drive plate)
The drive plate 13 is disposed so as to be rotatable with respect to the driven plate 14. The drive plate 13 is supported so as to be rotatable with respect to the driven plate 14.

  As shown in FIG. 2, the drive plate 13 is connected to the housing 2. Here, the drive plate 13 is coupled to the cover portion 6 of the housing 2 through the clutch portion 8 so as to be integrally rotatable.

  Specifically, the drive plate 13 is configured to be able to rotate integrally with the clutch portion 8 connected to the cover portion 6 of the housing 2. Here, the drive plate 13 is engaged with a piston 18 (described later) of the clutch portion 8 so as to be able to rotate integrally with the clutch portion 8.

  Specifically, the drive plate 13 includes a drive plate main body 13a, a plurality of engaging projections 13b, a plurality (for example, four) first outer peripheral side window portions 13c, and a plurality (for example, four) first. And an inner peripheral side window portion 13d.

  The drive plate body 13a is formed in a substantially annular and disc shape.

  The plurality of engaging convex portions 13b are formed on the outer peripheral portion of the drive plate main body 13a. Specifically, each of the plurality of engaging convex portions 13b protrudes radially outward from the outer peripheral portion of the drive plate main body 13a. The plurality of engaging protrusions 13b are arranged at a predetermined interval in the circumferential direction. The plurality of engaging projections 13b engage with the plurality of engaging recesses 18d of the piston 18 of the clutch unit 8 separately. In detail, each engagement convex part 13b is arrange | positioned inside each engagement recessed part 18d. As a result, the drive plate 13 can rotate integrally with the clutch portion 8.

  The plurality of first outer peripheral side window portions 13 c are provided on the outer peripheral side of the drive plate 13. Specifically, the first outer peripheral side windows 13c are provided on the drive plate 13 with a predetermined interval in the circumferential direction. Each of the first outer peripheral side window portions 13c is provided with a plurality of outer peripheral side coil springs 15a (described later).

  The plurality of first inner peripheral side window portions 13 d are provided on the inner peripheral side of the drive plate 13. Specifically, each first inner peripheral window portion 13d is provided on the drive plate 13 at a predetermined interval in the circumferential direction on the radially inner peripheral side from the plurality of first outer peripheral window portions 13c. Yes. Each of the first inner peripheral side window portions 13d is provided with a plurality of inner peripheral coil springs 15b (described later).

(Driven plate)
The driven plate 14 is disposed so as to be rotatable with respect to the drive plate 13. As shown in FIG. 2, the driven plate 14 is connected to the output hub 3.

  The driven plate 14 has a pair of driven plate main bodies 14a, a plurality of second outer peripheral side window portions 14b, and a plurality of second inner peripheral side window portions 14c.

  Each of the pair of driven plate bodies 14a is formed in a substantially annular and disk shape.

  The pair of driven plate main bodies 14a are arranged to face each other in the axial direction. A drive plate 13 (drive plate body 13a) is disposed between the pair of driven plate bodies 14a in the axial direction. One driven plate main body 14a is disposed on the engine side with the drive plate 13 as a reference. The other driven plate 14 is disposed on the transmission side with respect to the drive plate 13.

  Hereinafter, one driven plate body 14a may be referred to as a first driven plate body 114a. The other driven plate body 14a may be referred to as a second driven plate body 124a.

  Specifically, the inner peripheral portions of the first and second driven plate bodies 114a and 124a (14a), for example, the first fixing portions 14d are arranged adjacent to each other in the axial direction, and are fixed by the fixing means, for example, the plurality of rivets 12. The output hub 3 is fixed to the second hub flange 3b. The first and second driven plate bodies 114a and 124a (excluding the first fixing portion 14d) are arranged at a predetermined interval from each other in the axial direction. The drive plate 13 (drive plate body 13a) is disposed at this interval. That is, the drive plate 13 is disposed between the first and second driven plate bodies 114a and 124a (14a).

  The first driven plate body 114a is provided with a support portion 14e for supporting the inner peripheral portion of the drive plate 13 (drive plate body 13a). The support portion 14e is provided on the outer peripheral side of the first fixed portion 14d of the first driven plate body 114a. The support portion 14e is formed in an annular shape. The inner peripheral portion of the drive plate 13 (drive plate body 13a) is disposed on the outer peripheral surface of the support portion 14e. Thus, the 1st driven plate main body 114a positions the drive plate 13 (drive plate main body 13a) in radial direction in the support part 14e.

  The plurality of second outer peripheral side window portions 14b are provided on the outer peripheral side of each of the pair of driven plate main bodies 14a (the first driven plate main body 114a and the second driven plate main body 124a). Specifically, each second outer peripheral side window portion 14b is provided in each of the pair of driven plate main bodies 14a with a predetermined interval in the circumferential direction. Each second outer peripheral window portion 14b and each first outer peripheral window portion 13c of the drive plate main body 13a are disposed to face each other in the axial direction. A plurality of outer coil springs 15a (described later) are arranged in the second outer window portions 14b and the first outer window portions 13c, respectively.

  The plurality of second inner peripheral window portions 14c are provided on the inner peripheral side of each of the pair of driven plate main bodies 14a (the first driven plate main body 114a and the second driven plate main body 124a). Specifically, each second inner peripheral window portion 14c is provided in each of the pair of driven plate main bodies 14a with a predetermined interval in the circumferential direction. The second inner peripheral window portions 14c and the first inner peripheral window portions 13d of the drive plate main body 13a are arranged to face each other in the axial direction. A plurality of inner periphery side coil springs 15b (to be described later) are respectively disposed in the second inner periphery side window portions 14c and the first inner periphery side window portions 13d.

(coil spring)
The plurality of coil springs 15 elastically connect the drive plate 13 and the driven plate 14. Specifically, as shown in FIG. 2, the plurality of coil springs 15 include a plurality (for example, four) of outer peripheral side coil springs 15a and a plurality of (for example, four) inner peripheral side coil springs 15b. doing. Here, the plurality of outer peripheral coil springs 15 a and the plurality of inner peripheral coil springs 15 b operate in parallel between the drive plate 13 and the driven plate 14.

  Each of the plurality of outer peripheral side coil springs 15 a elastically connects the drive plate 13 and the driven plate 14. Each outer coil spring 15 a is disposed in each first outer window 13 c of the drive plate 13 and each second outer window 14 b of the driven plate 14.

  Each outer periphery side coil spring 15a is in contact with each first outer periphery side window portion 13c and each second outer periphery side window portion 14b in the circumferential direction. Specifically, each outer peripheral coil spring 15a is in contact with the wall portion of each first outer peripheral window portion 13c and the wall portion of each second outer peripheral window portion 14b. Further, each outer coil spring 15a is restricted from projecting in the axial direction by the cut-and-raised portion of each second outer window portion 14b.

  Each of the plurality of inner peripheral coil springs 15b elastically couples the drive plate 13 and the driven plate 14 to each other. Each inner peripheral coil spring 15 b is disposed in each first inner peripheral window portion 13 d of the drive plate 13 and each second inner peripheral window portion 14 c of the driven plate 14.

  Each inner peripheral coil spring 15b is in contact with each first inner peripheral window portion 13d and each second inner peripheral window portion 14c in the circumferential direction. Specifically, each inner peripheral coil spring 15b is in contact with the wall portion of each first inner peripheral window portion 13d and the wall portion of each second inner peripheral window portion 14c. Further, each inner circumferential coil spring 15b is restricted from projecting in the axial direction by the cut-and-raised portion of each second inner circumferential window 14c.

  Thus, by constituting the plurality of coil springs 15 (the plurality of outer peripheral side coil springs 15a and the plurality of inner peripheral side coil springs 15b), at least a part of the plurality of coil springs 15 is a dynamic damper in the axial direction. It is arranged side by side with an inertia part 51 (described later) of the device 5. For example, at least a part of the outer peripheral coil spring 15a is arranged side by side with the inertia part 51 in the axial direction. More specifically, a part of the outer peripheral side coil spring 15a is arranged side by side with the inertia part 51 in the axial direction.

<Clutch part>
The clutch unit 8 transmits the torque input to the housing 2 to the main damper device 4 or cancels the transmission of torque to the main damper device 4.

  The clutch portion 8 is configured to be able to connect the housing 2 and the main damper device 4. The clutch portion 8 is configured to be able to release the connection between the housing 2 and the main damper device 4.

  As shown in FIG. 1, the clutch portion 8 is disposed in the internal space S of the housing 2. The clutch portion 8 is disposed between the housing 2 and the main damper device 4 in the axial direction.

  Specifically, as shown in FIG. 2, the clutch portion 8 has a piston 18 and a friction member 19.

(piston)
The piston 18 engages with the main damper device 4 so as to be movable in the axial direction. For example, the piston 18 includes a piston main body 18a, a third outer peripheral side cylindrical portion 18b, and an inner peripheral side cylindrical portion 18c.

  The piston body 18a is formed in a substantially annular shape.

  The third outer peripheral cylindrical portion 18b is provided on the outer peripheral portion of the piston main body 18a. The third outer peripheral cylindrical portion 18b protrudes from the outer peripheral portion of the piston main body 18a toward the main damper device 4 side. A plurality of engaging recesses 18d are formed at the distal end of the third outer peripheral cylindrical portion 18b. Each of the plurality of engaging recesses 18d is disposed at a predetermined interval in the circumferential direction.

  The plurality of engaging recesses 18d engage with the plurality of engaging protrusions 13b of the main damper device 4 separately. Specifically, the plurality of engagement recesses 18 d engage with the plurality of engagement protrusions 13 b of the drive plate 13 so that the piston 18 can rotate integrally with the drive plate 13. In addition, the plurality of engagement recesses 18 d engage with the plurality of engagement projections 13 b of the drive plate 13 so that the piston 18 can move in the axial direction with respect to the drive plate 13.

  The inner peripheral cylindrical portion 18c is provided on the inner peripheral portion of the piston body 18a. The inner peripheral cylindrical portion 18c protrudes from the inner peripheral portion of the piston body 18a toward the main damper device 4 side. The inner peripheral cylindrical portion 18c is disposed on the outer peripheral portion of the output hub 3, for example, the outer peripheral surface of the second hub main body 3a. The inner peripheral cylindrical portion 18c is disposed on the outer peripheral surface of the second hub body 3a so as to be movable in the axial direction.

  Thus, the piston 18 can rotate integrally with the drive plate 13 and can move in the axial direction with respect to the drive plate 13 and the output hub 3.

(Friction member)
The friction member 19 is disposed between the cover portion 6 of the housing 2 and the axial direction of the piston 18. The friction member 19 is provided on the piston 18 so as to be in contact with the housing 2. For example, the friction member 19 is fixed to the piston main body 18 a so as to face the cover portion 6 of the housing 2.

  Here, the friction member 19 is pressed against the cover portion 6 of the housing 2 by the movement of the piston 18 toward the housing 2 side. In this state, the friction member 19 contacts the cover portion 6 of the housing 2, and the piston 18 rotates integrally with the housing 2. Thereby, the torque input to the housing 2 is transmitted from the housing 2 to the main damper device 4 via the piston 18.

  Here, in a state where the friction member 19 is in contact with the cover portion 6 of the housing 2, sliding of the friction member 19 with respect to the cover portion 6 of the housing 2 is permitted. For example, the pressing force of the piston 18 that presses the friction member 19 against the housing 2 is reduced from the clutch-on state. Then, the friction member 19 slides in contact with the cover portion 6 of the housing 2.

  Further, when the piston 18 moves to the transmission side, the friction member 19 moves away from the housing 2. Thereby, the transmission of torque from the housing 2 to the main damper device 4 is released.

  Here, a state in which the friction member 19 is pressed against the housing 2 by the piston 18, that is, a state in which torque is transmitted from the housing 2 to the main damper device 4 is defined as a clutch-on state. Further, a state in which the friction member 19 contacts the housing 2 and slides with the housing 2 and a state in which the friction member 19 is separated from the housing 2 are defined as a clutch-off state.

<Dynamic damper device>
The dynamic damper device 5 absorbs torsional vibration transmitted from the housing 2 to the main damper device 4. For example, when the torsional vibration of the engine is transmitted from the housing 2 to the main damper device 4, the torsional vibration is attenuated in the main damper device 4. Then, the torsional vibration output from the main damper device 4 is transmitted to the dynamic damper device 5. The dynamic damper device 5 absorbs this torsional vibration.

  The torsional vibration is vibration corresponding to torque fluctuation (rotational speed fluctuation). That is, the torsional vibration may include the meaning of torque fluctuation (rotational speed fluctuation).

  As shown in FIG. 1, the dynamic damper device 5 is disposed in the internal space S of the housing 2. The dynamic damper device 5 is arranged along with the main damper device 4 along the rotation axis O. Specifically, the dynamic damper device 5 is disposed between the transmission and the main damper device 4 in the axial direction. More specifically, the dynamic damper device 5 is disposed between the second cover 10 of the housing 2 and the main damper device 4 in the axial direction.

  Specifically, as shown in FIG. 3, the dynamic damper device 5 includes a damper plate part 50 (an example of an input member), an inertia part 51 (an example of an inertia mass body), and a plurality of (for example, four) dampers. A spring 52 (an example of a second elastic member) and a plurality of (for example, eight) stop pins 53 are provided.

(Damper plate part)
Torsional vibration output from the main damper device 4 is input to the damper plate portion 50. Specifically, as shown in FIG. 3, torsional vibration output from the main damper device 4 (see FIG. 2) is input to the damper plate portion 50 via the second hub flange 3 b of the output hub 3. Is done.

  Specifically, as shown in FIGS. 3 and 4, the damper plate portion 50 includes a damper plate main body 54 and a plurality of (for example, four) inertia engaging portions 55.

  The damper plate main body 54 is formed in a substantially annular shape. The inner peripheral portion of the damper plate main body 54, for example, the second fixing portion 54a is fixed to the second hub flange 3b of the output hub 3 by fixing means, for example, a plurality of rivets 12. Specifically, the second fixing portion 54a of the damper plate main body 54 is fixed to the second hub flange 3b of the output hub 3 together with the first fixing portions 14d of the pair of driven plate main bodies 14a by the plurality of rivets 12. .

  Each of the plurality of inertia engaging portions 55 is formed integrally with the outer peripheral portion of the damper plate main body 54. Each inertia engaging portion 55 is disposed on the outer peripheral portion of the damper plate main body 54 at a predetermined interval in the circumferential direction. Each inertia engaging portion 55 protrudes radially outward from the outer peripheral portion of the damper plate main body 54.

  At least a part of each inertia engagement portion 55 is arranged side by side with the plurality of coil springs 15 of the main damper device 4 in the axial direction. For example, at least a part of the inertia engaging portion 55 is arranged side by side with the outer peripheral side coil spring 15a in the axial direction. More specifically, a part of the inertia engaging portion 55 is arranged side by side with the outer peripheral side coil spring 15a in the axial direction.

  Each inertia engaging portion 55 includes a first spring accommodating portion 55a, a plurality of (for example, two) long holes 55b, and an inlay portion 55c.

  Each first spring accommodating portion 55a is provided in each inertia engaging portion 55 at a predetermined interval in the circumferential direction. Each first spring storage portion 55a is formed with a predetermined length in the circumferential direction. Each damper spring 52 is disposed in each first spring storage portion 55a.

  The plurality of long holes 55b are provided in each inertia engaging portion 55 on both sides in the circumferential direction of each first spring storage portion 55a. The plurality of long holes 55b have a predetermined length in the circumferential direction.

  Each inlay portion 55c is provided in each inertia engagement portion 55 on the radially inner side of the first spring storage portion 55a. Each inlay portion 55c is formed by cutting a part of each inertia engagement portion 55.

(Inertia part)
The inertia part 51 is configured to be movable relative to the damper plate part 50. Specifically, the inertia part 51 is configured to be rotatable relative to the damper plate part 50.

  Specifically, as shown in FIGS. 3 and 5, the inertia part 51 has a pair of inertia rings 56 and a pair of lid members 57.

  The pair of inertia rings 56 is configured to be rotatable relative to the damper plate portion 50. The pair of inertia rings 56 are disposed on both sides of the damper plate portion 50 in the axial direction. Each of the pair of inertia rings 56 has a substantially similar configuration.

  Each inertia ring 56 has a ring main body 56a, a plurality (for example, four) of second spring storage portions 56b, and a plurality (for example, four) of first through holes 56c.

  The ring body 56a is formed in a substantially annular shape. The ring main body 56a is disposed on both sides of the inertia engaging portion 55 in the axial direction. Similarly to the inertia engaging portion 55 described above, at least a part of the ring main body 56a is arranged side by side with the plurality of coil springs 15 of the main damper device 4 in the axial direction. For example, at least a part of the ring body 56a is arranged side by side with the outer peripheral coil spring 15a in the axial direction. More specifically, a part of the ring body 56a is arranged side by side with the outer peripheral coil spring 15a in the axial direction.

  Each of the second spring storage portions 56b is provided in the ring body 56a with a predetermined interval in the circumferential direction. Each second spring storage portion 56 b is formed at a position corresponding to the first spring storage portion 55 a of the damper plate portion 50. The first through holes 56c are provided in the ring body 56a with a predetermined interval in the circumferential direction. Each first through hole 56c is provided at a position corresponding to the center position in the circumferential direction of the long hole 55b of the damper plate portion 50.

  The pair of lid members 57 are configured to be rotatable relative to the damper plate portion 50 and to be integrally rotatable with the pair of inertia rings 56. As shown in FIG. 3, the pair of lid members 57 are disposed on both axial sides of the pair of inertia rings 56. The pair of lid members 57 have substantially the same configuration.

  Specifically, as shown in FIG. 6, the lid member 57 includes a lid body 57a, a second through hole 57b, and a third through hole 57c. The lid body 57a is formed in a substantially annular shape. The inner and outer diameters of the lid main bodies 57a are substantially the same as the inner and outer diameters of the inertia rings 56 (ring main bodies 56a). The second through holes 57b are provided in the lid body 57a with a predetermined interval in the circumferential direction. Each second through hole 57 b is provided at a position corresponding to each first through hole 56 c of the inertia ring 56. Each third through hole 57c is coaxial with each second through hole 57b and has a larger diameter than each second through hole 57b.

  In this configuration, the pair of lid members 57 is paired by inserting the stop pins 53 into the first through holes 56c of the inertia ring 56 and the second and third through holes 57b and 57c of the lid member 57. The inertia ring 56 and the damper plate portion 50 can be rotated relative to each other. The configuration of the stop pin 53 will be described later.

(Damper spring)
As shown in FIG. 3, each of the plurality of damper springs 52 is, for example, a coil spring 15. Each of the plurality of damper springs 52 is accommodated in the first spring accommodating portion 55 a of the damper plate portion 50 and the second spring accommodating portion 56 b of the inertia portion 51. Both end portions of each damper spring 52 are in contact with the circumferential wall portion of the first spring storage portion 55a and the circumferential wall portion of the second spring storage portion 56b. Thereby, when the damper plate part 50 and the inertia part 51 rotate relatively, each damper spring 52 is compressed between the circumferential wall part of the first spring storage part 55a and the circumferential wall part of the second spring storage part 56b. .

(stop pin)
Each of the plurality of stop pins 53 has a large-diameter trunk portion 53a and a small-diameter trunk portion 53b. The large-diameter trunk portion 53a is provided at the central portion in the axial direction. The large-diameter trunk portion 53 a has a larger diameter than the first through hole 56 c of the inertia ring 56 and a smaller diameter than the diameter (diameter direction dimension) of the long hole 55 b of the damper plate portion 50.

  The small-diameter trunk portion 53b is provided on both axial sides of the large-diameter trunk portion 53a. The small diameter trunk portion 53 b is inserted into the first through hole 56 c of the inertia ring 56 and the second through hole 57 b of the lid member 57. By caulking the head of the small-diameter trunk 53b, the head of the small-diameter trunk 53b is disposed in the third through hole 57c. As a result, the inertia ring 56 and the lid member 57 are fixed to both sides of the damper plate portion 50 in the axial direction.

  With the configuration described above, the inertia part 51 (the inertia ring 56 and the lid member 57) rotates relative to the damper plate part 50 within a range in which the stop pin 53 can move through the long hole 55b of the damper plate part 50. Is possible. And when the large diameter trunk | drum 53a of the stop pin 53 contact | abuts to the edge part of the elongate hole 55b, the relative rotation of the inertia part 51 (the inertia ring 56 and the cover member 57) with respect to the damper plate part 50 is controlled.

  Further, in a state where the inertia part 51 (the inertia ring 56 and the lid member 57) is fixed by the stop pin 53, the inner peripheral surface of the inertia ring 56 is in contact with the outer peripheral surface of the spigot part 55 c of the damper plate part 50. Thereby, the radial positioning of the inertia part 51 (the inertia ring 56 and the lid member 57) and the coil spring 15 is performed.

<Operation of vibration reduction device>
When engine torque is input to the housing 2, this torque is transmitted to the output hub 3 via the main damper device 4. Specifically, torque input to the housing 2 is transmitted to the main damper device 4 through the clutch portion 8.

  Here, on / off of the clutch portion 8 is switched by the hydraulic pressure difference between the hydraulic pressure in the space on the engine side from the piston 18 and the hydraulic pressure in the space on the transmission side from the piston 18.

  For example, when the hydraulic pressure of the transmission is greater than the hydraulic pressure on the engine side, the friction member 19 of the piston 18 contacts the housing 2 and the clutch is turned on. In this state, the friction member 19 of the piston 18 can slide with respect to the housing 2 by reducing the hydraulic pressure difference. When the engine-side hydraulic pressure is higher than the transmission-side hydraulic pressure, the friction member 19 of the piston 18 is separated from the housing 2 and the clutch is turned off.

  For example, when the clutch portion 8 connects the housing 2 and the main damper device 4 and the piston 18 rotates integrally with the housing 2 via the friction member 19 (when the clutch is on), the torque is “ It is transmitted to the output hub 3 through a path of the drive plate 13 → the plurality of outer periphery side coil springs 15a and the plurality of inner periphery side coil springs 15b → the driven plate 14 ”.

  Here, the main damper device 4 transmits torque and attenuates torsional vibration input from the housing 2 via the connecting plate. Specifically, when torsional vibration is input to the main damper device 4, each outer coil spring 15 a and each inner coil spring 15 b are compressed between the drive plate 13 and the driven plate 14. Thereby, the torsional vibration input from the engine can be attenuated.

  Further, when the friction member 19 slides on the housing 2 in a state where the friction member 19 of the clutch portion 8 is in contact with the housing 2, torque corresponding to the frictional resistance between the friction member 19 and the housing 2 is applied to the main damper device 4. Is input. In this case, torque corresponding to the frictional resistance is transmitted to the output hub 3 through the above-described path.

  Further, when the clutch portion 8 releases the connection between the housing 2 and the main damper device 4 (when the clutch is off), the friction member 19 of the clutch portion 8 is separated from the housing 2 of the housing 2. In this case, torque is not transmitted from the housing 2 to the main damper device 4. That is, when the clutch portion 8 is off, torque is not transmitted from the main damper device 4 to the output hub 3.

  Further, the output hub 3 is provided with a dynamic damper device 5 together with the main damper device 4. Thereby, the torsional vibration (torque fluctuation / rotational speed fluctuation) output from the main damper device 4 can be effectively suppressed in the dynamic damper device 5.

  For example, when the torsional vibration from the main damper device 4 is transmitted to the dynamic damper device 5, the inertia part 51 rotates relative to the damper plate part 50 via the plurality of damper springs 52. More specifically, the inertia part 51 rotates in a direction opposite to the rotation direction of the damper plate part 50 while the plurality of damper springs 52 are compressed and expanded by the input of torsional vibration. That is, the inertia part 51 and the damper plate part 50 produce a phase difference in the rotation direction (circumferential direction). Due to the occurrence of this phase difference, the torsional vibration is absorbed by the dynamic damper device 5.

  As described above, the vibration reducing device 1 operates. For example, when the vibration reduction device 1 (the main damper device 4 and the dynamic damper device 5) that operates in the clutch-on state may resonate due to a change in the engine speed, the system of the vibration reduction device 1 becomes a resonance point. As it approaches, the torsion angle in the main damper device 4 gradually increases.

  In this case, the pressing force of the piston 18 that presses the friction member 19 against the housing 2 is relaxed. Then, the friction member 19 slides in contact with the housing 2. Thereby, generation | occurrence | production of an excessive torsional vibration can be suppressed. That is, each component of the vibration reducing device 1 can be appropriately operated in the resonance point of the vibration reducing device 1 and in the vicinity of the resonance point, and torsional vibration can be stably damped in each component of the vibration reducing device 1.

  Further, when the vibration reducing device 1 is operating in the clutch-on state, when the system of the vibration reducing device 1 suddenly approaches the resonance point, the clutch unit 8 is connected to the housing 2 and the main damper device 4. Release the link. That is, the clutch unit 8 is set in a clutch-off state. Then, the friction member 19 is separated from the housing 2 of the housing 2, and the transmission of torque from the housing 2 to the main damper device 4 is released. Thereby, generation | occurrence | production of an excessive torsional vibration can be prevented. That is, each component of the vibration reducing device 1 can be appropriately operated in the resonance point of the vibration reducing device 1 and in the vicinity of the resonance point, and torsional vibration can be stably damped in each component of the vibration reducing device 1.

  After the torsional vibration is actively damped in the vibration reducing device 1 as described above, when the system of the vibration reducing device 1 leaves the resonance point, the clutch unit 8 returns to the clutch-on state, and the vibration reducing device 1 Works.

<Summary>
The above-described embodiment can also be described as follows.

  (1) The vibration reducing device 1 is for reducing torsional vibration from the engine. The vibration reducing device 1 includes a housing 2, an output hub 3, a main damper device 4, a dynamic damper device 5, and a clutch unit 8. Torsional vibration is input to the housing 2. The output hub 3 is disposed so as to be rotatable relative to the housing 2. The main damper device 4 is disposed between the housing 2 and the output hub 3, and attenuates torsional vibration input to the housing 2. The dynamic damper device 5 absorbs torsional vibration output from the main damper device 4. The clutch portion 8 is disposed between the housing 2 and the main damper device 4. The clutch unit 8 is configured to be able to connect the housing 2 and the main damper device 4 and to be able to release the connection between the housing 2 and the main damper device 4.

  In the vibration reducing device 1, when the clutch unit 8 is connected to the housing 2 and the main damper device 4 and the system of the vibration reducing device 1 approaches the resonance point, the clutch unit 8 is connected to the housing 2 and the main damper device 1. The connection of the damper device 4 is released. Thereby, it is possible to prevent transmission of excessive torsional vibration from the vibration reducing device 1 to the member on the transmission side. That is, the vibration reducing device 1 can be operated appropriately, and the torsional vibration can be appropriately damped in the vibration reducing device 1.

  (2) In the vibration reducing device 1, the housing 2 constitutes the internal space S that can contain the lubricating oil. The main damper device 4, the dynamic damper device 5, and the clutch unit 8 are disposed in the internal space S.

  In this case, the main damper device 4, the dynamic damper device 5, and the clutch portion 8 are disposed in the internal space S of the housing 2 in a state where the lubricating oil is accommodated in the internal space S of the housing 2. 4. The dynamic damper device 5 and the clutch unit 8 can be stably operated.

  (3) In the vibration reducing device 1, the clutch unit 8 includes the piston 18 and the friction member 19. The piston 18 engages with the main damper device 4 so as to be movable in a direction along the rotation axis O. The friction member 19 is provided on the piston 18 so as to be in contact with the housing 2.

  By configuring the clutch portion 8 in this manner, it is possible to suitably prevent transmission of excessive torsional vibration from the vibration reducing device 1 to the transmission-side member.

  (4) In the vibration reducing device 1, the piston 18 can rotate integrally with the housing 2 with the friction member 19 in contact with the housing 2. Further, the piston 18 can rotate relative to the housing 2 in a state where the friction member 19 is in contact with the housing 2.

  In this case, the torque can be transmitted from the housing 2 to the main damper device 4 by integrally rotating the piston 18 and the housing 2 via the friction member 19. Thereby, torsional vibration can be suitably damped.

  (5) In the vibration reducing device 1, the housing 2 constitutes the internal space S that can contain the lubricating oil. The friction member 19 contacts or separates from the housing 2 due to a hydraulic pressure difference between the hydraulic pressure between the housing 2 and the piston 18 and the hydraulic pressure between the main damper device 4 and the piston 18.

  By configuring the clutch portion 8 in this manner, it is possible to suitably prevent transmission of excessive torsional vibration from the vibration reducing device 1 to the transmission-side member.

  (6) In the vibration reducing device 1, the dynamic damper device 5 is arranged side by side with the main damper device 4 in the direction along the rotation axis O.

  In this case, since the dynamic damper device 5 is not restricted by the main damper device 4 in arrangement, the dynamic damper device 5 can be operated effectively. For example, since the dynamic damper device 5 can be disposed radially outside, the dynamic damper device 5 can be effectively operated.

  (7) In the vibration reducing device 1, the main damper device 4 includes the drive plate 13, the driven plate 14, and at least one coil spring 15. The drive plate 13 is connected to the housing 2. The driven plate 14 is disposed so as to be rotatable relative to the drive plate 13. The driven plate 14 is connected to the output hub 3. At least one coil spring 15 elastically connects the drive plate 13 and the driven plate 14.

  Even if the main damper device 4 is configured in this manner, the vibration reducing device 1 can be appropriately operated, and the torsional vibration can be stably damped in the vibration reducing device 1.

  (8) In the vibration reducing device 1, the dynamic damper device 5 includes a damper plate portion 50, an inertia portion 51, and at least one damper spring 52. Torsional vibration output from the main damper device 4 is input to the damper plate portion 50. The inertia part 51 is configured to be movable relative to the damper plate part 50. At least one damper spring 52 elastically connects the damper plate part 50 and the inertia part 51.

  Even if the dynamic damper device 5 is configured in this manner, the vibration reducing device 1 can be appropriately operated, and the torsional vibration can be stably damped in the vibration reducing device 1.

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

  (A) In the above-described embodiment, an example in which the on / off state of the clutch unit 8 is switched by the hydraulic pressure difference between the hydraulic pressure in the space closer to the engine than the piston 18 and the hydraulic pressure in the space closer to the transmission than the piston 18 has been described. Instead, as shown in FIG. 8, the vibration reducing device 101 may be configured to switch on and off of the clutch unit 8 using a cone spring (an example of an urging member).

  In FIG. 8, components that are substantially the same as those in the embodiment are denoted by the same reference numerals as those in the embodiment.

  In this case, as shown in FIG. 8, the clutch portion 108 further includes a cone spring 120. The cone spring 120 is disposed between the piston 18 and the axial direction of the main damper device 4. Specifically, the cone spring 120 is disposed between the inner peripheral portion of the piston 18 and the axial direction of the inner peripheral portion of the driven plate 14 of the main damper device 4. The cone spring 120 urges the piston 18 toward the housing 2, for example, the first cover portion 9. Thereby, the friction member 19 of the piston 18 is in contact with the housing 2 (clutch-on state). Here, the hydraulic pressure difference is set to substantially zero, for example.

  Subsequently, when the hydraulic pressure on the engine side is increased and the hydraulic pressure on the engine side becomes larger than the urging force of the cone spring 120, the friction member 19 of the piston 18 slides in contact with the housing 2. When the engine-side hydraulic pressure is further increased, the friction member 19 of the piston 18 separates from the housing 2. Even if comprised in this way, the clutch 108 can be operated similarly to the said embodiment.

  (B) In the said embodiment, the example in case the main damper apparatus 4 is arrange | positioned in the axial direction at the engine side rather than the dynamic damper apparatus 5 was shown. Instead of this, the dynamic damper device 5 may be disposed closer to the engine than the main damper device 4 in the axial direction.

  In this case, the piston 18 connects the main damper device 4 and the second cover 10 of the housing 2. The dynamic damper device 5 is disposed between the engine and the main damper device 4 in the axial direction. Specifically, the dynamic damper device 5 is arranged between the engine-side housing 2 and the main damper device 4 in the axial direction. More specifically, the dynamic damper device 5 is disposed between the first cover 9 of the housing 2 and the main damper device 4 in the axial direction. Even if comprised in this way, the effect similar to the said embodiment can be acquired.

  (C) The main damper device 4 of the above embodiment is shown as an example of the main damper device 4, and the main damper device 4 may be configured in any way.

  For example, the main damper device 4 elastically drives the drive plate 13 connected to the housing 2, the driven plate 14 that is arranged to be rotatable relative to the drive plate 13 and connected to the output hub 3, and the drive plate 13 and the driven plate 14. As long as it has at least one coil spring 15 to be connected to each other, it may be configured in any way.

  (D) The dynamic damper device 5 of the above embodiment is shown as an example of the dynamic damper device 5, and the configuration of the dynamic damper device 5 may be configured in any way.

  For example, the dynamic damper device 5 includes a damper plate portion 50 to which torsional vibration output from the main damper device 4 is input, an inertia portion 51 configured to be relatively movable with respect to the damper plate portion 50, and a damper plate portion. 50 and at least one damper spring 52 that elastically connects the inertia part 51 may be used.

  (E) The dynamic damper device 5 of the above-described embodiment is shown as an example of a dynamic vibration absorber, and the configuration of the dynamic damper device 5 may be configured in any way.

  For example, as shown in FIG. 9, the dynamic damper device 105 may be configured. In this case, the dynamic damper device 105 has a pair of damper plate portions 150 and a plurality of inertia portions 151. One of the pair of damper plate portions 150 is fixed to the output hub 3 (second hub flange 3b) by a plurality of rivets 12. The other (not shown) of the pair of damper plate portions 150 is disposed to face one of the pair of damper plate portions 150 in the axial direction, and one of the pair of damper plate portions 150 is formed by a plurality of rivets 155. It is fixed to.

  Each of the plurality of inertia portions 151 is disposed between the pair of damper plate portions 150 in the axial direction, and is supported to be swingable with respect to the pair of damper plate portions 150. In detail, each of the plurality of inertia parts 151 is swingably supported by the pair of damper plate parts 150 via a plurality of (for example, two) pin members 152.

  Each pin member 152 is inserted through each first long hole 150 a of the pair of damper plate portions 150 and each second long hole 151 a of the inertia portion 151. The first elongated hole 150a has a central portion that swells to the outer peripheral side, and is substantially arc-shaped. The second elongated hole 151a has a central portion that swells toward the inner peripheral side, and is substantially formed in an arc shape.

  In this configuration, when the torsional vibration from the main damper device 4 is transmitted to the dynamic damper device 105, each inertia part 151 swings with respect to the damper plate part 150 via the pin member 152.

  Here, the swing center P of each inertia part 151 is provided radially outward from the rotational axis O, and each inertia part 151 swings relative to the damper plate part 150 with respect to the swing center P. Move.

  More specifically, each inertia part 151 swings on the basis of the swing center P so as to suppress the rotation of the damper plate part 150. Thereby, the torsional vibration is absorbed by the dynamic damper device 105.

  (F) The dynamic damper device 5 of the above embodiment is shown as an example of a dynamic vibration absorber, and the configuration of the dynamic damper device 5 may be configured in any way.

  For example, as shown in FIG. 10, a dynamic damper device 205 may be configured. In this case, the dynamic damper device 205 includes a damper plate portion 250, an inertia portion 251 (for example, a pair of inertia rings), and a plurality of centrifuges 252. The damper plate portion 250 is fixed to the output hub 3 (second hub flange 3b) by a plurality of rivets 12 (see FIGS. 2 and 3).

  The inertia part 251 is configured to be rotatable relative to the damper plate part 250. The inertia part 251 has a pair of inertia rings 224 and a pin member 225 that connects the pair of inertia rings 224. A damper plate portion 250 is disposed between the axial directions of the pair of inertia rings.

  The centrifuge 252 engages with the inertia part 251 by centrifugal force. The centrifuge 252 guides the inertia part 251 so that the relative displacement between the damper plate part 250 and the inertia part 251 becomes small.

  Specifically, each centrifuge 252 is disposed in each of the plurality of recesses 250a of the damper plate portion 250 so as to be movable in the radial direction by centrifugal force. A cam surface 252a is formed on the radially outer surface of each centrifuge. Each pin member 225 can come into contact with each cam surface 252a. In a state where each pin member 225 is in contact with each cam surface 252a, each pin member 225 is movable along each cam surface 252a.

  The pin member 225 has a shaft portion that is fixed to each of the pair of inertia portions 251 at both ends, and a roller portion that can rotate around the shaft portion. Here, the roller portion is in contact with the cam surface 252a.

  In this configuration, as shown in FIG. 10A, when each centrifuge 252 moves radially outward by centrifugal force, the cam surface 252 a of each centrifuge 252 abuts on each pin member 225. In this state, when the torsional vibration from the main damper device 4 is transmitted to the dynamic damper device 205, as shown in FIG. 10 (b), the inertia portion 251 (a pair of inertia rings 224) becomes the damper plate portion. It moves relative to 250 in the circumferential direction. At this time, as each centrifuge 252 moves inward in the radial direction, each pin member 225 moves along the cam surface 252a of each centrifuge 252 in a rotation direction (opposite direction) opposite to the rotation direction of the damper plate portion 250. AR). That is, the inertia part 251 (pin member 225) moves in the opposite direction AR.

  At this time, each pin member 225 presses the cam surface 252a of each centrifuge 252. For example, the pressing force P <b> 0 in FIG. 10B acts from each pin member 225 to the cam surface 252 a of each centrifuge 252. Then, the damper plate portion 250 (each centrifuge 252) is pulled back in the opposite direction AR by the component force P1 of the pressing force P0. Thus, each centrifuge 252 guides the inertia part 251 so that the relative displacement of the damper plate part 250 and the inertia part 251 becomes small. In other words, the inertia part 251 suppresses the rotation of the damper plate part 250 through each centrifuge 252. Thereby, the torsional vibration is absorbed by the dynamic damper device 205.

DESCRIPTION OF SYMBOLS 1 Vibration reduction device 2 Housing 3 Output hub 4 Main damper device 13 Drive plate 14 Driven plate 15 Coil spring 5 Dynamic damper device 50 Damper plate part 51 Inertia part 52 Damper spring 8 Clutch part 18 Piston 19 Friction member O Rotating shaft core S Inside space

Claims (12)

  1. A vibration reducing device for reducing torsional vibration from an engine,
    An input rotating unit to which the torsional vibration is input;
    An output rotation unit arranged to be rotatable relative to the input rotation unit;
    A damper unit disposed between the input rotating unit and the output rotating unit and dampening torsional vibration input to the input rotating unit;
    A dynamic vibration absorber that absorbs torsional vibration output from the damper section;
    A clutch unit disposed between the input rotation unit and the damper unit, configured to be able to connect the input rotation unit and the damper unit, and to be able to disconnect the input rotation unit and the damper unit;
    A vibration reduction device comprising:
  2. The input rotating part constitutes an internal space capable of accommodating lubricating oil,
    The damper portion, the dynamic vibration absorber, and the clutch portion are disposed in the internal space.
    The vibration reducing device according to claim 1.
  3. The clutch portion includes a piston that engages with the damper portion so as to be movable in a direction along a rotation axis of the input rotation portion, and a friction member that is provided on the piston so as to be able to contact the input rotation portion. ing,
    The vibration reduction apparatus according to claim 1 or 2.
  4. In a state where the friction member is in contact with the input rotation unit, the piston can rotate integrally with the input rotation unit and can rotate relative to the input rotation unit.
    The vibration reducing apparatus according to claim 3.
  5. The input rotating part constitutes an internal space capable of accommodating lubricating oil,
    The friction member of the piston comes into contact with or separates from the input rotation part due to a hydraulic pressure difference between the oil pressure between the input rotation part and the piston and the oil pressure between the damper part and the piston.
    The vibration reducing device according to claim 3 or 4.
  6. The input rotating part constitutes an internal space capable of accommodating lubricating oil,
    The clutch portion further includes a biasing member that biases the piston toward the input rotation portion,
    The piston is moved toward the input rotating portion by the biasing force of the biasing member, the friction member is in contact with the input rotating portion,
    The piston is separated from the input rotation unit and the friction member is separated from the input rotation unit due to a hydraulic pressure difference between the hydraulic pressure between the input rotation unit and the piston and the hydraulic pressure between the damper unit and the piston. ,
    The vibration reducing device according to claim 3 or 4.
  7. The dynamic vibration absorber is arranged side by side with the damper portion in a direction along the rotation axis of the input rotation portion.
    The vibration reducing apparatus according to any one of claims 1 to 6.
  8. The damper part includes a first rotating member connected to the input rotating part, a second rotating member arranged to be rotatable relative to the first rotating member and connected to the output rotating part, and the first rotating member. And a first elastic member that elastically connects the second rotating member,
    The vibration reducing apparatus according to any one of claims 1 to 7.
  9. The dynamic vibration absorber includes an input member to which the torsional vibration output from the damper portion is input, and an inertia mass body configured to be relatively movable with respect to the input member.
    The vibration reducing apparatus according to any one of claims 1 to 8.
  10. The dynamic vibration absorber further includes a second elastic member that elastically connects the input member and the inertial mass body,
    The vibration reducing device according to claim 9.
  11. Each of the plurality of inertial mass bodies is supported by the input member so as to be swingable with reference to a swing center radially outside the rotational axis of the input rotating portion.
    The vibration reducing device according to claim 9.
  12. The dynamic vibration absorber further includes a centrifuge that engages the inertial mass body by centrifugal force and guides the inertial mass body so that a relative displacement between the input member and the inertial mass body is reduced.
    The vibration reducing device according to claim 9.
JP2016163973A 2016-08-24 2016-08-24 Vibration reduction device Pending JP2018031425A (en)

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JP2016163973A JP2018031425A (en) 2016-08-24 2016-08-24 Vibration reduction device

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Application Number Priority Date Filing Date Title
JP2016163973A JP2018031425A (en) 2016-08-24 2016-08-24 Vibration reduction device
PCT/JP2017/027186 WO2018037821A1 (en) 2016-08-24 2017-07-27 Vibration reduction device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112008003167B4 (en) * 2007-11-29 2016-07-21 Schaeffler Technologies AG & Co. KG Power transmission device with a speed adaptive absorber and method for improving the damping behavior
JP5595390B2 (en) * 2008-07-04 2014-09-24 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフトSchaeffler Technologies AG & Co. KG Hydrodynamic torque converter
JP6010476B2 (en) * 2013-02-07 2016-10-19 株式会社エクセディ Dynamic damper device
JP5685304B2 (en) * 2013-06-04 2015-03-18 株式会社エクセディ Torque converter lockup device
JP6541969B2 (en) * 2014-12-26 2019-07-10 株式会社エクセディ Power transmission device and lockup device for torque converter
JP6530604B2 (en) * 2015-01-06 2019-06-12 株式会社エクセディ Power transmission

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