阅读说明：本技术 旋转装置 (Rotating device ) 是由 北田贤司 富田雄亮 于 2020-02-18 设计创作，主要内容包括：一种使特性稳定了的旋转装置。转矩变动抑制装置(10)具备轮毂凸缘(2)、离心子(4)以及第一及第二施力部件(6a、6b)。轮毂凸缘(2)配置为能够旋转。轮毂凸缘(2)具有第一以及第二引导面(21a、21b)。离心子(4)安装在轮毂凸缘(2)上。离心子(4)受到基于轮毂凸缘(2)的旋转的离心力并能够沿着第一以及第二引导面(21a、21b)在径向上移动。第一施力部件(6a)对离心子(4)施力。第二施力部件(6b)在与第一施力部件(6a)的施力方向相反的方向上对离心子(4)施力。第一以及第二施力部件(6a、6b)使离心子(4)朝向引导面(21a、21b)旋转。(A rotating device having stabilized characteristics. A torque fluctuation suppression device (10) is provided with a hub flange (2), a centrifuge (4), and first and second urging members (6a, 6 b). The hub flange (2) is configured to be rotatable. The hub flange (2) has first and second guide surfaces (21a, 21 b). The centrifuge (4) is mounted on the hub flange (2). The centrifugal force generated by the rotation of the hub flange (2) is applied to the centrifugal force, and the centrifugal force can move in the radial direction along the first and second guide surfaces (21a, 21 b). The first force application member (6a) applies force to the ion (4). The second biasing member (6b) biases the centrifuge (4) in a direction opposite to the biasing direction of the first biasing member (6 a). The first and second biasing members (6a, 6b) rotate the centrifuge (4) toward the guide surfaces (21a, 21 b).)

1. A rotating device is characterized by comprising:

a first rotating body having a guide surface and configured to be rotatable;

a centrifugal member attached to the first rotating member, and movable in a radial direction along the guide surface by receiving a centrifugal force based on rotation of the first rotating member;

a first force application member that applies force to the centrifuge; and

a second biasing member that biases the centrifuge in a direction opposite to a biasing direction of the first biasing member,

the first and second biasing members rotate the centrifuge toward the guide surface.

2. The rotating device according to claim 1, further comprising:

a second rotating body rotatable together with the first rotating body and disposed to be rotatable relative to the first rotating body; and

and a cam mechanism that, when receiving a centrifugal force acting on the centrifuge and generating a relative displacement in a circumferential direction between the first rotating body and the second rotating body, converts the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced.

3. Rotating device according to claim 1 or 2,

the centrifuge has a guide member abutting against the guide surface.

4. Rotating device according to claim 1 or 2,

the first rotating body has a guide member constituting the guide surface.

5. The rotating device according to any one of claims 1 to 4,

the ion has:

a centrifuge body;

a first wrist extending from the centrifuge body; and

a second arm portion extending from the centrifuge body in a direction opposite to the first arm portion,

the first force application member applies a force to the first arm portion,

the second force application member applies force to the second arm portion.

6. The rotating device according to any one of claims 1 to 5,

the first urging member urges the centrifuge radially outward,

the second force application member applies a force to the centrifuge toward a radially inner side.

7. The rotating device according to claim 6, further comprising:

and a cutting mechanism for cutting off the force applied to the centrifuge by the second force application member when the centrifuge moves radially inward beyond a predetermined distance.

Technical Field

The present invention relates to a rotary device.

Background

There is known a rotation device in which a rotor rotating around a rotation axis is mounted with a centrifuge. The rotor receives a centrifugal force generated by the rotation of the rotor, and the rotor functions as the rotating device. As an example of such a rotating device, there is a torque fluctuation suppression device.

For example, the torque fluctuation suppression device described in patent document 1 suppresses torque fluctuation by centrifugal force applied to the ions. Specifically, the torque fluctuation suppression device includes: inertia ring, centrifuge, and cam mechanism. The inertia ring is rotatable relative to a hub flange for transmitting torque, and the centrifuge receives centrifugal force by rotation of the hub flange and the inertia ring. The cam mechanism includes: a cam formed on the surface of the centrifuge and a cam follower in contact with the cam.

When a circumferential offset occurs between the hub flange and the inertia ring due to torque fluctuations, the cam mechanism operates by receiving centrifugal force acting on the centrifugal element. The cam mechanism converts the centrifugal force into a circumferential force in a direction in which the offset between the hub flange and the inertia ring is reduced. The torque variation is suppressed by the circumferential force.

Disclosure of Invention

Problems to be solved by the invention

In the torque fluctuation suppression device of patent document 1, a recess that opens radially outward is formed in the outer peripheral portion of the hub flange. The recess accommodates the ion, and the ion can move in the recess in the radial direction. Of the inner wall surfaces defining the recess, the inner wall surface facing in the circumferential direction functions as a guide surface when the centrifuge moves in the radial direction. A gap is created between the guide surface and the centrifuge.

Since a gap exists between the centrifuge and the guide surface, the centrifuge tilts or moves in the circumferential direction during operation of the device. The inclination and movement of the centrifuge are changed according to the direction of the force in the circumferential direction to which the centrifuge is subjected. If the centrifuge tilts or moves in the circumferential direction, the cam profile formed on the surface of the centrifuge becomes different from a predetermined design shape. Therefore, the torque fluctuation suppression device cannot stably obtain the design characteristics.

Thus, if a gap exists between the centrifuge and the guide surface, there is a problem that the characteristics of the rotary device cannot be stably obtained. Therefore, the present invention is directed to stabilizing the characteristics of a rotating device.

Means for solving the technical problem

A rotating device according to one aspect of the present invention includes: the centrifugal force-applying device comprises a first rotating body, a centrifuge, a first force-applying component and a second force-applying component. The first rotating body has a guide surface. The first rotating body is configured to be rotatable. The centrifuge is mounted on the first rotating body. The ions are subjected to a centrifugal force based on the rotation of the first rotating body and can move in the radial direction along the guide surface. The first force application component applies force to the centrifuge. The second force application member applies a force to the centrifuge in a direction opposite to the force application direction of the first force application member. The first and second biasing members rotate the centrifuge toward the guide surface.

According to this configuration, the centrifuge is rotated toward the guide surface by the first and second biasing members. Therefore, even during the operation of the rotating device, the centrifuge is kept in contact with the guide surface, and no gap is formed between the centrifuge and the guide surface. That is, the centrifuge can maintain the same posture during operation. As a result, the characteristics of the rotating device can be stabilized. The biasing direction of the first biasing member and the biasing direction of the second biasing member are opposite to each other. Therefore, the urging forces acting on the ions by the first and second urging members are cancelled, and the influence of the urging forces of the first and second urging members on the ions can be suppressed.

Preferably, the rotating device further includes a second rotating body and a cam mechanism. The second rotating body is rotatable together with the first rotating body and is disposed to be rotatable relative to the first rotating body. The cam mechanism is subjected to centrifugal forces acting on the ions. When relative displacement in the circumferential direction occurs between the first rotating body and the second rotating body, the cam mechanism converts the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced.

In this configuration, when torque is input to the first or second rotating member, the first and second rotating members rotate. When the torque input to the first or second rotating body is not varied, there is no relative displacement in the circumferential direction between the first rotating body and the second rotating body. On the other hand, when there is a fluctuation in the input torque, the second rotating body is disposed so as to be relatively rotatable with respect to the first rotating body, and therefore, depending on the degree of the fluctuation in the torque, a relative displacement in the circumferential direction is generated between the first rotating body and the second rotating body (hereinafter, this displacement may be expressed as a "rotational phase difference").

Here, when the first and second rotating bodies rotate, the centrifuge receives a centrifugal force. When relative displacement in the circumferential direction occurs between the first rotating body and the second rotating body, the cam mechanism converts a centrifugal force acting on the centrifugal force into a circumferential force. The circumferential force acts to reduce the relative displacement between the first rotating body and the second rotating body. Torque fluctuations are suppressed by the operation of such a cam mechanism.

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

Preferably, the centrifuge has a guide member abutting against the guide surface.

Preferably, the first rotating body has a guide member constituting a guide surface.

Preferably, the centrifuge has: centrifuge main part, first wrist and second wrist. A first wrist extends from the centrifuge body. The second arm portion extends from the centrifuge main body in a direction opposite to the first arm portion. The first force application member applies force to the first arm portion. The second force application member applies force to the second arm portion.

Preferably, the first biasing member biases the centrifuge radially outward. The second biasing member biases the centrifuge radially inward.

Preferably, the rotating device further includes a cutting mechanism. The cutting mechanism cuts off the force applied to the centrifuge by the second force application member when the centrifuge moves radially inward beyond a predetermined distance. According to this configuration, when the centrifuge moves radially inward beyond the predetermined distance, the biasing force of the second biasing member to the centrifuge is cut off. Therefore, the load acting on the radial outer side of the rotor becomes relatively large, and the first rotating body and the second rotating body can be prevented from being excessively twisted.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, the characteristics of the rotating device can be stabilized.

Drawings

FIG. 1 is a schematic illustration of a torque converter.

Fig. 2 is an enlarged view of the torque fluctuation suppression device.

Fig. 3 is a view seen from an arrow a of fig. 2.

Fig. 4 is an enlarged view of the torque fluctuation suppression device in a state in which torque fluctuation is input.

Fig. 5 is a graph showing a relationship between the rotation speed and the torque variation.

Fig. 6 is an enlarged view of the torque fluctuation suppression device according to the modification.

Fig. 7 is an enlarged view showing the operation of the torque fluctuation suppression device according to the modification.

Fig. 8 is an enlarged view showing the operation of the torque fluctuation suppression device according to the modification.

Fig. 9 is an enlarged view of the torque fluctuation suppression device according to the modification.

Description of the symbols

2: a hub flange; 21 a: a first guide surface; 21 b: a second guide surface; 3: an inertia ring; 4: a centrifuge; 41: a centrifuge body; 42 a: a first wrist portion; 42 b: a second wrist portion; 43 a: a first guide roller; 43 b: a second guide roller; 5: a cam mechanism; 6 a: a first force application member; 6 b: a second force application member; 7: a cutting mechanism; 10: a torque variation suppressing device.

Detailed Description

Hereinafter, a torque fluctuation suppression device, which is an embodiment of a rotating device according to the present invention, will be described with reference to the drawings. Fig. 1 is a schematic diagram of a torque fluctuation suppression device according to the present embodiment when the torque fluctuation suppression device is mounted on a lockup device of a torque converter. In the following description, the axial direction refers to a direction in which the rotation axis O of the torque fluctuation suppression device extends. The circumferential direction is a circumferential direction of a circle having the rotation axis O as a center, and the radial direction is a radial direction of a circle having the rotation axis O as a center. The circumferential direction does not necessarily need to be completely coincident with the circumferential direction of a circle centered on the rotation axis O, and for example, fig. 2 is a concept including the left-right direction with respect to the ion. The radial direction does not necessarily coincide with the radial direction of a circle centered on the rotation axis O, and for example, fig. 2 is a concept including the vertical direction with respect to the ion.

[ integral Structure ]

As shown in fig. 1, the torque converter 100 includes: a front cover 11, a torque converter body 12, a locking device 13, and an output hub 14. Torque is input from the engine to the front cover 11. The torque converter main body 12 includes: an impeller 121, a turbine 122, and a stator (not shown) coupled to the front cover 11. The turbine 122 is coupled to the output hub 14. An input shaft (not shown) of the transmission is spline-fitted to the output hub 14.

[ locking device 13]

The lock device 13 includes: a clutch section, a piston operated by oil pressure, and the like, and can acquire a lock-on state and a lock-off state. In the lock-up open state, torque input to the front cover 11 is transmitted to the output hub 14 via the lock-up device 13 without passing through the torque converter body 12. On the other hand, in the locked closed state, the torque input to the front cover 11 is transmitted to the output hub 14 via the torque converter body 12.

The lock device 13 includes: the input-side rotating body 131, the damper 132, and the torque fluctuation suppression device 10.

The input-side rotating body 131 includes a piston that is movable in the axial direction, and a friction member 133 is fixed to a side surface on the front cover 11 side. The friction member 133 presses the front cover 11, and thereby torque is transmitted from the front cover 11 to the input-side rotating body 131.

The damper 132 is disposed between the input-side rotating body 131 and a hub flange 2 described later. The damper 132 has a plurality of torsion springs, and elastically couples the input-side rotating body 131 and the hub flange 2 in the circumferential direction. The damper 132 transmits torque from the input-side rotating body 131 to the hub flange 2, and absorbs and damps torque fluctuations.

[ Torque fluctuation suppression device 10]

Fig. 2 is a front view of the torque fluctuation suppression device 10. Fig. 2 shows the inertial ring removed on one side (near side). Fig. 3 is a view of fig. 2 viewed from a direction a. Although fig. 2 shows a part of the torque fluctuation suppression device 10, the parts shown in fig. 2 are provided at equal angular intervals at a plurality of locations (for example, four locations) in the circumferential direction as a whole. One of them will be explained below.

As shown in fig. 2 and 3, the torque fluctuation suppression device 10 includes: a hub flange 2 (an example of a first rotating body), a pair of inertia rings 3 (an example of a second rotating body), a centrifuge 4, a cam mechanism 5, a first biasing member 6a, and a second biasing member 6 b.

< hub flange 2 >

The hub flange 2 is configured to be rotatable. The hub flange 2 and the input-side rotating body 131 are arranged so as to axially face each other. The hub flange 2 is rotatable relative to the input-side rotator 131. The hub flange 2 is coupled to the output hub 14. That is, the hub flange 2 rotates integrally with the output hub 14.

The hub flange 2 is formed annularly. The inner peripheral portion of the hub flange 2 is coupled to the output hub 14. The hub flange 2 has first and second guide surfaces 21a, 21 b. The first and second guide surfaces 21a and 21b are flat surfaces facing in the circumferential direction. Specifically, the first and second guide surfaces 21a and 21b face in the left-right direction in fig. 2. The first and second guide surfaces 21a, 21b extend in the radial direction. Specifically, the first and second guide surfaces 21a and 21b extend in the vertical direction in fig. 2. Preferably, the first guide surface 21a and the second guide surface 21b extend substantially in parallel.

The hub flange 2 has a recess 22 formed in an outer peripheral portion thereof and opening radially outward. The recess 22 is formed to open radially outward and has a predetermined depth. Of the inner wall surfaces defining the recess 22, a pair of inner wall surfaces facing in the circumferential direction serve as a first guide surface 21a and a second guide surface 21 b.

The hub flange 2 has first and second mounting surfaces 23a and 23 b. The first installation surface 23a faces radially outward, and the second installation surface 23b faces radially inward.

< inertia ring 3 >

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 suppression device 10. The pair of inertia rings 3 are disposed so as to sandwich the hub flange 2. The pair of inertia rings 3 are disposed with a predetermined gap left on both sides of the hub flange 2 in the axial direction. That is, the hub flange 2 and the pair of inertia rings 3 are arranged in the axial direction. The inertia ring 3 has the same rotational axis as the hub flange 2. The inertia ring 3 is rotatable together with the hub flange 2 and relatively rotatable with respect to the hub flange 2.

A hole 31 penetrating in the axial direction is formed in the inertia ring 3. The pair of inertia rings 3 are fixed by rivets 32 that pass through these holes 31. Therefore, the pair of inertia rings 3 cannot move in the axial direction, the radial direction, and the circumferential direction relative to each other.

< centrifuge 4 >

The ion 4 has: a centrifuge body 41, a first arm 42a, and a second arm 42 b. The first and second arm portions 42a and 42b extend in the circumferential direction from the centrifuge body 41. First and second arm portions 42a and 42b extend in opposite directions to each other.

The centrifuge 4 has first and second pressure receiving surfaces 45a and 45 b. The first pressure receiving surface 45a receives the biasing force from the first biasing member 6a, and the second pressure receiving surface 45b receives the biasing force from the second biasing member 6 b. The first pressure receiving surface 45a faces radially inward, and the second pressure receiving surface 45b faces radially outward. The first pressure receiving surface 45a is formed on the first arm portion 42a, and the second pressure receiving surface 45b is formed on the second arm portion 42 b. In a state where the first biasing member 6a is not provided, the first pressure receiving surface 45a faces the first mounting surface 23 a. In a state where the second biasing member 6b is not provided, the second pressure receiving surface 45b faces the second mounting surface 23 b.

The centrifuge 4 is mounted to the hub flange 2. In detail, the centrifuge 4 is disposed in the recess 22 of the hub flange 2. The ion 4 is configured to: is movable in the radial direction within the recess 22. The centrifugal force is applied to the centrifugal force by the rotation of the hub flange 2 and the centrifugal force can move in the radial direction.

The ions 4 can move in the radial direction along the first and second guide surfaces 21a, 21 b. Specifically, the centrifuge 4 is movable in the radial direction along the first and second guide surfaces 21a and 21b via the first and second guide rollers 43a and 43 b.

The centrifuge 4 includes first and second guide rollers 43a and 43b (an example of a support member). The first and second guide rollers 43a and 43b are rotatably attached to the centrifuge body 41. The first guide roller 43a abuts on the first guide surface 21 a. The second guide roller 43b abuts on the second guide surface 21 b. By the movement of the centrifuge 4 in the radial direction, the first guide roller 43a rolls on the first guide surface 21a, and the second guide roller 43b rolls on the second guide surface 21 b. This allows the centrifuge 4 to move smoothly in the radial direction.

The centrifuge 4 has a cam surface 44. The cam surface 44 is formed in an arc shape recessed inward in the radial direction when viewed from the front (when viewed in the axial direction). The cam surface 44 is an outer peripheral surface of the centrifuge 4. As described later, the cam surface 44 of the centrifuge 4 functions as a cam of the cam mechanism 5.

< force application part >

The first and second biasing members 6a and 6b bias the centrifuge 4. Specifically, the first biasing member 6a biases the first arm portion 42a of the centrifuge 4. The second biasing member 6b biases the second arm 42b of the centrifuge 4.

The first biasing member 6a is disposed between the first mounting surface 23a and the first pressure receiving surface 45 a. The second biasing member 6b is disposed between the second mounting surface 23b and the second pressure receiving surface 45 b. The first and second biasing members 6a and 6b are, for example, coil springs. The first and second biasing members 6a and 6b are provided in a compressed state.

When the torque fluctuation suppression device 10 is stopped, the biasing force of the first biasing member 6a may be larger than the biasing force of the second biasing member 6 b. That is, the biasing force of the first biasing member 6a with respect to the centrifuge 4 is larger than the biasing force of the second biasing member 6b with respect to the centrifuge 4. Specifically, the biasing force of the first biasing member 6a is preferably larger than the biasing force of the second biasing member 6b by an amount corresponding to the weight of the centrifuge 4. In the case where the plurality of first and second biasing members 6a and 6b are provided, respectively, the total value of the biasing forces of the plurality of first biasing members 6a is preferably larger than the total value of the biasing forces of the plurality of second biasing members 6b by an amount corresponding to the weight of the centrifuge 4. The pretension of the first force application element 6a and the pretension of the second force application element 6b can also be identical to each other.

The urging direction of the first urging member 6a and the urging direction of the second urging member 6b are opposite to each other. In detail, the first urging member 6a and the second urging member 6b urge the centrifuge 4 in mutually opposite directions in the radial direction. The first biasing member 6a biases the centrifuge 4 radially outward, and the second biasing member 6b biases the centrifuge 4 radially inward. Therefore, the urging forces of the first and second urging members 6a, 6b acting on the ion 4 cancel each other in the radial direction.

The first and second biasing members 6a and 6b bias the rotor 4 so as to apply a rotational torque to the rotor 4. That is, the line of action of the biasing force of the first biasing member 6a and the line of action of the biasing force of the second biasing member 6b do not coincide with each other. In the present embodiment, the first and second biasing members 6a and 6b bias the centrifuge 4 so that the centrifuge 4 rotates counterclockwise in fig. 2.

In this way, the first and second biasing members 6a and 6b apply a rotational torque to the centrifuge 4, and the centrifuge 4 rotates. That is, the first and second biasing members 6a and 6b rotate the centrifuge 4 toward the first and second guide surfaces 21a and 21 b. As a result, the centrifuge 4 abuts the first and second guide surfaces 21a and 21b of the hub flange 2 without any gap. Specifically, the first guide roller 43a of the centrifuge 4 abuts on the first guide surface 21a without a gap. The second guide roller 43b of the centrifuge 4 abuts on the second guide surface 21b without a gap.

< cam mechanism 5 >

The cam mechanism 5 is configured to receive a centrifugal force acting on the centrifuge 4 and convert the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced when the relative displacement in the circumferential direction is generated between the hub flange 2 and the inertia ring 3.

The cam mechanism 5 is constituted by a cam follower 51 and a cam surface 44 of the centrifuge 4. The cam surface 44 of the centrifuge 4 functions as a cam of the cam mechanism 5. A cam follower 51 is mounted to the body portion of rivet 32. That is, the cam follower 51 is supported by the rivet 32. Further, the cam follower 51 is preferably mounted so as to be rotatable with respect to the rivet 32, but may be mounted so as not to be rotatable. The cam surface 44 is a surface that abuts against the cam follower 51, and is arcuate in the axial direction. When the hub flange 2 and the inertia ring 3 relatively rotate within a predetermined angular range, the cam follower 51 moves along the cam surface 44.

When a rotational phase difference is generated between the hub flange 2 and the inertia ring 3 by the contact between the cam follower 51 and the cam surface 44, a centrifugal force generated in the centrifuge 4 is converted into a circumferential force that reduces the rotational phase difference.

< stopper mechanism >

The torque fluctuation suppression device 10 further includes a stopper mechanism 8. The stopper mechanism 8 limits the relative rotational angular range of the hub flange 2 and the inertia ring 3. The stopper mechanism 8 has a stopper pin 81 and an elongated hole 82.

The retaining pin 81 is fixed to the inertia ring 3. The stopper pin 81 interconnects a pair of inertia rings 3. The long hole 82 extends in the circumferential direction. The elongated hole 82 is formed in the hub flange 2. The elongated hole 82 is disposed between adjacent recesses 22. The stopper pin 81 axially penetrates the elongated hole 82. Furthermore, the stopper pin 81 may be fixed to the hub flange 2, and the elongated hole 82 is formed in the inertia ring 3.

[ operation of Torque fluctuation suppression device ]

The operation of the torque fluctuation suppression device 10 will be described with reference to fig. 2 and 4.

When the lock is opened, the torque transmitted to the front cover 11 is transmitted to the hub flange 2 via the input-side rotator 131 and the damper 132.

When there is no torque variation during torque transmission, the hub flange 2 and the inertia ring 3 rotate in the state shown in fig. 2. In this state, the cam follower 51 of the cam mechanism 5 abuts on the radially inner side (the circumferential center position) of the cam surface 44. In this state, the rotational phase difference between the hub flange 2 and the inertia ring 3 is "0".

As described above, the amount of relative displacement in the circumferential direction between the hub flange 2 and the inertia ring 3 is referred to as a "rotational phase difference", and fig. 2 and 4 show the displacement between the center position in the circumferential direction of the ion 4 and the cam surface 44 and the center position of the cam follower 51.

Here, if there is torque fluctuation during torque transmission, a rotational phase difference θ is generated between the hub flange 2 and the inertia ring 3 as shown in fig. 4. Fig. 4 shows a case where a rotational phase difference + θ (for example, 5 degrees) is generated on the + R side.

As shown in fig. 4, when the rotational phase difference + θ is generated between the hub flange 2 and the inertia ring 3, the cam follower 51 of the cam mechanism 5 moves to the right in fig. 4 relatively along the cam surface 44. At this time, since a centrifugal force acts on the centrifuge 4, the reaction force received from the cam follower 51 on the cam surface 44 formed on the centrifuge 4 becomes the direction and magnitude of P0 in fig. 4. By this reaction force P0, a first component force P1 in the circumferential direction and a second component force P2 in the direction of moving the centrifuge 4 toward the radially inner side are generated.

Then, the first component force P1 becomes a force that moves the hub flange 2 in the right direction in fig. 4 via the cam mechanism 5 and the centrifuge 4. That is, a force in a direction in which the rotational phase difference between the hub flange 2 and the inertia ring 3 is reduced acts on the hub flange 2. Further, the centrifuge 4 moves to the inner peripheral side against the centrifugal force by the second component force P2.

When the rotational phase difference occurs in the reverse direction, the cam follower 51 moves along the cam surface 44 to the left in fig. 4, but the operation principle is the same.

As described above, when a rotational phase difference is generated between the hub flange 2 and the inertia ring 3 due to the torque variation, the hub flange 2 receives a force (the first component force P1) in a direction in which the rotational phase difference between the hub flange 2 and the inertia ring is reduced by the centrifugal force acting on the centrifuge 4 and the action of the cam mechanism 5. The torque variation is suppressed by this force.

The force for suppressing the above torque fluctuation varies depending on the centrifugal force, that is, the rotational speed of the hub flange 2, and also varies depending on the rotational phase difference and the shape of the cam surface 44. Therefore, by appropriately setting the shape of the cam surface 44, the characteristics of the torque fluctuation suppression device 10 can be optimized in accordance with the engine specification and the like.

For example, the shape of the cam surface 44 may be such that the first component force P1 linearly changes according to the rotational phase difference in a state where the same centrifugal force acts. The shape of the cam surface 44 may be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

During the operation of the cam mechanism 5 as described above, the first and second biasing members 6a and 6b apply a rotational moment to the centrifuge 4 so that the first and second guide rollers 43a and 43b of the centrifuge 4 contact the first and second guide surfaces 21a and 21b without a gap therebetween. Therefore, when the torque fluctuation suppression device 10 is operated, the centrifuge 4 moves in the radial direction while keeping a fixed posture as it is. Therefore, the characteristics (particularly, the torsional characteristics) of the torque fluctuation suppression device 10 can be designed, and the characteristics of the torque fluctuation suppression device 10 can be stabilized.

The first biasing member 6a biases the centrifuge 4 radially outward. Therefore, for example, at the time of low rotation of the torque fluctuation suppression device 10, the centrifugal force 4 can be prevented from moving radially inward by its own weight, and as a result, the centrifugal force 4 can be prevented from colliding with the hub flange 2 and generating rattling noise. The centrifuge 4 is biased radially outward by the first biasing member 6a and radially inward by the second biasing member 6 b. In this way, since the biasing force of the first biasing member 6a and the biasing force of the second biasing member 6b bias the centrifuge in opposite directions to each other, the biasing forces acting on the centrifuge 4 cancel each other out. Therefore, it is possible to suppress the performance of the torque fluctuation suppression device 10 from deteriorating while suppressing a force (applied force) other than the centrifugal force acting on the centrifuge 4.

[ examples of characteristics ]

Fig. 5 is a diagram illustrating an example of characteristics of the torque fluctuation suppression device 10. The horizontal axis represents the rotation speed, and the vertical axis represents the torque variation (rotation speed variation). The characteristic Q1 shows a case where a device for suppressing torque variation is not provided, the characteristic Q2 shows a case where a conventional dynamic damper device without a cam mechanism is provided, and the characteristic Q3 shows a case where the torque variation suppression device 10 of the present embodiment is provided.

As can be seen from fig. 5, in the device provided with the dynamic damper device without the cam mechanism (characteristic Q2), the torque variation can be suppressed only in a specific rotation speed range. On the other hand, in the present embodiment (characteristic Q3) having the cam mechanism 5, torque variation can be suppressed in all the rotation speed ranges.

[ modified examples ]

The present invention is not limited to the above-described embodiments, and various modifications and corrections can be made without departing from the scope of the present invention.

< modification 1 >

As shown in fig. 6, the torque fluctuation suppression device 10 may further include a cutting mechanism 7. The cutting mechanism 7 is configured to: when the centrifuge 4 moves radially inward beyond a predetermined distance, the second biasing member 6b cuts off the biasing force applied to the centrifuge 4.

More specifically, the cutting mechanism 7 has an abutment surface 24 formed on the hub flange 2. The contact surface 24 is arranged on an extension line of the second biasing member 6b in the biasing direction of the second biasing member 6 b. The contact surface 24 faces the second installation surface 23b in a state where the second biasing member 6b is not installed. The contact surface 24 extends substantially parallel to the second installation surface 23 b. In addition, the contact surface 24 extends substantially parallel to the second pressure receiving surface 45 b.

In a state where no torque variation is input to the torque variation suppression device 10, that is, in a state where there is no rotational phase difference between the hub flange 2 and the inertia ring 3, the abutment surface 24 is disposed radially inward of the second pressure receiving surface 45 b. Therefore, the abutment surface 24 does not abut on the second biasing member 6b, and the second pressure receiving surface 45b abuts on the second biasing member 6 b. In the normal operation of the torque fluctuation suppression device 10, the contact surface 24 is disposed radially inward of the second pressure receiving surface 45 b.

When torque fluctuation is input to the torque fluctuation suppression device 10 and the hub flange 2 and the inertia ring 3 rotate relatively, the cam follower 51 presses the ions 4 radially inward and the ions 4 move radially inward.

As shown in fig. 7, when the hub flange 2 and the inertia ring 3 are excessively twisted due to rapid acceleration or rapid deceleration, the cam follower 51 presses the ions 4 radially inward and the ions 4 move radially inward beyond a predetermined distance. When the ion 4 moves radially inward beyond a predetermined distance, the second pressure receiving surface 45b is disposed radially inward of the contact surface 24. With this arrangement, the contact surface 24 is located radially outward of the second pressure receiving surface 45b and contacts the second biasing member 6b, and the second pressure receiving surface 45b does not contact the second biasing member 6 b. Therefore, the second pressure receiving surface 45b does not receive the biasing force from the second biasing member 6 b. That is, the biasing force of the second biasing member 6b to the centrifuge 4 is cut off.

In this way, when the biasing force of the second biasing member 6b to the centrifuge 4 is cut by the cutting mechanism 7, the load acting on the centrifuge 4 in the radial direction becomes small. That is, the load (centrifugal force and the biasing force of the first biasing member 6a) acting on the radial outer side of the ion 4 is relatively increased. As a result, the hub flange 2 and the inertia ring 3 can be prevented from being excessively twisted while suppressing the movement of the rotor 4 radially inward. Therefore, the generation of the knocking sound in the stopper mechanism 8 can be prevented.

The cutting mechanism 7 may not have the abutment surface 24. For example, as shown in fig. 8, the following configuration may be adopted: when the centrifuge 4 moves radially inward beyond a predetermined distance by adjusting the free length of the second biasing member 6b, the second biasing member 6b is separated from the second pressure receiving surface 45b of the centrifuge 4. In this way, the second biasing member 6b is separated from the second pressure receiving surface 45b, and the biasing force of the second biasing member 6b to the centrifuge 4 can be cut off.

< modification 2 >

In the above embodiment, the centrifuge 4 has the guide rollers 43a and 43b, but the centrifuge 4 may not have the first and second guide rollers 43a and 43 b. In this case, for example, as shown in fig. 9, the hub flange 2 preferably has first and second guide rollers 25a and 25 b. The outer peripheral surfaces of the first and second guide rollers 25a and 25b constitute first and second guide surfaces 21a and 21 b.

< modification 3 >

In the above embodiment, the first and second guide rollers 43a and 43b are exemplified as an example of the guide member, but the guide member is not limited thereto. For example, the guide member may be another member that reduces friction between the ion 4 and the first and second guide surfaces 21a and 21b, such as a resin sheet.

< modification 4 >

In the above embodiment, the centrifuge 4 is provided on the hub flange 2, but the centrifuge 4 may be provided on the inertia ring 3. In this case, the inertia ring 3 corresponds to a first rotating body of the present invention, and the hub flange corresponds to a second rotating body of the present invention.

< modification 5 >

In the above embodiment, the first and second guide surfaces 21a and 21b are formed by the inner wall surfaces of the recess 22, but the guide surfaces are not limited to this configuration as long as they can guide the radial movement of the centrifuge 4.

< modification 6 >

In the above embodiment, the coil spring is exemplified as the first and second urging members, but the first and second urging members are not limited to the coil spring. For example, the first and second biasing members may be leaf springs or other elastic members.

< modification 7 >

In the above embodiment, the hub flange 2 is exemplified as an example of the first rotating body, but the first rotating body is not limited thereto. For example, when the torque fluctuation suppression device is attached to a torque converter as in the present embodiment, the front cover 11, the input side rotating body 131, and the like of the torque converter 100 may be used as the first rotating body.

< modification 8 >

In the above embodiment, the torque fluctuation suppression device 10 is attached to the torque converter 100, but the torque fluctuation suppression device 10 may be attached to another power transmission device such as a clutch device.