阅读说明：本技术 摩擦联接装置 (Friction coupling device ) 是由 石川靖浩 于 2019-11-08 设计创作，主要内容包括：具有：与离合器鼓(44)可滑动地卡合的多个外径侧摩擦板(42)；与离合器毂(45)可滑动地卡合的多个内径侧摩擦板(41)；通过沿旋转轴(X)方向移动而按压外径侧摩擦板(42)及内径侧摩擦板(41)的活塞(43)；对活塞(43)施加旋转轴(X)方向的作用力的弹簧(B2)；支承弹簧(B2)的一端(B2a)的板部件(49),板部件(49)作为与离合器毂(45)可在旋转轴(X)方向滑动地卡合的锁止离合器(4)。(Comprising: a plurality of outer diameter side friction plates (42) which are slidably engaged with the clutch drum (44); a plurality of inner diameter side friction plates (41) which are slidably engaged with the clutch hub (45); a piston (43) which presses the outer diameter side friction plate (42) and the inner diameter side friction plate (41) by moving along the direction of the rotating shaft (X); a spring (B2) that applies a biasing force in the direction of the rotation axis (X) to the piston (43); the plate member (49) that supports one end (B2a) of the spring (B2) serves as a lock-up clutch (4) that is slidably engaged with the clutch hub (45) in the direction of the rotation axis (X).)

1. A friction coupling device, comprising:

a plurality of first plates slidably engaged with the outer-peripheral-side cylindrical member;

a plurality of second plates slidably engaged with the inner peripheral side tubular member;

a piston that presses the first plate and the second plate by moving in an axial direction;

an urging member that applies the axial urging force to the piston;

a plate member supporting one end of the urging member,

the plate member is slidably engaged with one of the outer peripheral side cylindrical member and the inner peripheral side cylindrical member in the axial direction.

2. Friction coupling device according to claim 1,

the other end of the biasing member is supported by a member that rotates integrally with one of the outer-peripheral-side cylindrical member and the inner-peripheral-side cylindrical member.

3. Friction coupling device according to claim 1 or 2,

the plate member is engaged with the inner peripheral side cylindrical member.

4. Friction coupling device according to any of claims 1 to 3,

the oil passing through the space on the plate member side flows into the first plate and the second plate.

5. Friction coupling device according to any of claims 1 to 4,

the friction coupling device is a lock-up clutch of a torque converter.

Technical Field

The present invention relates to a friction coupling device.

Background

In patent document 1, a rotation prevention structure is formed to prevent relative rotation between a piston and one member of a lock-up clutch by directly engaging the piston with a boss member of the lock-up clutch.

Fig. 4 is a diagram illustrating a conventional lockup clutch 100. (a) A diagram illustrating the periphery of the piston 200 of the lockup clutch 100 is shown. (b) Is a perspective view of the piston 200.

As shown in fig. 4 (a) and (b), the piston 200 includes: an annular base 210; a pressing portion 220 provided on the outer peripheral side of the base portion 210; an annular protrusion 250 protruding from the base 210 in the center line direction (the rotation axis X direction) on the inner diameter side of the pressing portion 220.

A spline Sp is formed on the outer peripheral surface of the protrusion 250. The protrusion 250 is spline-engaged with the inner periphery of the clutch hub 300 of the lockup clutch 100. This prevents relative rotation between the piston 200 and the clutch hub 300.

In the piston 200, the protrusion 250 is formed integrally with the base 210. Therefore, the piston 200 has to have a complicated shape, and the shape of the piston 200 cannot be freely selected.

Accordingly, it is required to ensure the degree of freedom in selecting the shape of the piston.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2014-74438

Disclosure of Invention

The friction coupling device of the present invention includes:

a plurality of first plates slidably engaged with the outer-peripheral-side cylindrical member;

a plurality of second plates slidably engaged with the inner peripheral side tubular member;

a piston that presses the first plate and the second plate by moving in an axial direction;

an urging member that applies the axial urging force to the piston;

a plate member supporting one end of the urging member,

the plate member is slidably engaged with one of the outer peripheral side cylindrical member and the inner peripheral side cylindrical member in the axial direction.

According to the present invention, the degree of freedom in selecting the piston shape can be ensured.

Drawings

Fig. 1 is a diagram illustrating a locking device.

Fig. 2 is a diagram illustrating the lock-up clutch.

Fig. 3 is a diagram illustrating the periphery of the piston.

Fig. 4 is a diagram illustrating a conventional piston.

Detailed Description

Hereinafter, a case where the friction engagement device of the present invention is the lock-up clutch 4 provided in the torque converter 1 will be described as an example.

Fig. 1 is a diagram illustrating a locking device 2.

Fig. 2 is a view illustrating the periphery of the lockup clutch 4, and is an enlarged view of the area a in fig. 1.

Fig. 3 is a view illustrating the periphery of the piston 43, and is an exploded perspective view of the piston 43 as viewed from the left side in fig. 1.

As shown in fig. 1, the lock-up device 2 is provided inside a front cover 11 of the torque converter 1. The lockup device 2 is composed of a damper device 3 and a lockup clutch 4.

The rotational driving force of the driving source (not shown) is transmitted to the front cover 11 of the torque converter 1 via a circular plate (not shown).

In the damper device 3, when the lock-up device 2 is in the locked-up state, the rotational driving force transmitted to the front cover 11 is input to the drive plate 31 of the damper device 3 via the lock-up clutch 4.

The damper 3 includes a driven plate 32 and a side plate 33 in addition to the driving plate 31.

The drive plate 31 and the driven plate 32 are arranged on a common axis of rotation X in a relatively rotatable manner. The drive plate 31 and the driven plate 32 are coupled to each other so as to be rotatable and transmittable via a spring B1 provided in the circumferential direction around the rotation axis X.

In the damper device 3, a drive plate 31 is provided on one side (the front cover 11 side) of a driven plate 32 in the rotation axis X direction, and a side plate 33 is provided on the other side (the turbine wheel 13 side).

The side plate 33 is coupled to the turbine impeller 13 of the torque converter 1.

The inner diameter side of the driven plate 32 is coupled to the coupling portion 121 of the turbine hub 12 so as not to be rotatable relative thereto.

The turbine hub 12 has a cylindrical fitting portion 122 on the inner diameter side of the coupling portion 121, and the fitting portion 122 is spline-engaged with the outer periphery of the rotation transmission shaft 20.

The fitting portion 122 extends from the inner diameter side of the coupling portion 121 in a direction (right direction in fig. 1) away from the coupling portion 121 along the rotation axis X, and the support member 15 of the turbine impeller 13 is coupled to the outer periphery of the fitting portion 122 so as not to be relatively rotatable.

The inner diameter side of the side plate 33 is connected to the support member 15 together with the turbine wheel 13 so as not to be relatively rotatable. The driven plate 32 and the side plate 33 are provided on a common rotation axis X via the turbine hub 12 and the support member 15 so as not to be relatively rotatable.

The drive plate 31 is coupled to the clutch drum 44 of the lock-up clutch 4 so as to be integrally rotatable on the front cover 11 side of the driven plate 32 in the direction of the rotation axis X.

The lockup clutch 4 includes: an inner diameter side friction plate 41 that rotates integrally with the front cover 11; an outer diameter side friction plate 42 that rotates integrally with the drive plate 31; and a piston 43 that presses the inner diameter side friction plate 41 and the outer diameter side friction plate 42 in the rotation axis direction.

The outer diameter side friction plate 42 is spline-engaged with the inner circumference of the peripheral wall portion 441 of the clutch drum 44. The inner diameter side friction plate 41 is spline-engaged with the outer periphery of the peripheral wall portion 451 of the clutch hub 45.

The inner-diameter side friction plates 41 and the outer-diameter side friction plates 42 are alternately arranged in the direction of the rotation axis X.

In the present embodiment, the inner diameter side friction plates 41, 41 are positioned on both sides in the direction of the rotation axis X, and the inner diameter side friction plates 41 and the outer diameter side friction plates 42 are alternately arranged between the inner diameter side friction plates 41, 41 positioned on both sides.

As shown in fig. 2, the clutch drum 44 is formed in a bottomed cylindrical shape including a bottom wall portion 442 and a peripheral wall portion 441 surrounding a peripheral edge of the bottom wall portion 442.

The clutch drum 44 is provided such that the bottom wall 442 faces perpendicular to the direction of the rotation axis X, and the opening of the peripheral wall 441 faces toward the front cover 11.

The bottom wall portion 442 of the clutch drum 44 is coupled on the inner diameter side to the drive plate 31, and the clutch drum 44 is coupled to the drive plate 31 so as to be relatively non-rotatable.

The outer diameter side friction plate 42 is spline-engaged with the inner circumference of the circumferential wall 441 of the clutch drum 44 so as to be movable in the rotation axis X direction.

As shown in fig. 2, the clutch hub 45 is formed in a bottomed cylindrical shape including a bottom wall portion 452 and a peripheral wall portion 451 surrounding a peripheral edge of the bottom wall portion 452. The clutch hub 45 has a bottom wall 452 fixed to the front cover 11 in a state where the opening of the peripheral wall 451 faces the bottom wall 442 of the clutch drum 44.

The clutch hub 45 is coupled to the front cover 11 so as not to be rotatable relative thereto.

The inner diameter side friction plate 41 is spline-engaged with the outer periphery of the peripheral wall portion 451 of the clutch hub 45 so as to be movable in the rotation axis X direction.

The clutch drum 44 and the clutch hub 45 are coaxially arranged on a common rotation axis X.

The peripheral wall portion 451 and the peripheral wall portion 441 overlap in the radial direction of the rotation axis X, as viewed in the radial direction of the rotation axis X, such that the peripheral wall portion 451 of the clutch hub 45 and the peripheral wall portion 441 of the clutch drum 44 overlap.

An abutting portion 111 that abuts against the inner diameter side friction plate 41 is provided in the front cover 11.

The contact portion 111 faces a region where the inner diameter side friction plate 41 and the outer diameter side friction plate 42 overlap with each other in the rotation axis X direction when viewed from the rotation axis X direction.

The piston 43 is provided on the side opposite to the front cover 11 (the bottom wall portion 442 side) as viewed from the inner diameter side friction plate 41 and the outer diameter side friction plate 42.

As shown in fig. 2 and 3, the piston 43 has a ring-shaped base portion 430 and a cylindrical portion 432 surrounding the outer peripheral edge of the base portion 430 over the entire circumference when viewed from the direction of the rotation axis X. The annular base 430 is formed with a substantially uniform thickness in the direction of the rotation axis X. A side surface 430a (left side in the drawing) of the base 430 on the front cover 11 side becomes a flat surface orthogonal to the rotation axis X direction.

As shown in fig. 1, a support member 10 for supporting the piston 43 is provided on the inner diameter side of the front cover 11. The support member 10 is provided to penetrate through an opening 11a on the inner diameter side of the front cover 11 in the rotation axis X direction, and the outer periphery of the fitting portion 101 fitted in the opening 11a is welded to the front cover 11.

The support member 10 is provided with a support portion 102 of the piston 43 adjacent to the fitting portion 101. The support portion 102 is formed with a larger outer diameter than the fitting portion 101, and is housed inside the front cover 11.

As shown in fig. 2, the outer periphery 102a of the support portion 102 is a flat surface parallel to the rotation axis X, and the base portion 430 of the piston 43 is inserted outside the outer periphery of the support portion 102. In this state, the piston 43 is slidably provided in the outer periphery 102a in the rotation axis X direction.

The piston 43 inserted in the support portion 102 is provided such that the base portion 430 is oriented perpendicular to the rotation axis X, and in this state, the piston 43 is provided such that the center line of the base portion 430 is positioned on the rotation axis X.

In the piston 43, a seal ring C is fitted to the inner periphery of the base portion 430, and a gap between the inner periphery of the base portion 430 and the outer periphery 102a of the support portion 102 is sealed by the seal ring C.

The base portion 430 is provided across a region where the clutch hub 45 is provided from the inner diameter side to the outer diameter side when viewed from the rotation axis X direction.

The outer peripheral edge side region of the base 430 is bent in a direction (left direction in the drawing) approaching the inner diameter side friction plate 41 and the outer diameter side friction plate 42. The bent region serves as a pressing portion 431 that presses the inner diameter side friction plate 41 in the direction of the rotation axis X.

The pressing portion 431 faces a region where the inner diameter side friction plate 41 and the outer diameter side friction plate 42 overlap, as viewed from the rotation axis X direction.

As shown in fig. 2, the cylindrical portion 432 surrounding the outer periphery of the base portion 430 extends in a direction (rightward in the drawing) away from the inner diameter side friction plate 41 and the outer diameter side friction plate 42 in the inner diameter side of the peripheral wall portion 441 of the clutch drum 44.

The front end 432a of the cylindrical portion 432 faces the bottom wall 442 of the clutch drum 44 with a gap in the rotation axis X direction.

The seal ring C provided on the outer periphery of the annular wall 46 elastically contacts the inner periphery of the cylindrical portion 432. The seal ring C is provided to seal a gap between the inner periphery of the cylindrical portion 432 and the outer periphery of the annular wall 46.

The inner periphery of the annular wall 46 is fixed to the support portion 102 of the piston 43.

Therefore, a space surrounded by the piston 43, the annular wall 46, and the support portion 102 is formed on the inner diameter side (the rotation axis X side) of the cylindrical portion 432 of the piston 43, and this space serves as an oil chamber R to which the hydraulic pressure of the piston 43 is supplied.

The hydraulic pressure of the piston 43 is supplied to the oil chamber R through an oil passage (not shown) provided in the support member 10.

In the lockup clutch 4, when the hydraulic pressure is supplied to the oil chamber R, the piston 43 is displaced toward the front cover 11 (leftward in the drawing) while sliding on the outer periphery 102a of the support portion 102.

Then, the inner diameter side friction plate 41 and the outer diameter side friction plate 42 are coupled to each other so as not to be relatively rotatable between the pressing portion 431 of the piston 43 and the contact portion 111 of the front cover 11.

Thereby, the relative rotation of the front cover 11, in which the inner-diameter side friction plates 41 are coupled via the clutch hub 45, and the drive plate 31, in which the outer-diameter side friction plates 42 are coupled via the clutch drum 44, is restricted around the rotation axis X, and the lock-up clutch 4 is brought into the engaged state.

As shown in fig. 2, in the lockup clutch 4, a spring B2 is provided on the inner diameter side of the peripheral wall portion 451 of the clutch hub 45.

The other end B2B of the spring B2 is supported by a spring support piece 455 fixed to the bottom wall portion 452 of the clutch hub 45, and the one end B2a of the spring B2 is supported by the plate member 49 interposed between the base portion 430 of the piston 43.

The spring B2 is provided in parallel with the rotation axis X and is provided in a state of being compressed in the rotation axis X direction.

Therefore, the plate member 49 is pressed against the side surface 430a of the base portion 430 of the piston 43 by the urging force acting from the spring B2.

A spline Sp is formed on the outer periphery of the plate member 49 along the rotation axis X direction. The plate member 49 is spline-engaged with the inner periphery of the peripheral wall portion 451 of the clutch hub 45. Relative rotation of the plate member 49 and the clutch hub 45 about the rotation axis X is restricted. Further, in this state, the plate member 49 and the peripheral wall portion 451 of the clutch hub 45 can be relatively displaced in the direction of the rotation axis X.

Therefore, the plate member 49 is displaced relative to the peripheral wall portion 451 of the clutch hub 45 in conjunction with the displacement of the piston 43 in the direction of the rotation axis X, and thereby the displacement of the piston 43 in the direction of the rotation axis X is not hindered.

The spring B2 is disposed in the space (internal space S1) on the inner diameter side of the clutch hub 45. The plurality of springs B2 are provided at equal intervals in the circumferential direction around the rotation axis X.

The spring B2 biases the piston 43 in a direction of displacing toward the oil chamber R (right side in the drawing).

Therefore, in the lock-up clutch 4, when the supply of the hydraulic oil pressure to the oil chamber R is completed, the piston 43 is displaced toward the oil chamber R by the biasing force of the spring B2 acting through the plate member 49.

Due to the displacement of the piston 43 toward the oil chamber R, the pressing portion 431 of the piston 43 is displaced in a direction away from the inner diameter side friction plate 41, and the inner diameter side friction plate 41 and the outer diameter side friction plate 42 are relatively rotatable.

Thus, relative rotation of the front cover 11, in which the inner-diameter side friction plates 41 are coupled via the clutch hub 45, and the drive plate 31, in which the outer-diameter side friction plates 42 are coupled via the clutch drum 44, around the rotation axis X is allowed, and the lock-up clutch 4 is brought into the released state.

In the present embodiment, the plate member 49 supports one end B2a of the spring B2, and the spring support piece 455 supports the other end B2B, thereby forming a rotation stop structure for preventing relative rotation between the spring B2 and the clutch hub 45.

In this state, the plate member 49 and the bottom wall portion 452 supporting the spring B2 are disposed in the internal space S1 of the clutch hub 45.

Here, a lubricating oil passage (not shown) for supplying the oil OL to the internal space S1 is provided in the support member 10 (see fig. 1) located on the inner diameter side of the internal space S1.

Here, the oil OL discharged from the lubricating oil passage (not shown) into the internal space S1 flows from the inner diameter side to the outer diameter side in the internal space S1 (the inner diameter side of the clutch hub 45) by the centrifugal force generated by the rotation of the torque converter 1, and passes through the plate member 49 side to reach the inner diameter side friction plate 41 and the outer diameter side friction plate 42.

The lubricating oil path (not shown) is provided for supplying and cooling the oil OL to the inner diameter side friction plate 41 and the outer diameter side friction plate 42. The internal space S1 can be said to be a lubrication path for supplying the cooling oil OL to the inner diameter side friction plate 41 and the outer diameter side friction plate 42.

In the lubrication path, the plate member 49 supporting the spring B2 and the spring support piece 455 face each other.

The lockup clutch 4 (friction engagement device) of the present embodiment has the following configuration.

(1) Comprising:

a plurality of outer diameter side friction plates 42 (first plates) slidably engaged with a clutch drum 44 (outer circumferential side cylindrical member);

a plurality of inner diameter side friction plates 41 (second plates) slidably engaged with a clutch hub 45 (inner peripheral side cylindrical member);

a piston 43 that presses the outer diameter side friction plate 42 and the inner diameter side friction plate 41 by moving in the direction of the rotation axis X;

a spring B2 (urging member) that urges the piston 43 in the direction of the rotation axis X;

a plate member 49 supporting one end B2a of the spring B2,

the plate member 49 is slidably engaged with the clutch hub 45 in the direction of the rotation axis X.

With this configuration, the plate member 49, which is a member different from the piston 43, forms a rotation stop structure of the spring B2 for preventing relative rotation with the clutch hub 45.

This can ensure the freedom of selecting the shape of the piston 43. For example, the piston may be formed in a simple shape (annular base 430) without forming a rotation stop structure, or may be formed in a specialized shape that satisfies functional requirements other than rotation stop. Further, since the base portion 430 of the piston 43 is plate-shaped, the axial length of the entire device can be reduced.

The lockup clutch 4 (friction engagement device) of the present embodiment has the following configuration.

(2) The other end B2B of the spring B2 is supported by a spring support piece 455 (a member that rotates integrally with the inner peripheral side cylindrical member) of the bottom wall portion 452 of the clutch hub 45.

With this configuration, the one end B2a and the other end B2B of the spring B2 rotate integrally in the circumferential direction around the rotation axis X. Therefore, the spring B2 can be prevented from being twisted by the rotation.

In the present embodiment, the case where the other end B2B of the spring B2 is supported by the spring support piece 455 (the inner peripheral side cylindrical member itself) of the bottom wall portion 452 of the clutch hub 45 is illustrated, but the present invention is not limited thereto. For example, the other end B2B of the spring B2 may be supported by the front cover 11 (another member that rotates integrally with the inner peripheral side cylindrical member).

The lockup clutch 4 (friction engagement device) of the present embodiment has the following configuration.

(3) The oil OL passing through the space on the plate member 49 side flows into the outer diameter side friction plate 42 and the inner diameter side friction plate 41.

As shown in fig. 4, in the lock-up clutch 100 of the conventional example, when the piston 200 is engaged with a member of the frictional engagement element, the flow of the oil OL from the inner diameter side to the outer diameter side is blocked by a portion (protrusion portion 250) of the piston 200 protruding in the direction of the rotation axis X.

Thus, with the above-described configuration, the plate member 49 separate from the piston 43 enlarges the space in which the oil OL flows, and the oil OL can be smoothly supplied to the lockup clutch 4 (the outer-diameter-side friction plate 42 and the inner-diameter-side friction plate 41).

In the above-described embodiment, the plate member 49 is spline-engaged with the clutch hub 45 slidably in the direction of the rotation axis X, and a rotation stop structure of the spring B2 for preventing relative rotation with the clutch hub 45 is provided. For example, the plate member 49 may be spline-engaged with the clutch drum 44 slidably in the direction of the rotation axis X, thereby forming a rotation stop structure of the spring B2 that prevents relative rotation with the clutch drum 44.

In this case, the other end B2B of the spring B2 may be supported by the clutch drum 44 itself, or may be supported by a member that rotates integrally with the clutch drum 44.

Further, when the plate member 49 is spline-engaged with the clutch drum 44, the connection portion between the piston 43 and the plate member 49 needs to be provided on the outer circumferential side, and therefore the piston 43 expands in the radial direction. Thus, the lock-up clutch 4 increases in size in the radial direction.

In contrast, when the plate member 49 is spline-engaged with the clutch hub 45, the piston 43 does not need to be radially expanded by the space inside the clutch hub 45. Therefore, it is preferable that the plate member 49 is spline-engaged with the clutch hub 45 in order to prevent the lock-up clutch 4 from being increased in size.

The present invention is not limited to the above-described embodiments, and various changes and modifications can be made within the scope of the technical idea thereof.