JP2022071388A - Torque fluctuation suppressing device - Google Patents

Abstract

To suppress excessive increase of a torsion angle of a torque fluctuation suppressing device.SOLUTION: A torque fluctuation suppressing device 10 is constituted to be used in the air. The torque fluctuation suppressing device 10 is constituted to suppress torque fluctuation of a motor. The torque fluctuation suppressing device 10 includes a first rotor 2, a second rotor 3, and a variable rigidity mechanism 4. The first rotor 2 is rotatably disposed. The second rotor 3 is disposed to be rotated with the first rotor 2, and relatively rotatably to the first rotor 2. The variable rigidity mechanism 4 changes torsional rigidity between the first rotor 2 and the second rotor 3 according to a rotational frequency of the first rotor 2 or the second rotor 3. The torque fluctuation suppressing device 10 is designed so that its natural frequency becomes larger than a combustion frequency of the motor.SELECTED DRAWING: Figure 3

Description

The present invention relates to a torque fluctuation suppressing device.

The torque fluctuation suppressing device is configured to suppress torque fluctuations from a prime mover such as an engine. For example, the torque fluctuation suppressing device described in Patent Document 1 changes the torsional rigidity between the hub flange and the inertia ring according to the rotation speed of the engine. Specifically, the torque fluctuation suppressing device has a variable torsional rigidity that increases as the engine speed increases.

JP-A-2017-53467

If the torque fluctuation from the prime mover is large, the torsion angle of the torque fluctuation suppressing device may become too large. For example, when a torque fluctuation suppressing device is attached to a manual mission vehicle, it is preferable that the torque fluctuation suppressing device is arranged between the prime mover and the damper device. In this case, since the torque fluctuation before being attenuated by the damper device is input to the torque fluctuation suppressing device, there may be a problem that the torsion angle becomes too large.

If the torsion angle of the torque fluctuation suppressing device becomes too large, problems such as the torque cannot be appropriately fluctuated and the centrifuge collides with the hub flange to generate a striking sound may occur. As described above, if the helix angle of the torque fluctuation suppressing device becomes too large, various problems may occur.

Therefore, an object of the present invention is to prevent the torsion angle of the torque fluctuation suppressing device from becoming too large.

The torque fluctuation suppressing device according to a certain aspect of the present invention is configured to be used in the air. The torque fluctuation suppressing device is configured to suppress the torque fluctuation of the prime mover. The torque fluctuation suppressing device includes a first rotating body, a second rotating body, and a variable rigidity mechanism. The first rotating body is rotatably arranged. The second rotating body rotates with the first rotating body and is arranged so as to be rotatable relative to the first rotating body. The variable rigidity mechanism changes the torsional rigidity between the first rotating body and the second rotating body according to the number of rotations of the first rotating body or the second rotating body. The torque fluctuation suppression device is designed so that its natural frequency is higher than the combustion frequency of the prime mover.

The torque fluctuation suppressing device described above is designed so that its natural frequency is higher than the combustion frequency of the prime mover. That is, the torque fluctuation suppressing device is designed so that the natural frequency is higher than the optimum natural frequency at a certain rotation speed. As a result, while the torque fluctuation suppressing function is lowered to some extent, it is possible to prevent the torsion angle of the torque fluctuation suppressing device from becoming too large.

Preferably, the torque fluctuation suppressing device is designed so that its natural frequency is 1.1 times or more the combustion frequency of the prime mover.

Preferably, the torque fluctuation suppressing device is designed so that its natural frequency is 1.4 times or less of the combustion frequency of the prime mover.

Preferably, the first rotating body is a flywheel attached to the crankshaft.

Preferably, the flywheel has a disc portion and a mounting portion. The disk portion is attached to the crankshaft. The mounting portion is mounted on the outer peripheral portion of the disk portion.

Preferably, the second rotating body is inertial. The inertia ring is arranged between the disc portion and the mounting portion in the axial direction. The mounting portion has a convex portion that penetrates the inertia ring and extends to the disc portion.

Preferably, the flywheel has a ring gear formed on the outer peripheral surface of the mounting portion.

Preferably, the variable stiffness mechanism has a centrifuge and a cam mechanism. The centrifuge is arranged so as to be movable in the radial direction by receiving a centrifugal force due to the rotation of the first rotating body or the second rotating body. The cam mechanism is configured to receive a centrifugal force acting on the centrifuge and convert the centrifugal force into a circumferential force in a direction in which the twist angle between the first rotating body and the second rotating body becomes smaller.

Preferably, the cam mechanism has a cam surface and a cam follower. The cam surface is formed on the centrifuge. The cam follower comes into contact with the cam surface and transmits a force between the centrifuge and the second rotating body.

Preferably, the variable stiffness mechanism is configured to increase the torsional rigidity between the first rotating body and the second rotating body as the rotation speed of the first rotating body or the second rotating body increases.

According to the present invention, it is possible to prevent the torsion angle of the torque fluctuation suppressing device from becoming too large.

The schematic which shows the power transmission path. Sectional drawing of the clutch device. The plan view of the torque fluctuation suppression device in the state where one of the inertia rings is removed. The graph which shows the relationship between the engine speed and the torsion angle of a torque fluctuation suppression device. A graph showing the relationship between the engine speed and the torque fluctuation output from the torque fluctuation suppression device. The plan view of the torque fluctuation suppression device in the state where one of the inertia rings is removed.

Hereinafter, the torque fluctuation suppressing device according to the present embodiment will be described with reference to the drawings. In the following description, the axial direction is the direction in which the rotation axis O of the torque fluctuation suppressing device extends. Further, the circumferential direction is the circumferential direction of the circle centered on the rotation axis O, and the radial direction is the radial direction of the circle centered on the rotation axis O.

[overall structure]
As shown in FIG. 1, the torque fluctuation suppressing device 10 is arranged between the engine 101 (an example of a prime mover) and the transmission 102. The transmission is, for example, a manual transmission. The torque fluctuation suppressing device 10 is arranged between the engine 101 and the damper 124. The torque fluctuation suppressing device 10 is used in the air. That is, the torque fluctuation suppressing device 10 is not arranged in the oil. The torque fluctuation suppressing device 10 is configured to suppress the torque fluctuation of the engine.

As shown in FIG. 2, the torque fluctuation suppressing device 10 is incorporated in the clutch device 100. The clutch device 100 includes a torque fluctuation suppressing device 10, a clutch cover assembly 11, and a clutch disc assembly 12.

[Torque fluctuation suppression device]
As shown in FIGS. 2 and 3, the torque fluctuation suppressing device 10 includes a flywheel 2 (an example of a first rotating body), a pair of inertia rings 3 (an example of a second rotating body), and a variable rigidity mechanism 4. are doing.

<Flywheel>
As shown in FIG. 2, the flywheel 2 is rotatably arranged. The flywheel 2 is attached to the crankshaft 103. The flywheel 2 rotates integrally with the crankshaft 103.

The flywheel 2 has a disk portion 21, a mounting portion 22, and a ring gear 23. The disk portion 21 is formed in a disk shape. The inner peripheral portion of the disk portion 21 is connected to the crankshaft 103. For example, the disk portion 21 is fixed to the crankshaft 103 by a fastening member such as a bolt. The disk portion 21 is formed with a recess 211 that opens radially outward on the outer peripheral portion. The recess 211 is formed so as to open radially outward and has a predetermined depth.

The mounting portion 22 is formed in an annular shape. The mounting portion 22 extends in the circumferential direction. The mounting portion 22 is mounted on the disk portion 21. For example, the mounting portion 22 is fixed to the disc portion 21 by a fastening member such as a rivet. The mounting portion 22 rotates integrally with the disc portion 21. The mounting portion 22 has a plurality of convex portions 221, an annular convex portion 222, and a friction surface 223.

The convex portion 221 protrudes toward the disk portion 21. The convex portions 221 are arranged at intervals in the circumferential direction. The convex portion 221 penetrates one of the inertia rings 3. The tip surface of the convex portion 221 is in contact with the disk portion 21.

The annular convex portion 222 is an annular shape extending in the circumferential direction. The annular convex portion 222 is arranged at the outer peripheral end portion of the mounting portion 22. The annular convex portion 222 projects in a direction away from the disc portion 21. That is, the annular convex portion 222 protrudes on the opposite side to the convex portion 221.

The friction surface 223 faces the transmission side. The clutch disc 121 of the clutch disc assembly 12, which will be described later, is pressed against the friction surface 223.

The ring gear 23 is provided on the outer peripheral surface of the mounting portion 22. The ring gear 23 rotates integrally with the mounting portion 22. The ring gear 23 may be configured by a member separate from the mounting portion 22, or may be configured by one member.

<Inertia ring 3>
The inertia ring 3 can rotate together with the flywheel 2 and can rotate relative to the flywheel 2. That is, the inertia ring 3 is elastically connected to the flywheel 2. The inertia ring 3 is an annular plate. Specifically, the inertia ring 3 is formed in a continuous annular shape. The inertia ring 3 functions as a mass body of the torque fluctuation suppressing device 10.

The pair of inertia rings 3 are arranged so as to sandwich the flywheel 2. Specifically, the pair of inertia rings 3 are arranged so as to sandwich the disk portion 21 of the flywheel 2. The pair of inertia rings 3 are arranged with a predetermined gap on both sides of the flywheel 2 in the axial direction. The flywheel 2 and the pair of inertia rings 3 are arranged side by side in the axial direction. One inertia ring 3 is arranged between the disk portion 21 and the mounting portion 22 in the axial direction. The inertia ring 3 has the same rotation axis as the rotation axis of the flywheel 2.

The pair of inertia rings 3 are fixed to each other by rivets 31. Therefore, the pair of inertia rings 3 are immovable with each other in the axial, radial, and circumferential directions.

<Variable rigidity mechanism 4>
As shown in FIG. 3, the variable rigidity mechanism 4 is configured to change the torsional rigidity between the flywheel 2 and the inertia ring 3 according to the rotation speed of the flywheel 2 or the inertia ring 3. In the present embodiment, the variable rigidity mechanism 4 is configured to change the torsional rigidity according to the rotation speed of the flywheel 2. Specifically, the variable stiffness mechanism 4 increases the torsional stiffness between the flywheel 2 and the inertia ring 3 as the rotation speed of the flywheel 2 increases.

The variable rigidity mechanism 4 has a centrifuge 41 and a cam mechanism 42. The centrifuge 41 is attached to the flywheel 2. Specifically, the centrifuge 41 is arranged in the recess 211 of the flywheel 2. The centrifuge 41 is arranged so as to be movable in the radial direction in the recess 211. The centrifuge 41 can move in the radial direction by receiving a centrifugal force due to the rotation of the flywheel 2.

Specifically, the centrifuge 41 has a plurality of guide rollers 411. As the centrifuge 41 moves in the radial direction, the guide roller 411 rolls on the inner wall surface of the recess 211. As a result, the centrifuge 41 can move smoothly in the radial direction.

The centrifuge 41 has a cam surface 412. The cam surface 412 is formed in an arc shape that is recessed inward in the radial direction in a front view (a state viewed along the axial direction as shown in FIG. 3). The cam surface 412 is an outer peripheral surface of the centrifuge 41. The cam surface 412 of the centrifuge 41 functions as a cam of the cam mechanism 42, as will be described later.

When the cam mechanism 42 receives a centrifugal force acting on the centrifugal force 41 and a twist (relative displacement in the circumferential direction) occurs between the flywheel 2 and the inertia ring 3, the centrifugal force causes the twist angle to become smaller. It is configured to convert to centrifugal force in the direction.

The cam mechanism 42 includes a cam follower 421 and a cam surface 412 of the centrifuge 41. The cam surface 412 of the centrifuge 41 functions as a cam of the cam mechanism 42. The cam follower 421 is attached to the body of the rivet 31. That is, the cam follower 421 is supported by the rivet 31. The cam follower 421 is preferably mounted rotatably with respect to the rivet 31, but may be mounted non-rotatably. The cam surface 412 is a surface with which the cam follower 421 abuts, and is arcuate in the axial direction. When the flywheel 2 and the inertia ring 3 rotate relative to each other within a predetermined angle range, the cam follower 421 moves along the cam surface 412.

When a helix angle (rotational phase difference) is generated between the flywheel 2 and the inertia ring 3 due to contact between the cam follower 421 and the cam surface 412, the centrifugal force generated in the centrifuge 41 reduces the helix angle. It is converted into a force in the circumferential direction.

<Natural frequency>
The torque fluctuation suppressing device 10 is designed so that the natural frequency f _VDD of the torque fluctuation suppressing device 10 is larger than the combustion frequency f _C of the engine 101. For example, the natural frequency f _VDD of the torque fluctuation suppressing device 10 is preferably 1.1 times or more the combustion frequency f _C of the engine. Further, it is preferable that the natural frequency f _VDD of the torque fluctuation suppressing device 10 is 1.4 times or less of the combustion frequency f _C of the engine 101.

The natural frequency f _VDD of the torque fluctuation suppressing device 10 is expressed by the following equation.

なお、ｋはトルク変動抑制装置１０のねじり剛性（Ｎｍ／ｒａｄ）を示し、Iはトルク変動抑制装置１０のイナーシャ量（ｋｇｍ^２）を示す。ねじり剛性は、トルク変動抑制装置１０のフライホイール２の回転数Ｎ（ｒ／ｍｉｎ）に応じて変化し、以下の式によって表される。

Note that k indicates the torsional rigidity (Nm / rad) of the torque fluctuation suppressing device 10, and I indicates the inertia amount (kgm ² ) of the torque fluctuation suppressing device 10. The torsional rigidity changes according to the rotation speed N (r / min) of the flywheel 2 of the torque fluctuation suppressing device 10, and is expressed by the following equation.

このため、トルク変動抑制装置１０の固有振動数ｆ_ＶＤＤは、以下の式（３）によって表される。

Therefore, the natural frequency f _VDD of the torque fluctuation suppressing device 10 is expressed by the following equation (3).

ここで、ねじり剛性ｋ＝ｆ（Ｎ^２）は、次の式によって表すことができる。

Here, the torsional rigidity k = f (N ² ) can be expressed by the following equation.

ここで、Rは回転軸Ｏからカムフォロア４２１の中心までの距離、ｍは遠心子４１の質量、ｒは回転軸Ｏから遠心子４１の重心までの距離、ωはフライホイール２の回転速度（ｒａｄ／ｓ）、θはＰ０の方向と分力Ｐ２の方向とがなす角度（図６参照）、αはねじり角度（図６参照）を示す。

Here, R is the distance from the rotation axis O to the center of the cam follower 421, m is the mass of the centrifuge 41, r is the distance from the rotation axis O to the center of gravity of the centrifuge 41, and ω is the rotation speed (rad) of the fly wheel 2. / S), θ indicates the angle formed by the direction of P0 and the direction of the component force P2 (see FIG. 6), and α indicates the twisting angle (see FIG. 6).

Further, the combustion frequency f _C of the engine 101 is expressed by the following equation.

なお、ｎはエンジン１０１の気筒数を示し、Ｎｅはエンジン１０１の回転数（ｒｐｍ）を示す。

Note that n indicates the number of cylinders of the engine 101, and Ne indicates the rotation speed (rpm) of the engine 101.

FIG. 4 is a graph showing the relationship between the rotation speed of the engine 101 and the twist angle of the torque fluctuation suppressing device 10. The horizontal axis shows the rotation speed of the engine 101, and the vertical axis shows the twist angle. In FIG. 4, the line A shows the characteristics when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to be the same as the combustion frequency f _C of the engine 101. Further, the line B shows the characteristics when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to 1.1 times the combustion frequency f _C of the engine 101. Further, the line C shows the characteristics when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to 1.2 times the combustion frequency f _C of the engine 101. Further, the line D shows the characteristics when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to 1.4 times the combustion frequency f _C of the engine 101. As shown in FIG. 4, the torsion angle of the torque fluctuation suppressing device 10 can be reduced by making the natural frequency f _VDD of the torque fluctuation suppressing device 10 larger than the combustion frequency f _C of the engine 101.

FIG. 5 is a graph showing the relationship between the rotation speed of the engine 101 and the torque fluctuation output from the torque fluctuation suppressing device 10. The horizontal axis shows the number of revolutions of the engine 101, and the vertical axis shows the torque fluctuation (rotational speed fluctuation). The line A shows the characteristics when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to be the same as the combustion frequency f _C of the engine 101. Further, the line B has characteristics when the natural frequency f _VDD is set to 1.2 times the combustion frequency f _C , the line C is 1.4 times, the line D is 1.5 times, and the line E is 1.6. The double and line F show the characteristics when set to 1.7 times. Further, the line G shows the characteristics when the dynamic vibration absorber is not installed.

As shown in FIG. 5, when the dynamic vibration absorber is not installed, the torque fluctuation increases when the engine speed is around 3000 rpm. On the other hand, as shown by the line A, when the natural frequency f _VDD of the torque fluctuation suppressing device 10 is set to be the same as the combustion frequency f _C , the torque fluctuation does not increase, and the torque fluctuation does not increase, and also in other regions. The torque fluctuation is smaller than when the dynamic vibration absorber is not installed.

As shown by lines B to F, even when the natural frequency f _VDD of the torque fluctuation suppression device 10 is set to 1.2 to 1.7 times the combustion frequency f _C , when the dynamic vibration absorber is not installed. In comparison, the torque fluctuation is small as a whole. On the other hand, as shown by lines D to F, when the natural frequency f _VDD of the torque fluctuation suppression device 10 is set to 1.5 times or more the combustion frequency f _C , the torque fluctuation occurs when the engine speed is around 3000 rpm. It can be seen that it is amplified. Therefore, the natural frequency f _VDD is preferably 1.4 times or less of the combustion frequency f _C.

[Operation of torque fluctuation suppression device]
The operation of the torque fluctuation suppressing device 10 will be described with reference to FIGS. 3 and 6.

The torque from the engine 101 is transmitted to the flywheel 2. In this embodiment, the torque from the engine 101 is transmitted to the flywheel 2 without going through the damper 124.

If there is no torque fluctuation during torque transmission, the flywheel 2 and inertia ring 3 rotate in the state shown in FIG. In this state, the cam follower 421 of the cam mechanism 42 abuts on the innermost position in the radial direction (center position in the circumferential direction) of the cam surface 412. Further, in this state, the helix angle between the flywheel 2 and the inertia ring 3 is substantially zero.

The helix angle between the flywheel 2 and the inertia ring 3 is the center position of the centrifuge 41 and the cam surface 412 in the circumferential direction, the center position of the cam follower 421, and the circumference in FIGS. 3 and 6. It indicates a deviation in direction.

When torque fluctuations are present during torque transmission, a helix angle α is generated between the flywheel 2 and the inertia ring 3, as shown in FIG. FIG. 6 shows a case where a helix angle + α is generated on the + R side.

As shown in FIG. 6, when a helix angle + α occurs between the flywheel 2 and the inertia ring 3, the cam follower 421 of the cam mechanism 42 moves relatively to the right side in FIG. 6 along the cam surface 412. do. At this time, since the centrifugal force acts on the centrifugal force 41, the reaction force received from the cam follower 421 by the cam surface 412 formed on the centrifugal force 41 is in the direction and magnitude of P0 in FIG. This reaction force P0 generates a first component force P1 in the circumferential direction and a second component force P2 in the direction of moving the centrifugal force 41 inward in the radial direction.

The first component force P1 is a force that moves the flywheel 2 to the right in FIG. 6 via the cam mechanism 42 and the centrifugal force 41. That is, the force in the direction of reducing the helix angle α between the flywheel 2 and the inertia ring 3 acts on the flywheel 2. Further, the centrifugal force 41 is moved to the inner peripheral side against the centrifugal force by the second component force P2.

When a helix angle occurs in the opposite direction, the cam follower 421 moves relatively to the left side of FIG. 6 along the cam surface 412, but the operating principle is the same.

As described above, when a twist angle is generated between the flywheel 2 and the inertia ring 3 due to torque fluctuation, the flywheel 2 has a twist angle of both due to the centrifugal force acting on the centrifuge 41 and the action of the cam mechanism 42. Receives a force (first component force P1) in the direction of reducing. This force suppresses torque fluctuations.

The force for suppressing the above torque fluctuation changes depending on the centrifugal force, that is, the rotation speed of the flywheel 2, and also changes depending on the rotation phase difference and the shape of the cam surface 412. Therefore, by appropriately setting the shape of the cam surface 412, the characteristics of the torque fluctuation suppressing device 10 can be made optimum characteristics according to the engine specifications and the like.

As described above, the force for suppressing the torque fluctuation by the torque fluctuation suppressing device 10 changes depending on the rotation speed of the flywheel 2. Specifically, when the engine 101 rotates at a high speed, the flywheel 2 also rotates at a high speed, so that the centrifugal force acting on the centrifuge 41 is large. Therefore, the torsional rigidity of the variable rigidity mechanism 4 also increases, and the torsional angle between the flywheel 2 and the inertia ring 3 becomes smaller. On the other hand, when the engine 101 rotates at a low speed, the flywheel 2 also has a low rotation speed, so that the centrifugal force acting on the centrifuge 41 is small. Therefore, the torsional rigidity of the variable rigidity mechanism 4 is also reduced, and the torsional angle between the flywheel 2 and the inertia ring 3 is increased.

In this way, the torsional rigidity of the variable rigidity mechanism 4 changes according to the rotation speed of the flywheel 2. When the flywheel 2 has a low rotation speed, the torsional rigidity due to the variable rigidity mechanism 4 becomes small, so that the torsional angle between the flywheel 2 and the inertia ring 3 tends to be large.

[Clutch cover assembly]
As shown in FIG. 2, the clutch cover assembly 11 includes a clutch cover 111, a pressure plate 112, and a diaphragm spring 113.

The clutch cover 111 is annular and extends in the circumferential direction. The clutch cover 111 is fixed to the mounting portion 22 of the flywheel 2. Specifically, the outer peripheral portion of the clutch cover 111 is fixed to the annular convex portion 222 of the mounting portion 22 by a fastening member such as a bolt.

The pressure plate 112 is an annular member. The pressure plate 112 is configured to press the clutch disc 121 against the flywheel 2. Specifically, the pressure plate 112 is urged to the flywheel 2 side by the diaphragm spring 113.

The diaphragm spring 113 is configured to urge the pressure plate 112 toward the flywheel 2. The pressure plate 112 presses the clutch disc 121 toward the flywheel 2 by being urged by the diaphragm spring 113.

[Clutch disc assembly]
The clutch disc assembly 12 has a clutch disc 121, an input side rotating body 122, an output side rotating body 123, and a damper 124. The clutch disc 121 is configured to frictionally engage with the flywheel 2.

The damper 124 elastically connects the input side rotating body 122 and the output side rotating body 123. The damper 124 has a plurality of coil springs. The coil springs are arranged at intervals in the circumferential direction.

[Modification example]
The present invention is not limited to the above embodiments, and various modifications or modifications can be made without departing from the scope of the present invention.

<Modification 1>
In the above embodiment, the flywheel 2 is illustrated as an example of the first rotating body, but the first rotating body is not limited to this. That is, a rotating body different from the flywheel 2 can be used as the first rotating body.

<Modification 2>
In the above embodiment, the flywheel 2 has the ring gear 23, but the present invention is not limited to this configuration. For example, a ring gear may be provided on the outer peripheral surface of the inertia ring 3. In this case, the engine 101 is started via the torque fluctuation suppressing device 10.

<Modification 3>
In the above embodiment, the torque fluctuation suppressing device 10 is attached to the clutch device 100, but the torque fluctuation suppressing device 10 can also be attached to another power transmission device such as a damper device.

2 Flywheel 21 Disc 22 Mounting 221 Convex 3 Initialing 4 Variable stiffness mechanism 41 Centrifuge 412 Cam surface 42 Cam mechanism 421 Cam follower 10 Torque fluctuation suppression device 103 Crankshaft

Claims (10)

It is a torque fluctuation suppression device used in the air to suppress torque fluctuations of the prime mover.
The first rotating body, which is rotatably arranged, and
A second rotating body that rotates with the first rotating body and is arranged so as to be relatively rotatable relative to the first rotating body.
A variable rigidity mechanism that changes the torsional rigidity between the first rotating body and the second rotating body according to the rotation speed of the first rotating body or the second rotating body.
Equipped with
The torque fluctuation suppressing device is designed so that its natural frequency is higher than the combustion frequency of the prime mover.
Torque fluctuation suppression device.
The torque fluctuation suppressing device is designed so that its natural frequency is 1.1 times or more the combustion frequency of the prime mover.
The torque fluctuation suppressing device according to claim 1.
The torque fluctuation suppressing device is designed so that its natural frequency is 1.4 times or less the combustion frequency of the prime mover.
The torque fluctuation suppressing device according to claim 1 or 2.
The first rotating body is a flywheel attached to a crankshaft.
The torque fluctuation suppressing device according to any one of claims 1 to 3.
The flywheel
The disk part attached to the crankshaft and
A mounting portion mounted on the outer peripheral portion of the disk portion and a mounting portion
Have,
The torque fluctuation suppressing device according to claim 4.
The second rotating body is an inertia ring arranged between the disk portion and the mounting portion in the axial direction.
The mounting portion has a convex portion that penetrates the inertia ring and extends to the disk portion.
The torque fluctuation suppressing device according to claim 5.
The flywheel has a ring gear formed on the outer peripheral surface of the mounting portion.
The torque fluctuation suppressing device according to claim 5 or 6.
The variable rigidity mechanism is
A centrifuge arranged so as to be movable in the radial direction by receiving a centrifugal force due to the rotation of the first rotating body or the second rotating body.
A cam mechanism configured to receive a centrifugal force acting on the centrifuge and convert the centrifugal force into a circumferential force in a direction in which the twist angle between the first rotating body and the second rotating body becomes smaller. When,
Have,
The torque fluctuation suppressing device according to any one of claims 1 to 7.
The cam mechanism is
The cam surface formed on the centrifuge and
A cam follower that comes into contact with the cam surface and transmits a force between the centrifuge and the second rotating body.
Have,
The torque fluctuation suppressing device according to claim 8.
The variable rigidity mechanism is configured to increase the torsional rigidity between the first rotating body and the second rotating body as the rotation speed of the first rotating body or the second rotating body increases. ,
The torque fluctuation suppressing device according to any one of claims 1 to 9.

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