WO2018016212A1

WO2018016212A1 - Torque fluctuation suppression device, torque converter, and motive force transmission device

Info

Publication number: WO2018016212A1
Application number: PCT/JP2017/020880
Authority: WO
Inventors: 富山　直樹
Original assignee: 株式会社エクセディ
Priority date: 2016-07-20
Filing date: 2017-06-05
Publication date: 2018-01-25
Also published as: JP2018013153A

Abstract

The present invention suppresses a torque fluctuation peak across a comparatively wide rotation speed range in a device for suppressing the torque fluctuations of a rotating member. To this end, this device is equipped with a body of mass (20), a centrifugal element (21), a cam mechanism (22), and a movement restriction part. The body of mass (20) is capable of rotating relative to an output-side rotating body (12). The centrifugal element (21) is supported by the output-side rotating body (12), and is capable of moving in the radial direction. The cam mechanism (22) has a cam (31) and a roller (30), receives a centrifugal force acting on the centrifugal element (21), and when a rotational phase difference is produced between the output-side rotating body (12) and the body of mass (20), converts the centrifugal force into a circumferential-direction force in the direction which decreases relative displacement. The movement restriction part has an orifice (Or) capable of circulating a working fluid according to the movement of the centrifugal element (21) in the radial direction, and restricts the speed of the movement of the centrifugal element (21) toward the inside in the radial direction.

Description

Torque fluctuation suppressing device, torque converter, and power transmission device

The present invention relates to a torque fluctuation suppressing device, and more particularly to a torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input. The present invention also relates to a torque converter and a power transmission device including a torque fluctuation suppressing device.

For example, a clutch device including a damper device and a torque converter are provided between an automobile engine and a transmission. Further, the torque converter is provided with a lockup device for mechanically transmitting torque at a predetermined rotational speed or more in order to reduce fuel consumption.

The lockup device generally has a clutch part and a damper having a plurality of torsion springs. The clutch portion has a piston with a friction member that is pressed against the front cover by the action of hydraulic pressure. In the lock-up-on state, torque is transmitted from the front cover to the piston via the friction member, and further transmitted to the output side member via the plurality of torsion springs.

In such a lock-up device, torque fluctuations (rotational speed fluctuations) can be suppressed by a damper having a plurality of torsion springs.

Further, in the lock-up device of Patent Document 1, torque fluctuation is suppressed by providing a dynamic damper device including an inertia member. The dynamic damper device of Patent Document 1 is mounted on a plate that supports a torsion spring, a pair of inertia rings that are rotatable relative to the plate, and a plurality of coil springs provided between the plate and the inertia ring. And have.

Japanese Patent Laying-Open No. 2015-094424

In the conventional dynamic damper device including Patent Document 1, the peak of torque fluctuation in a predetermined rotation speed range can be suppressed. However, when the engine specifications change, the rotational speed range in which the peak of torque fluctuations changes accordingly. For this reason, it is necessary to change the inertial amount of inertia and the spring constant of the coil spring in accordance with changes in the engine specifications and the like, which may be difficult to cope with.

An object of the present invention is to be able to suppress a peak of torque fluctuation in a relatively wide rotational speed range in an apparatus for suppressing torque fluctuation of a rotating member.

(1) A torque fluctuation suppressing device according to the present invention is a device for suppressing torque fluctuation of a rotating body to which torque is input, and includes a mass body, a centrifuge, a cam mechanism, a movement restricting portion, It has. The mass body is arranged side by side with the rotating body in the axial direction, is rotatable with the rotating body, and is disposed so as to be relatively rotatable with respect to the rotating body. The centrifuge is supported by the rotating body and is arranged to be movable in the radial direction under centrifugal force. The cam mechanism has a cam and a cam follower, and receives a centrifugal force acting on the centrifuge, and when a relative displacement in the rotational direction occurs between the rotating body and the mass body, the centrifugal force is reduced to a small relative displacement. Convert to a circumferential force in the direction The cam is provided on one of the centrifuge and the mass body. The cam follower is provided on the other of the centrifuge and the mass body and moves along the cam. The movement restricting unit has an oil passage through which the viscous fluid can flow along with the movement of the centrifuge in the radial direction, and regulates the moving speed of the centrifuge inward in the radial direction.

In this device, when torque is input to the rotating body, the rotating body and the mass body rotate. When there is no change in the torque input to the rotating body, there is no relative displacement in the rotating direction between the rotating body and the mass body, and the rotor rotates synchronously. On the other hand, when there is a fluctuation in the input torque, the mass body is arranged so as to be relatively rotatable with respect to the rotating body. This displacement may be expressed as “rotational phase difference”).

Here, when the rotating body and the mass body rotate, the centrifuge receives a centrifugal force. When a relative displacement occurs between the rotating body and the mass body, the cam mechanism converts the centrifugal force acting on the centrifuge into a circumferential force, which is applied between the rotating body and the mass body. It acts to reduce the relative displacement of. Torque fluctuation is suppressed by the operation of the cam mechanism.

Here, since the centrifugal force acting on the centrifuge is used as a force for suppressing the torque fluctuation, the characteristic for suppressing the torque fluctuation changes according to the rotational speed of the rotating body. Further, for example, the characteristics for suppressing torque fluctuation can be appropriately set depending on the shape of the cam and the like, and the peak of torque fluctuation in a wider rotational speed range can be suppressed.

Also, here, when the centrifuge moves in the radial direction, the viscous fluid passes through the oil passage of the movement restricting portion. Due to the resistance caused by the viscous fluid passing through the oil passage (especially the oil passage having a reduced cross-sectional area), the moving speed of the centrifuge decreases. Therefore, it is possible to suppress the hitting sound when the centrifuge falls to the inner peripheral side and collides with another member when the rotation is stopped. In addition, when the torque fluctuation increases and the relative displacement between the rotating body and the mass body increases, the centrifuge is moved inward in the radial direction by the action of the cam mechanism. In this case as well, the movement of the centrifuge is restricted. The For this reason, the relative displacement between the rotating body and the mass body is restricted. That is, the movement restricting portion also functions as a stopper mechanism that restricts the relative rotation angle between the rotating body and the mass body.

(2) Preferably, the rotating body has a protrusion protruding outward in the radial direction on the outer periphery. The protruding portion opens in the outer peripheral direction and has an opening having a predetermined depth on the inner peripheral side. And a centrifuge has a hole part in which a projection part is inserted, and a piston part inserted in an opening part.

Here, the centrifuge can move in the radial direction along the protrusion. Moreover, an opening part functions as a cylinder by inserting a piston part in an opening part. Accordingly, the viscous fluid in the cylinder is moved by the movement of the piston portion of the centrifuge, and the moving speed of the centrifuge is regulated by the moving viscous fluid passing through the oil passage.

(3) Preferably, the oil passage is a gap around the piston portion inserted into the opening. Here, it is possible to configure an oil passage that becomes a resistance when the hydraulic oil passes by a simple configuration.

(4) Preferably, a fluid accommodating portion capable of accommodating a viscous fluid is formed by the opening of the rotating body and the hole of the centrifuge into which the protrusion of the rotating body is inserted.

(5) Preferably, the centrifuge is formed so as to extend in the rotational direction and has guide portions formed at both ends in the rotational direction. And the guide part is supported by the end surface of the circumferential direction of the projection part of a rotary body.

(6) Preferably, the cam is provided in the centrifuge and the cam follower is provided in the mass body. When the relative displacement in the rotational direction occurs between the rotating body and the mass body, the centrifuge guide portion is located on the opposite side of the contact point between the cam and the cam follower with the center of gravity of the centrifuge interposed therebetween. Abuts against the circumferential end face.

Here, when a relative displacement in the rotational direction occurs between the rotating body and the mass body and the cam mechanism is operated, the guide portion of the centrifuge has at least a contact point between the cam and the cam follower with the center of gravity of the centrifuge interposed therebetween. It abuts against the end face of the protrusion at the opposite position. For this reason, in a centrifuge, it can suppress that a big rotational moment arises by using the end of a rotation direction as a fulcrum. Therefore, the centrifuge moves smoothly, and the configuration of the guide portion can be simplified.

(7) Preferably, the guide portion is a pair of rollers that are rotatably supported at both ends in the rotation direction of the centrifuge and roll on the circumferential end surface of the protrusion.

In this case, the movement of the centrifuge in the radial direction becomes smooth. Also, if the centrifuge is configured to generate a rotational moment with one end in the rotation direction as a fulcrum, in order to move the centrifuge smoothly, for example, the guide portions are respectively arranged on the inner peripheral side and the outer peripheral side. It is necessary to provide a pair of rollers (two pairs in total).

However, in the present invention, as described above, in the centrifuge, since the rotational moment with one end in the rotational direction as a fulcrum is suppressed, even if the guide portion is configured by only a pair of rollers, The centrifuge can be moved smoothly.

(8) Preferably, the rotating body has a concave portion recessed on the inner peripheral side on the outer peripheral surface, and the centrifuge is accommodated in the concave portion.

(9) Preferably, the centrifuge has a hole that is recessed from the inner peripheral surface to the outer peripheral side, and the rotating body has a protrusion that is inserted into the hole of the centrifuge on the bottom surface of the recess.

(10) Preferably, a viscous fluid can be accommodated in the hole of the centrifuge, and the oil passage is a gap around the protrusion of the rotating body inserted into the hole.

(11) Preferably, the mass body includes a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween, and a pin that connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. , Further. Preferably, the centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin. The cam follower is a cylindrical roller having a hole through which a pin penetrates in the axial direction. In addition, the cam is formed in the centrifuge and contacts the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body.

Here, the cam follower is mounted using a pin that connects the first inertia ring and the second inertia ring. This simplifies the configuration of the cam mechanism.

(12) The torque converter according to the present invention is disposed between the engine and the transmission. The torque converter includes an input-side rotating body that receives torque from the engine, an output-side rotating body that outputs torque to the transmission, and a damper that is disposed between the input-side rotating body and the turbine. Any of the torque fluctuation suppression devices.

(13) A power transmission device according to the present invention includes a flywheel, a clutch device, and any of the torque fluctuation suppression devices described above. The flywheel includes a first inertial body that rotates about a rotation axis, a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body, and a first inertial body and a second inertial body. And a damper disposed therebetween. The clutch device is provided on the second inertial body of the flywheel.

In the present invention as described above, the peak of torque fluctuation can be suppressed in a relatively wide rotational speed range in the apparatus for suppressing torque fluctuation of the rotating member. Further, according to the present invention, it is possible to suppress the hitting sound that the centrifuge collides with other members, and it is possible to realize the stopper mechanism with a simple configuration.

The schematic diagram of the torque converter by a 1st embodiment of the present invention. FIG. 2 is a partial front view of the output side rotating body and the torque fluctuation suppressing device of FIG. 1. FIG. 3 is an arrow A view of FIG. 2. The external appearance perspective view of the part shown by FIG. The figure for demonstrating the internal structure of a centrifuge. The figure for demonstrating the action | operation of a cam mechanism. The figure for demonstrating the action | operation of a cam mechanism. The characteristic view which shows the relationship between a rotation speed and a torque fluctuation. The figure corresponding to FIG. 2 of 2nd Embodiment of this invention. The arrow B figure of FIG. The schematic diagram which shows the application example 1 of this invention. The schematic diagram which shows the application example 2 of this invention. The schematic diagram which shows the application example 3 of this invention. The schematic diagram which shows the application example 4 of this invention. The schematic diagram which shows the application example 5 of this invention. The schematic diagram which shows the application example 6 of this invention. The schematic diagram which shows the application example 7 of this invention. The schematic diagram which shows the application example 8 of this invention. The schematic diagram which shows the application example 9 of this invention.

-First embodiment-
FIG. 1 is a schematic diagram when the torque fluctuation suppressing device according to the first embodiment of the present invention is mounted on a lock-up device of a torque converter. In FIG. 1, OO is the rotational axis of the torque converter.

[overall structure]
The torque converter 1 includes a front cover 2, a torque converter main body 3, a lockup device 4, and an output hub 5. Torque is input to the front cover 2 from the engine. The torque converter main body 3 includes an impeller 7 connected to the front cover 2, a turbine 8, and a stator (not shown). The turbine 8 is connected to the output hub 5, and an input shaft (not shown) of the transmission can be engaged with the inner peripheral portion of the output hub 5 by a spline.

[Lock-up device 4]
The lock-up device 4 has a clutch part, a piston that is operated by hydraulic pressure, and the like, and can take a lock-up on state and a lock-up off state. In the lock-up on state, the torque input to the front cover 2 is transmitted to the output hub 5 via the lock-up device 4 without passing through the torque converter body 3. On the other hand, in the lock-up off state, torque input to the front cover 2 is transmitted to the output hub 5 via the torque converter body 3.

The lockup device 4 includes an input side rotating body 11, an output side rotating body 12, a damper 13, and a torque fluctuation suppressing device 14.

The input side rotating body 11 includes a piston that is movable in the axial direction, and has a friction member 16 on the side surface on the front cover 2 side. When the friction member 16 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the input side rotating body 11.

The output side rotator 12 is disposed so as to face the input side rotator 11 in the axial direction, and is rotatable relative to the input side rotator 11. The output side rotating body 12 is connected to the output hub 5.

The damper 13 is disposed between the input side rotating body 11 and the output side rotating body 12. The damper 13 has a plurality of torsion springs, and elastically connects the input side rotating body 11 and the output side rotating body 12 in the rotation direction. The damper 13 transmits torque from the input-side rotator 11 to the output-side rotator 12, and absorbs and attenuates torque fluctuations.

[Torque fluctuation suppressing device 14]
FIG. 2 is a front view of the output side rotating body 12 and the torque fluctuation suppressing device 14. 2 shows a part of the output-side rotator 12 and the torque fluctuation suppressing device 14, but as a whole, the portions shown in FIG. 2 are provided at equiangular intervals at four locations in the circumferential direction. ing. 3 is a view seen from the direction A in FIG. 2, and FIG. 4 is an external perspective view of FIG. In FIG. 4, the inertia ring on one side (front side in FIG. 4) is removed and shown.

The torque fluctuation suppressing device 14 includes a first inertia ring 201 and a second inertia ring 202 that constitute the mass body 20, four centrifuges 21, and four cam mechanisms 22.

<First and second inertia rings 201, 202>
The first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape. As shown in FIG. 3, the output-side rotator 12 sandwiches the output-side rotator 12. Are arranged with a predetermined gap on both sides in the axial direction. That is, the output-side rotating body 12 and the first and second inertia rings 201 and 202 are arranged side by side in the axial direction. The first and second inertia rings 201 and 202 have the same rotation axis as that of the output-side rotator 12, can rotate together with the output-side rotator 12, and can rotate relative to the output-side rotator 12. It is.

In the first and second inertia rings 201, 202,

holes

201a, 202a penetrating in the axial direction are formed. And the 1st inertia ring 201 and the 2nd inertia ring 202 are being fixed by the rivet 24 which penetrates those

holes

201a and 202a. Therefore, the first inertia ring 201 cannot move in the axial direction, the radial direction, and the rotation direction with respect to the second inertia ring 202.

<Output-side rotator 12>
The output-side rotator 12 is formed in a disc shape, and the inner peripheral portion is connected to the output hub 5 as described above. On the outer peripheral portion of the output-side rotator 12, four protrusions 121 that further protrude on the outer peripheral side and have a predetermined width in the circumferential direction are formed. The protrusion 121 has

guide support portions

121a and 121b on both end faces in the circumferential direction, and further has an opening 121c with a predetermined width at the center in the circumferential direction. The opening 121c is formed so as to open to the outer peripheral side and has a predetermined depth.

<Centrifuge 21 and movement restriction unit>
The centrifuge 21 has a first member 211 and a second member 212 whose longitudinal ends are connected by four screw members. The first and

second members

211 and 212 have the same shape. The first and

second members

211 and 212 sandwich the protrusion 121 of the output-side rotator 12 on the inner peripheral side of the rivet 24 between the axial directions of the first inertia ring 201 and the second inertia ring 202. Is arranged. The centrifuge 21 rotates with the output-side rotator 12 and is movable in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 12.

More specifically, the centrifuge 21 is formed to extend in the rotation direction. The first member 211 and the second member 212 constituting the centrifuge 21 are, as shown by the hatched lines in FIG. 5, connected portions C1 to C4 formed by four screw members formed at both ends in the longitudinal direction. Except for the central portion C5 in the longitudinal direction, a gap is provided in the axial direction. This gap constitutes a hole into which the protruding portion 121 of the output side rotating body 12 is inserted. In other words, the first member 211 and the second member 212 constituting the centrifuge 21 are composed of connecting portions C1 to C4 formed by four screw members formed at both ends in the longitudinal direction, and a central portion C5 in the longitudinal direction. , Are in close contact.

In the gap between both ends of the first member 211 and the second member 212 (the gap in the axial direction of both members 211 and 212), one first guide roller 26a and second guide roller 26b (guide portion), Both ends of the protrusion 121 of the output side rotating body 12 are arranged. The first and

second guide rollers

26a and 26b are rotatably mounted via bushes 28 around pins 27 supported at both ends of the first and

second members

211 and 212. The outer peripheral surface of the first guide roller 26 a is in contact with one guide support portion (side surface) 121 a of the protrusion 121 and can roll, and the outer peripheral surface of the second roller 26 b is the other guide support of the protrusion 121. It is possible to roll in contact with the portion (side surface) 121b.

The central portion of the centrifuge 21 is formed with a piston portion 21a (a region C5 where the first member 211 and the second member 212 shown in FIG. 5 are in close contact with each other) having a predetermined length from the upper end surface to the inner peripheral side. . As described above, the piston portion 21a is formed such that the first member 211 and the second member 212 are in close contact with each other without a gap. The piston portion 21a is inserted into the opening 121c of the projection 121 so as to be movable in the radial direction through a predetermined gap.

With the configuration as described above, the hydraulic oil can be accumulated by the opening 121c of the protrusion 121 and the hole portion (the gap between the first member 211 and the second member 212) in which the protrusion 121 is inserted. A fluid containing portion is formed. The gap between the piston portion 21a and the fluid storage portion functions as an oil passage through which the working oil flows, that is, an orifice Or in which a cross-sectional area through which the working oil passes is narrowed. When the centrifuge 21 moves in the radial direction, the hydraulic oil accommodated in the fluid accommodating portion passes through the orifice Or, so that resistance when the centrifuge 21 moves is provided. For this reason, the moving speed decreases in the radial direction of the centrifuge 21. That is, the movement restricting portion that restricts the moving speed in the radial direction of the centrifuge 21 is configured by a member such as the centrifuge 21 that covers the piston portion 21a, the opening 121c, and the opening 121c.

The first and

second members

211 and 212 of the centrifuge 21 are formed in an arc shape in which the outer

peripheral surfaces

211a and 212a are recessed toward the inner peripheral side, and as will be described later, these outer

peripheral surfaces

211a and 212a, 212 a functions as the cam 31.

<Cam mechanism 22>
The cam mechanism 22 includes a cylindrical roller 30 as a cam follower and cams 31 that are outer

peripheral surfaces

211 a and 212 a of the first and

second members

211 and 212. The roller 30 is fitted on the outer periphery of the trunk portion of the rivet 24. That is, the roller 30 is supported by the rivet 24. The roller 30 is preferably mounted so as to be rotatable with respect to the rivet 24, but may not be rotatable. The cam 31 is an arc-shaped surface with which the roller 30 abuts. When the output side rotating body 12 and the first and second inertia rings 201 and 202 are relatively rotated within a predetermined angular range, the roller 30 It moves along the cam 31.

As will be described in detail later, when a rotational phase difference is generated between the output-side rotating body 12 and the first and second inertia rings 201 and 202 due to contact between the roller 30 and the cam 31, it occurs in the centrifuge 21. The centrifugal force is converted into a circumferential force that reduces the rotational phase difference.

[Operation of cam mechanism 22]
The operation of the cam mechanism 22 (torque fluctuation suppression) will be described with reference to FIGS. In the following description, the first and second inertia rings 201 and 202 may be simply referred to as “inertia ring 20”.

When the lockup is on, the torque transmitted to the front cover 2 is transmitted to the output side rotator 12 via the input side rotator 11 and the damper 13.

When there is no torque fluctuation during torque transmission, the output side rotating body 12 and the inertia ring 20 rotate in the state shown in FIG. In this state, the roller 30 of the cam mechanism 22 is in contact with the innermost position (the center position in the circumferential direction) of the cam 31, and the rotational phase difference between the output-side rotating body 12 and the inertia ring 20 is “0”. It is.

As described above, the relative displacement amount in the rotation direction between the output-side rotator 12 and the inertia ring 20 is referred to as “rotational phase difference”. In FIG. 2, FIG. 6, and FIG. The deviation between the center position of the centrifuge 21 and the cam 31 in the circumferential direction and the center position of the roller 30 is shown.

Here, if torque fluctuation is present during torque transmission, a rotational phase difference ± θ is generated between the output-side rotating body 12 and the inertia ring 20 as shown in FIGS. FIG. 6 shows a case where a rotational phase difference + θ occurs on the + R side, and FIG. 7 shows a case where a rotational phase difference −θ occurs on the −R side.

As shown in FIG. 6, when a rotational phase difference + θ occurs between the output-side rotator 12 and the inertia ring 20, the roller 30 of the cam mechanism 22 moves along the cam 31 relatively to the left side in FIG. 6. Move to. At this time, since centrifugal force is acting on the centrifuge 21, the reaction force received from the roller 30 by the cam 31 formed on the centrifuge 21 is the direction and magnitude of P0 in FIG. The reaction force P0 generates a first component force P1 in the circumferential direction and a second component force P2 in a direction that moves the centrifuge 21 toward the inner periphery.

The first component force P1 is a force that moves the output side rotating body 12 to the left in FIG. 6 via the cam mechanism 22 and the centrifuge 21. That is, a force in the direction of reducing the rotational phase difference between the output side rotating body 12 and the inertia ring 20 acts on the output side rotating body 12. Moreover, the centrifuge 21 is moved to the inner peripheral side against the centrifugal force by the second component force P2.

FIG. 7 shows a case where a rotational phase difference −θ is generated between the output-side rotator 12 and the inertia ring 20, and the moving direction of the roller 30 of the cam mechanism 22, the reaction force P0, and the first component force P1. The operation of the cam mechanism 22 is the same except that the direction of the second component force P2 is different from that in FIG.

As described above, when a rotational phase difference is generated between the output-side rotating body 12 and the inertia ring 20 due to torque fluctuation, the output-side rotating body 12 is caused by the centrifugal force acting on the centrifuge 21 and the action of the cam mechanism 22. , A force (first component force P1) in a direction to reduce the rotational phase difference between the two is received. This force suppresses torque fluctuations.

The force that suppresses the above torque fluctuations changes depending on the centrifugal force, that is, the rotational speed of the output side rotating body 12, and also changes depending on the rotational phase difference and the shape of the cam 31. Therefore, by setting the shape of the cam 31 as appropriate, the characteristics of the torque fluctuation suppressing device 14 can be optimized according to engine specifications and the like.

For example, the shape of the cam 31 can be made such that the first component force P1 changes linearly according to the rotational phase difference in the state where the same centrifugal force is acting. In addition, the shape of the cam 31 can be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

[Example of characteristics]
FIG. 8 is a diagram illustrating an example of torque fluctuation suppression characteristics. The horizontal axis represents the rotational speed, and the vertical axis represents the torque fluctuation (rotational speed fluctuation). The characteristic Q1 is a case where a device for suppressing torque fluctuation is not provided, the characteristic Q2 is a case where a conventional dynamic damper device is provided, and the characteristic Q3 is a case where the torque fluctuation suppressing device 14 of the present embodiment is provided. Show.

As is apparent from FIG. 8, in the device (characteristic Q2) provided with the conventional dynamic damper device, torque fluctuation can be suppressed only in a specific rotational speed range. On the other hand, in the present embodiment (characteristic Q3), torque fluctuation can be suppressed in all the rotational speed ranges.

[Operation of centrifuge 21]
For example, as shown in FIG. 6, when a rotational phase difference is generated between the output-side rotator 12 and the inertia ring 20, the centrifuge 21 has a force P 0 from the inertia ring 20 at the contact C 1 with the roller 30. Works. With this force P0, the first guide roller 26a attached to the centrifuge 21 and one side surface 121a of the projection 121 come into contact with each other at the contact C2, and the second guide roller 26b and the other side surface 121b of the projection 121 are in contact with each other. Abuts at the contact C3. That is, as shown in FIG. 6, when a rotational phase difference of + θ occurs between the output-side rotator 12 and the inertia ring 20, the force acts on the contact point C3 with the center of gravity G of the centrifuge 21 in between. A force acts on at least the contact points C1 and C2 on both sides thereof. In this case, with the contact C2 as a fulcrum, a moment acts clockwise on the centrifuge 21 due to the centrifugal force W acting on the center of gravity G, and a counterclockwise moment acts on the contact C1 due to the force P0. For this reason, a large rotational moment does not act on the centrifuge 21 only on one side. Therefore, the centrifuge 21 can be prevented from tilting, and the centrifuge 21 can be smoothly moved in the radial direction only by the two

guide rollers

26a and 26b.

[Movement restriction of centrifuge 21]
As described above, the centrifuge 21 moves in the radial direction and suppresses torque fluctuation. Here, during operation, hydraulic fluid is accumulated in the fluid storage portion formed by the opening 121c of the output side rotating body 12 and the like. In such a state, when the centrifuge 21 moves inward in the radial direction, the hydraulic oil stored in the fluid storage portion is discharged to the outside through the orifice Or. When the hydraulic oil passes through the orifice Or, resistance is applied, so that the moving speed of the centrifuge 21 can be suppressed.

For example, when the engine is stopped and the rotation of the output-side rotator 12 is stopped, the centrifuge 21 located above the plurality of centrifuges 21 falls downward. At this time, since the moving speed of the centrifuge 21 is suppressed by the hydraulic oil passing through the orifice Or as described above, the striking when the inner peripheral surface of the piston portion 21a of the centrifuge 21 collides with the bottom surface of the opening 121c. The sound can be suppressed.

Further, depending on the setting of the orifice Or, or by appropriately setting the length of the piston portion 21a toward the inner peripheral side and the depth of the opening 121c, the rotational phase difference between the inertia ring 20 and the output-side rotator 12 is set to a predetermined value. The angle can be regulated. That is, a stopper mechanism can be realized. Furthermore, even if a stopper mechanism due to the collision of the members is provided separately, the hitting sound at the time of the collision of the members can be suppressed.

-Second Embodiment-
FIG. 9 shows a part of the torque fluctuation suppressing device according to the second embodiment of the present invention, and corresponds to FIG. 2 of the first embodiment. FIG. 10 is a view seen from the direction B in FIG. FIG. 9 shows the inertia ring removed from one side (front side in FIG. 9).

The torque fluctuation suppressing device 140 of the second embodiment is basically the same as that of the first embodiment, but mainly the shape of the output-side rotator, the configuration for supporting the centrifuge, and the movement restricting portion. The configuration is different.

As shown in FIGS. 9 and 10, inertia rings 201 and 202 constituting the mass body 20 are the same as those in the first embodiment. That is, the first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape, and are disposed so as to sandwich the output-side rotating body 120 and the centrifuge 210.

Similarly to the first embodiment, the first and second inertia rings 201, 202 are fixed by the rivet 24, and the first inertia ring 201 is axially and radially oriented with respect to the second inertia ring 202. And immovable in the rotational direction.

A recess 120a that opens to the outer peripheral side is formed on the outer peripheral surface of the output-side rotator 120. In addition, a protrusion 120b that protrudes from the bottom surface of the recess 120a by a predetermined height on the outer peripheral side is formed at the center in the circumferential direction of the recess 120a.

The centrifuge 210 is disposed in the recess 120a of the output-side rotator 120, and can be moved in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 120. The centrifuge 210 has

grooves

210a and 210b at both ends in the circumferential direction. The width of the

grooves

210a and 210b is larger than the thickness of the output-side rotator 120, and the output-side rotator 120 is inserted into a part of the

grooves

210a and 210b.

Further, a hole 210c that is recessed toward the outer peripheral side is formed on the inner peripheral surface of the central portion in the circumferential direction (longitudinal direction) of the centrifuge 210. In the hole 210c, the protrusion 120b of the output side rotating body 120 is inserted through a predetermined gap. That is, the hole 210c functions as a fluid storage unit capable of storing hydraulic oil, and the gap between the hole 210c and the protrusion 120b is an oil passage through which hydraulic oil flows, as in the first embodiment, that is, It functions as an orifice Or in which the cross-sectional area of the flow path through which the hydraulic oil passes is reduced.

The outer peripheral surface 210d of the centrifuge 210 is formed in an arc shape that is recessed toward the inner peripheral side, and functions as the cam 31 as in the first embodiment.

Two

rollers

26a and 26b are disposed in the

grooves

210a and 210b at both ends of the centrifuge 210, respectively. The configuration of each

roller

26a, 26b is the same as in the first embodiment. Each of the

rollers

26a and 26b can be brought into contact with the side surface of the recess 120a to roll.

The cam mechanism 220 is the same as that of the first embodiment, and includes a cylindrical roller 30 as a cam follower and a cam 31 formed on the outer peripheral surface 210d of the centrifuge 210. Further, the operation of the cam mechanism 220 is the same as that in the first embodiment. When torque fluctuation occurs, the rotational position between the output side rotating body 120 and the first and second inertia rings 201 and 202 is increased. A phase difference is generated, and torque fluctuation is suppressed by the action of the cam mechanism 220.

Also, the configuration of the movement restricting unit that restricts the moving speed of the centrifuge 210 is basically the same as that of the first embodiment. Specifically, when a rotational phase difference occurs between the output-side rotating body 120 and the inertia rings 201 and 202, the centrifuge 210 moves radially inward by the operation of the cam mechanism 220. Due to the movement of the centrifuge 210, the hydraulic oil stored in the hole 210c is discharged through the orifice Or. At this time, the moving speed of the centrifuge 210 is suppressed by the resistance of the hydraulic oil passing through the orifice Or.

[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, the inertia ring is constituted by a continuous annular member, but a plurality of divided inertia bodies may be arranged in the circumferential direction. In this case, in order to hold a plurality of inertia bodies, it is necessary to provide a holding member such as an annular holding ring on the outer peripheral side of the inertia body.

(B) In the above-described embodiment, the guide roller is disposed as the guide portion, but another member that reduces friction such as a resin race or a sheet may be disposed.

(C) In the above embodiment, the gap is used as the oil passage constituting the movement restricting portion, but other configurations may be adopted. For example, in the first embodiment, a hole penetrating in the radial direction may be formed in the piston portion 21a of the centrifuge 21.

[Application example]
When the torque fluctuation suppressing device as described above is applied to a torque converter or another power transmission device, various arrangements are possible. Below, a specific application example is demonstrated using the schematic diagram of a torque converter or another power transmission device.

(1) FIG. 11 is a diagram schematically showing a torque converter, which includes an input-side rotating body 41, an output-side rotating body 42, and a damper provided between the

rotating bodies

41 and 42. 43. The input side rotating body 41 includes members such as a front cover, a drive plate, and a piston. The output side rotating body 42 includes a driven plate and a turbine hub. The damper 43 includes a plurality of torsion springs.

In the example shown in FIG. 11, a centrifuge is provided in any of the rotating members that constitute the input-side rotator 41, and a cam mechanism 44 that operates using centrifugal force acting on the centrifuge is provided. It has been. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

(2) The torque converter shown in FIG. 12 is provided with a centrifuge in any of the rotating members constituting the output-side rotator 42, and is a cam mechanism that operates by utilizing the centrifugal force acting on the centrifuge. 44 is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

(3) The torque converter shown in FIG. 13 has another damper 45 and an intermediate member 46 provided between the two

dampers

43, 45 in addition to the configurations shown in FIGS. is doing. The intermediate member 46 is relatively rotatable with the input side rotating body 41 and the output side rotating body 42, and causes the two

dampers

43 and 45 to act in series.

In the example shown in FIG. 13, the intermediate member 46 is provided with a centrifuge, and a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

(4) The torque converter shown in FIG. 14 has a float member 47. The float member 47 is a member for supporting the torsion spring constituting the damper 43, and is formed, for example, in an annular shape so as to cover the outer periphery and at least one side surface of the plurality of torsion springs. The float member 47 is relatively rotatable with the input-side rotator 41 and the output-side rotator 42, and rotates around the damper 43 by friction with the plurality of torsion springs of the damper 43. That is, the float member 47 also rotates.

In the example shown in FIG. 14, the float member 47 is provided with a centrifuge 48, and a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge 48 is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

(5) FIG. 15 is a schematic diagram of a power transmission device having a flywheel 50 having two

inertia bodies

51 and 52 and a clutch device 54. In other words, the flywheel 50 disposed between the engine and the clutch device 54 includes a first inertial body 51, a second inertial body 52 disposed so as to be rotatable relative to the first inertial body 51, and two inertial bodies. And a damper 53 disposed between 51 and 52. The second inertia body 52 also includes a clutch cover that constitutes the clutch device 54.

In the example shown in FIG. 15, a centrifuge is provided in any of the rotating members that constitute the second inertial body 52, and a cam mechanism 55 that operates using a centrifugal force acting on the centrifuge is provided. ing. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

(6) FIG. 16 is an example in which a centrifuge is provided in the first inertial body 51 in the same power transmission device as in FIG. A cam mechanism 55 that operates using centrifugal force acting on the centrifuge is provided. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

(7) In addition to the configuration shown in FIGS. 15 and 16, the power transmission device shown in FIG. 17 includes another damper 56 and an intermediate member 57 provided between the two

dampers

53, 56. Have. The intermediate member 57 is rotatable relative to the first inertial body 51 and the second inertial body 52.

In the example shown in FIG. 17, the intermediate member 57 is provided with a centrifuge 58, and a cam mechanism 55 that operates using a centrifugal force acting on the centrifuge 58 is provided. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

(8) FIG. 18 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel. The first inertia body 61 in FIG. 18 includes one flywheel and a clutch cover of the clutch device 62. In this example, a centrifuge is provided in any of the rotating members constituting the first inertial body 61, and a cam mechanism 64 that operates by utilizing a centrifugal force acting on the centrifuge is provided. About the cam mechanism 64, the structure similar to the structure shown by the said each embodiment is applicable.

(9) FIG. 19 is an example in which a centrifuge 65 is provided on the output side of the clutch device 62 in the same power transmission device as FIG. A cam mechanism 64 that operates by utilizing the centrifugal force acting on the centrifuge 65 is provided. About the cam mechanism 64, the structure similar to the structure shown by the said each embodiment is applicable.

(10) Although not shown in the drawings, the torque fluctuation suppressing device of the present invention may be disposed on any of the rotating members constituting the transmission, and further, the shaft (propeller shaft or drive) on the output side of the transmission (Shaft).

(11) As another application example, the torque fluctuation suppressing device of the present invention may be further applied to a conventionally known dynamic damper device or a power transmission device provided with a pendulum type damper device.

DESCRIPTION OF SYMBOLS 1 Torque converter 11 Input side rotary body 12,120 Output side rotary body 121 Protrusion part 121c Opening part 14,140 Torque fluctuation suppression apparatus 20,201,202 Inertia ring (mass body)
21, 210 Centrifuge

21a Piston portion

210c Centrifuge hole 211 First member 212

Second member

22, 220

Cam mechanism

26a, 26b Guide roller (guide portion)
30 Kolo (Cam Follower)
31 Cam Or Orifice (oil passage, gap)

Claims

A torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input,
A mass body that is arranged side by side with the rotating body, is rotatable with the rotating body, and is relatively rotatable with respect to the rotating body;
A centrifuge supported by the rotating body and arranged to be movable in the radial direction under centrifugal force,
Centrifugal force acting on the centrifuge having a cam provided on one of the centrifuge and the mass body and a cam follower provided on the other of the centrifuge and the mass body and moving along the cam In response, when a relative displacement in the rotational direction occurs between the rotating body and the mass body, the cam mechanism converts the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced.
A movement restricting section that has an oil passage through which viscous fluid can flow along with the movement of the centrifuge in the radial direction and regulates the moving speed of the centrifuge inward in the radial direction;
Torque fluctuation suppressing device comprising:
The rotating body has a protruding portion that protrudes radially outward at an outer peripheral portion, the protruding portion opens in the outer peripheral direction and has an opening portion of a predetermined depth on the inner peripheral side,
The centrifuge has a hole portion into which the protrusion is inserted and a piston portion to be inserted into the opening.
The torque fluctuation suppressing device according to claim 1.
The torque fluctuation suppressing device according to claim 2, wherein the oil passage is a gap around the piston portion inserted into the opening.
A fluid accommodating portion capable of accommodating a viscous fluid is formed by the opening of the rotating body and the hole of the centrifuge into which the protrusion of the rotating body is inserted.
The torque fluctuation suppressing device according to claim 2 or 3.
The centrifuge is formed to extend in the rotation direction, and has guide portions formed at both ends in the rotation direction.
The guide portion is supported by a circumferential end surface of the protrusion of the rotating body,
The torque fluctuation suppressing device according to any one of claims 2 to 4.
The cam is provided on the centrifuge;
The cam follower is provided on the mass body,
When relative displacement in the rotational direction occurs between the rotating body and the mass body, the guide portion of the centrifuge is positioned opposite to the contact point of the cam and the cam follower across the center of gravity of the centrifuge. In contact with the circumferential end surface of the protrusion,
The torque fluctuation suppressing device according to claim 5.
The torque variation suppression according to claim 6, wherein the guide portion is a pair of rollers that are rotatably supported at both ends of the centrifuge in the rotation direction and roll on a circumferential end surface of the protrusion. apparatus.
The rotating body has a recess recessed on the inner peripheral side on the outer peripheral surface,
The centrifuge is housed in the recess,
The torque fluctuation suppressing device according to claim 1.
The centrifuge has a hole recessed from the inner peripheral surface to the outer peripheral side,
The rotating body has a protrusion inserted into the hole on the bottom surface of the recess.
The torque fluctuation suppressing device according to claim 8.
A viscous fluid can be accommodated in the hole of the centrifuge,
The oil passage is a gap around the protrusion of the rotating body inserted into the hole.
The torque fluctuation suppressing device according to claim 9.
The mass body includes a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween, and a pin that connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. Have
The centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin.
The cam follower is a cylindrical roller having a hole through which the pin penetrates in the axial direction.
The cam is formed on the centrifuge and abuts on the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body. ,
The torque fluctuation suppressing device according to any one of claims 1 to 10.
A torque converter having a turbine disposed between the engine and the transmission and coupled to the transmission;
An input-side rotating body to which torque from the engine is input;
An output-side rotating body that outputs torque to the transmission;
A damper disposed between the input-side rotor and the turbine;
A torque fluctuation suppressing device according to any one of claims 1 to 11,
Torque converter with
A first inertial body that rotates about a rotation axis; a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body; and the first inertial body and the second inertial body. A flywheel having a damper disposed therebetween,
A clutch device provided in the second inertial body of the flywheel;
A torque fluctuation suppressing device according to any one of claims 1 to 11,
Power transmission device with