阅读说明：本技术 扭矩波动抑制装置及扭矩转换器 (Torque ripple suppression device and torque converter ) 是由 冨田雄亮 冈町悠介 于 2020-03-12 设计创作，主要内容包括：一种扭矩波动抑制装置及扭矩转换器,能够减少零件件数。扭矩波动抑制装置(10)具备输入部件(2)、弹性部件(6)、质量体(3)及离心件(51)。输入部件(2)具有在轴方向上排列的一对输入板(22)。输入部件(2)配置为能够旋转。弹性部件(6)被一对输入板(22)保持。质量体(3)配置为能够与输入部件(2)一起旋转,且与输入部件(2)相对旋转。离心件(51)配置为受到由输入部件(2)的旋转导致的离心力而能够在径向方向上移动。另外,离心件配置于一对输入板(22)间。(A torque ripple suppressing device and a torque converter are provided, which can reduce the number of parts. A torque ripple suppression device (10) is provided with an input member (2), an elastic member (6), a mass body (3), and a centrifugal member (51). The input member (2) has a pair of input plates (22) arranged in the axial direction. The input member (2) is configured to be rotatable. The elastic member (6) is held by a pair of input plates (22). The mass body (3) is configured to be rotatable together with the input member (2) and to rotate relative to the input member (2). The centrifugal member (51) is configured to be movable in a radial direction by a centrifugal force caused by rotation of the input member (2). The centrifugal element is disposed between the pair of input plates (22).)

1. A torque ripple suppression device is characterized by comprising:

an input member configured to be rotatable and having a pair of input plates arranged in an axial direction;

an elastic member held by the pair of input plates;

a mass body configured to be rotatable together with the input member and to rotate relative to the input member; and

and a centrifugal member disposed between the pair of input plates, the centrifugal member being movable in a radial direction by a centrifugal force generated by rotation of the input member.

2. The torque ripple suppressing device according to claim 1,

the input member further includes a plurality of guide members that are disposed between the pair of input plates and guide the centrifugal member.

3. The torque fluctuation suppression device according to claim 1 or 2,

the pair of input plates are disposed at intervals on the outer peripheral portion and abut against each other on the inner peripheral portion.

4. The torque fluctuation suppression device according to any one of claims 1 to 3,

the torque ripple suppression device further includes a cam mechanism that receives a centrifugal force acting on the centrifugal member and converts the centrifugal force into a circumferential force in a direction in which a torsion angle between the input member and the mass body is reduced.

5. A torque converter is characterized by comprising:

a torque converter body having a pump impeller, a turbine, and a stator; and

the torque ripple suppressing device of any one of claims 1 to 4.

Technical Field

The invention relates to a torque ripple suppression device.

Background

The torque ripple suppression device includes an input member and an inertia member. For example, a vibration reduction device described in patent document 1 includes a disc member and a mass body attached to an outer peripheral portion of the disc member. Torque from the lockup clutch is input to the disc member via the damper spring. The damping spring is used to reduce vibration caused by torque fluctuation at the time of locking.

Disclosure of Invention

Technical problem to be solved by the invention

In the torque ripple suppression device as described above, it is desirable to reduce the number of parts. Therefore, an object of the present invention is to provide a torque ripple suppression device and a torque converter that can reduce the number of components.

Means for solving the technical problem

A torque ripple suppression device according to a first aspect of the present invention includes an input member, an elastic member, a mass body, and a centrifugal member. The input unit has a pair of input plates arranged in an axial direction. The input member is configured to be rotatable. The elastic member is held by the pair of input plates. The mass body is configured to be rotatable together with the input member and to rotate relative to the input member. The centrifugal member is configured to be movable in a radial direction by a centrifugal force caused by rotation of the input member. In addition, the centrifugal member is disposed between the pair of input plates.

According to this structure, the centrifugal member is disposed between the pair of input plates. In this way, the centrifugal member can be supported in the axial direction by the pair of input plates that hold the elastic member. That is, the pair of input plates holding the elastic member also serve as parts for supporting the axial direction of the centrifugal member, and therefore the number of parts can be reduced.

Preferably, the input member further includes a plurality of guide members that are disposed between the pair of input plates and guide the centrifugal piece.

Preferably, the pair of input plates are disposed at intervals on the outer peripheral portion and abut against each other on the inner peripheral portion.

Preferably, the torque ripple suppression device is further provided with a cam mechanism. The cam mechanism receives a centrifugal force acting on the centrifugal member, and converts the centrifugal force into a circumferential force in a direction in which a torsion angle between the input member and the mass body is reduced.

A torque converter according to a second aspect of the present invention includes a torque converter main body and any one of the torque ripple reducing devices described above. The torque converter body has a pump impeller, a turbine runner, and a stator.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, it is possible to provide a torque ripple suppression device and a torque converter that can reduce the number of components.

Drawings

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

Fig. 2 is a front view of the torque ripple restraining device.

Fig. 3 is a perspective view of the torque ripple suppression device.

Fig. 4 is a perspective view of the torque ripple suppression device.

Fig. 5 is a sectional view of the torque ripple suppressing device.

Fig. 6 is a perspective view of the torque ripple suppression device.

Fig. 7 is an enlarged view of the torque fluctuation suppression device in the twisted state (twist angle θ).

Fig. 8 is a graph showing the relationship of the rotation speed and the torque ripple.

Detailed Description

Hereinafter, a torque ripple suppression device, which is an embodiment of the rotating device according to the present invention, will be described with reference to the drawings. Fig. 1 is a schematic diagram of a case where the torque ripple suppression device according to the present embodiment is incorporated in a lockup device of a torque converter. Note that, in the following description, the shaft direction refers to a direction in which the rotation axis O of the torque ripple suppressing device extends. The circumferential direction is a circumferential direction of a circle centered on the rotation axis O, and the radial direction is a radial direction of a circle centered on the rotation axis O.

[ integral Structure ]

As shown in fig. 1, the torque converter 100 has a front cover 11, a torque converter main body 12, a lock device 13, and an output hub 14. Torque from the engine is input to the front cover 11. The torque converter body 12 includes a pump impeller 121, a turbine runner 122, and a stator 123 coupled to the front cover 11. Turbine 122 is coupled to 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 portion, a piston operated by hydraulic pressure, and the like, and can be set to a lock-on state and a lock-off state. In the lock-on state, torque input to the front cover 11 is transmitted to the output hub 14 via the lock device 13 without passing through the torque converter main body 12. On the other hand, in the lock-closed state, the torque of the input front cover 11 is transmitted to the output hub 14 via the torque converter main body 12.

The locking device 13 has the input-side rotating body 131 and the torque ripple suppression device 10.

The input-side rotating body 131 can rotate relative to the output hub 14. The input-side rotating body 131 includes a piston that is movable in the axial direction, and a friction material 132 is fixed to a side surface on the front cover 11 side. By pressing the friction material 132 against the front cover 11, torque is transmitted from the front cover 11 to the input side rotary body 131.

[ Torque fluctuation suppression device 10]

Fig. 2 is a front view of the torque ripple suppression device 10, and fig. 3 is a perspective view of the torque ripple suppression device 10. Note that in fig. 2, one (front side) inertia ring is taken out.

As shown in fig. 2 and 3, the torque ripple suppression device 10 includes an input member 2, a pair of inertia rings 3 (an example of a mass body), a plurality of inertia blocks 4, a plurality of variable stiffness mechanisms 5, and a plurality of elastic members 6.

< input part 2 >

The input member 2 is inputted with torque. Specifically, torque is input to the input member 2 from the input-side rotating body 131 via the elastic member 6. The input member 2 is configured to be rotatable. The input member 2 is disposed to face the input-side rotating body 131 in the axial direction. The input member 2 is rotatable relative to the input-side rotator 131. The input member 2 is coupled to the output hub 14. That is, the input member 2 rotates integrally with the output hub 14.

The input member 2 is formed in a ring shape. The inner peripheral portion of the input member 2 is coupled to the output hub 14. The input member 2 has a plurality of accommodating portions 21. The accommodating portion 21 is formed on the outer peripheral portion of the input member 2 and opens outward in the radial direction. The accommodating portion 21 extends in the circumferential direction.

Fig. 4 is a perspective view of the torque ripple suppression device 10, and fig. 5 is a sectional view of the torque ripple suppression device. Note that, in fig. 4, the pair of inertia rings 3, members rotating integrally therewith, and the like are taken out.

As shown in fig. 4 and 5, the input unit 2 includes a pair of input boards 22. The pair of input pads 22 are arranged in the axial direction. The pair of input plates 22 are arranged on the outer peripheral portion at intervals in the axial direction. The pair of input plates 22 hold the elastic member 6 on the inner peripheral portion. Further, the pair of input plates 22 abut against each other at the inner peripheral portion.

As shown in fig. 6, the input member 2 has a plurality of guide members 23. Guide member 23 is disposed between a pair of input boards 22. The guide member 23 guides the movement of the centrifugal piece 51 in the radial direction. Specifically, the plurality of guide members 23 are arranged at intervals in the circumferential direction. The centrifugal piece 51 is disposed between the plurality of guide members 23 in the circumferential direction. According to this configuration, the plurality of guide members 23 hold the centrifugal member 51 in the circumferential direction. The guide member 23 is, for example, a guide roller. The guide member 23 is attached to the pair of input plates 22 and can rotate. The guide member 23 rotates by the centrifugal member 51 moving in the radial direction. Thereby, the centrifugal piece 51 can be smoothly moved in the radial direction.

< inertia ring 3 >

As shown in fig. 3, the inertia ring 3 is a ring-shaped plate. Specifically, the inertia ring 3 is formed in a continuous annular shape. The outer peripheral surface of inertia ring 3 and the outer peripheral surface of input plate 22 are located at substantially the same position in the radial direction. The inertia ring 3 functions as a mass body of the torque ripple suppression device 10.

As shown in fig. 5, the pair of inertia rings 3 are disposed so as to sandwich the input member 2. The pair of inertia rings 3 is disposed on both sides of the input member 2 in the axial direction. That is, the input member 2 and the pair of inertia rings 3 are arranged in the axial direction. The inertia ring 3 has the same axis of rotation as the axis of rotation of the input member 2.

The pair of inertia rings 3 are fixed to each other by rivets 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.

The inertia ring 3 is configured to be rotatable together with the input member 2 and to be rotatable relative to the input member 2. That is, the inertia ring 3 is elastically coupled to the input member 2. Specifically, the inertia ring 3 is elastically coupled to the input member 2 via the variable stiffness mechanism 5.

< inertial mass 4 >

As shown in fig. 2 and 3, the inertia mass 4 is disposed between the pair of inertia rings 3. The inertial mass 4 extends in the circumferential direction. The dimension of the inertial mass 4 in the circumferential direction is larger than that in the radial direction. The inertial mass 4 is made of metal, for example. Note that the density of the inertia mass 4 can be set smaller than the density of the inertia ring 3. The inertia mass 4 may be sintered metal.

The inertia mass 4 is a different component from the inertia ring 3. The inertia mass 4 is mounted to the pair of inertia rings 3. That is, the inertia mass 4 rotates integrally with the pair of inertia rings 3. By mounting this type of inertia mass 4, the inertia force of the inertia ring 3 is increased. Note that the inertia mass 4 is mounted to the inertia ring 3 by a plurality of rivets 140.

The plurality of inertial masses 4 are arranged at intervals in the circumferential direction. The inertia mass 4 is accommodated in the accommodating portion 21 of the input member 2. The pair of inertia rings 3 to which the inertia mass 4 is attached rotate relative to the input member 2. Therefore, when the torsion angle between the input member 2 and the pair of inertia rings 3 reaches the threshold value θ 1, the inertia mass 4 abuts against the inner wall surface 211 of the housing portion 21. That is, the input member 2 and the inertia ring 3 do not rotate relative to each other beyond the threshold value θ 1. Note that the inner wall surface 211 of the accommodating portion 21 faces in the circumferential direction.

The inertial mass 4 is arranged on the same circumference as the centrifugal member 51. The outer circumferential surface of the inertia mass 4 and the outer circumferential surface of the inertia ring 3 are substantially the same in position in the radial direction.

< variable stiffness means 5 >

As shown in fig. 2, the variable stiffness mechanism 5 is configured to change the torsional stiffness between the input member 2 and the inertia ring 3 in accordance with the rotation speed of the input member 2 or the inertia ring 3. In the present embodiment, the variable stiffness mechanism 5 is configured to change the torsional stiffness in accordance with the rotation speed of the input member 2. Specifically, the variable stiffness mechanism 5 increases the torsional stiffness between the input member 2 and the inertia ring 3 as the rotation speed of the input member 2 increases.

The variable stiffness mechanism 5 includes a centrifugal piece 51 and a cam mechanism 52. The centrifugal member 51 is attached to the input member 2. Specifically, the centrifugal element 51 is disposed between the pair of input plates 22. The centrifugal member 51 is held in the axial direction by a pair of input plates 22. In addition, the centrifugal piece 51 is held by the plurality of guide members 23 in the circumferential direction.

The centrifugal member 51 is movable in the radial direction by the centrifugal force caused by the rotation of the input member 2. The centrifugal member 51 is disposed between the pair of input plates 22 so as to be movable in the radial direction. Further, the guide member 23 rotates by the centrifugal piece 51 moving in the radial direction. Thereby, the centrifugal piece 51 can be smoothly moved in the radial direction. Note that the centrifugal piece 51 may have a projection projecting in the axial direction. The movement of the centrifugal piece 51 toward the inside in the axial direction can be restricted by the engagement of the projection with the through hole of the input plate 22 or the like.

The centrifugal member 51 has a cam surface 511. Cam surface 511 is formed in an arc shape that is recessed inward in the radial direction in a front view (as viewed in the axial direction as shown in fig. 2). Note that the cam surface 511 is the outer peripheral surface of the centrifugal member 51. As described later, the cam surface 511 of the eccentric member 51 functions as a cam of the cam mechanism 52.

When the cam mechanism 52 receives a centrifugal force acting on the centrifugal element 51 and generates torsion (relative displacement in the circumferential direction) between the input member 2 and the inertia ring 3, the centrifugal force is converted into a circumferential force in a direction in which the torsion angle is reduced.

The cam mechanism 52 is composed of a cam follower 521 and a cam surface 511 of the eccentric member 51. Note that the cam surface 511 of the centrifugal piece 51 functions as a cam of the cam mechanism 52. The cam follower 521 is attached to the rivet 31. That is, the cam follower 521 is supported by the rivet 31. Note that the cam follower 521 is preferably assembled to be rotatable with respect to the rivet 31, but may be assembled to be non-rotatable. The cam surface 511 is a surface that abuts the cam follower 521, and has an arc shape as viewed in the axial direction. When the input member 2 and the inertia ring 3 relatively rotate within a predetermined angular range, the cam follower 521 moves along the cam surface 511.

When the cam follower 521 comes into contact with the cam surface 511 to generate a torsion angle (rotational phase difference) between the input member 2 and the inertia ring 3, the centrifugal force generated in the centrifugal piece 51 is converted into a force in the circumferential direction to reduce the torsion angle.

< elastic component >

As shown in fig. 5, the elastic member 6 is held by the pair of input pads 22. Specifically, the elastic member 6 is held by the tilt portion 221 formed by the pair of input pads 22. Elastic member 6 is exposed from window portions 222 formed in the pair of input plates 22.

The elastic member 6 expands and contracts in the circumferential direction. The elastic member 6 is a coil spring. A centrifugal piece 51 is disposed outside the elastic member 6 in the radial direction. Specifically, the variable stiffness mechanism 5 including the centrifugal piece 51 is disposed outside the elastic member 6 in the radial direction.

The elastic member 6 receives torque from the input-side rotating body 131. Torque from the input-side rotating body 131 is input to the pair of input plates 22 via the elastic member 6.

[ operation of Torque ripple suppressor ]

Next, the operation of the torque ripple suppression device 10 will be described.

When the lock is opened, the torque transmitted to the front cover 11 is transmitted to the input member 2 via the input-side rotator 131 and the elastic member 6.

In the case where there is no torque fluctuation during torque transmission, the input member 2 and the inertia ring 3 rotate in the state shown in fig. 2. In this state, the cam follower 521 of the cam mechanism 52 abuts against the radially innermost position (the circumferential central position) of the cam surface 511. In this state, the torsion angle between the input member 2 and the inertia ring 3 is substantially 0.

The torsion angle between the input member 2 and the inertia ring 3 is a deviation between the center position of the eccentric 51 and the cam surface 511 in the circumferential direction and the center position of the cam follower 521 in the circumferential direction shown in fig. 2 and 7.

As shown in fig. 7, if torque fluctuation occurs during torque transmission, a torsion angle θ is generated between the input member 2 and the inertia ring 3. Fig. 7 shows a case where the twist angle + θ is generated on the + R side.

As shown in fig. 7, when the torsion angle + θ is generated between the input member 2 and the inertia ring 3, the cam follower 521 of the cam mechanism 52 moves to the right in fig. 7 along the cam surface 511. At this time, since a centrifugal force acts on the centrifugal element 51, the reaction force received from the cam follower 521 by the cam surface 511 formed on the centrifugal element 51 becomes the direction and magnitude of P0 in fig. 7. A first component force P1 in the circumferential direction and a second component force P2 in the direction of moving the centrifugal piece 51 toward the inside in the radial direction are generated by this reaction force P0.

The first component force P1 is a force that moves the input member 2 in the right direction in fig. 7 via the cam mechanism 52 and the eccentric element 51. That is, a force in a direction in which the torsion angle θ between the input member 2 and the inertia ring 3 is reduced becomes a force acting on the input member 2. Further, the centrifugal piece 51 is moved to the inner peripheral side against the centrifugal force by the second component force P2.

Note that, when a torsion angle is generated in the reverse direction, the cam follower 521 moves along the cam surface 511 to the left side in fig. 7, and the operation principle is the same.

As described above, when a torsion angle is generated between the input member 2 and the inertia ring 3 due to torque fluctuation, the input member 2 receives a force (the first component force P1) in a direction to reduce the torsion angle between the input member 2 and the inertia ring by the centrifugal force acting on the centrifugal piece 51 and the action of the cam mechanism 52. With this force, torque fluctuations can be suppressed.

The force for suppressing the torque ripple is changed according to the centrifugal force, that is, the rotation speed of the input member 2, and is also changed according to the rotational phase difference and the shape of the cam surface 511. Therefore, by appropriately setting the shape of the cam surface 511, the characteristics of the torque ripple suppression device 10 can be set to optimally different characteristics according to the engine model and the like.

For example, in a state where the same centrifugal force acts, the shape of cam surface 511 may be a shape in which first component force P1 linearly changes according to the torsion angle. The shape of the cam surface 511 may be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

As described above, the force with which the torque ripple is suppressed by the torque ripple suppression device 10 varies depending on the rotation speed of the input member 2. Specifically, since the input member 2 rotates at a high speed when the driving source such as the engine rotates at a high speed, the centrifugal force acting on the centrifugal member 51 is large. Therefore, the torsional rigidity of the variable stiffness mechanism 5 also increases, and the torsional angle between the input member 2 and the inertia ring 3 decreases. On the other hand, since the input member 2 rotates at a low speed when the driving source such as the engine rotates at a low speed, the centrifugal force acting on the centrifugal member 51 is small. Therefore, the torsional rigidity of the variable stiffness mechanism 5 also becomes smaller, and the torsional angle between the input member 2 and the inertia ring 3 becomes larger.

[ examples of characteristics ]

Fig. 8 is a diagram showing an example of the characteristics of the torque ripple suppression device 10. The horizontal axis represents the rotational speed, and the vertical axis represents the torque ripple (rotational speed ripple). The characteristic Q1 shows a case where a device for suppressing torque ripple is not provided, the characteristic Q2 shows a case where an existing dynamic damper device without a cam mechanism is provided, and the characteristic Q3 shows a case where the torque ripple suppressing device 10 of the present embodiment is provided.

As is apparent from fig. 8, in the device provided with the dynamic damper device without the variable stiffness mechanism (characteristic Q2), the torque ripple can be suppressed only for a specific rotation speed region. On the other hand, in the present embodiment (characteristic Q3) having the variable stiffness mechanism 5, torque ripple can be suppressed in all the rotation speed regions.

[ modified examples ]

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

< modification 1 >

In the above embodiment, the inertia mass 4 is formed of a member different from the inertia ring 3, but is not limited thereto. For example, the inertia mass 4 may be formed of the same member as the inertia ring 3.

< modification 2 >

In the above embodiment, the inertia mass 4 is disposed in the housing portion 21 of the input member 2, but the present invention is not limited to this configuration. For example, the inertia mass 4 may be disposed radially outward of the outer peripheral edge of the input member 2. In this case, the input member 2 may not have the housing portion 21.

< modification 3 >

In the present embodiment, the inertia mass 4 is attached to the inertia ring 3, but the configuration of the torque ripple suppression device 10 is not limited thereto. For example, the torque ripple suppression device 10 may not have the inertia mass 4.

< modification 4 >

In the above embodiment, the elastic member 6 is disposed inside the centrifugal member 51 in the radial direction, but the structure of the torque ripple suppression device 10 is not limited thereto. For example, the elastic member 6 may be disposed outside the centrifugal member 51 in the radial direction.

< modification 5 >

In the above embodiment, the torque ripple suppression device 10 is mounted on the torque converter 100, but the torque ripple suppression device 10 may be mounted on another power transmission device such as a clutch device.

Description of the reference numerals

2 … input means; 22 … input pad; 23 … guide member; 3 … inertia ring; 5 … variable stiffness mechanism; a 51 … centrifuge; 52 … cam mechanism; 6 … an elastic member; 10 … torque ripple suppression means; 100 … torque converter; 12 … torque converter body.