JP7077045B2 - Torque converter and fluid transfer device - Google Patents

Description

The present invention relates to a torque converter and a fluid transmission device.

The torque converter has an impeller and a turbine, and transmits torque from the impeller to the turbine via internal hydraulic oil. The impeller is fixed to the front cover where the torque from the engine is input. The turbine is located facing the impeller. When the impeller rotates, hydraulic oil flows from the impeller to the turbine, and torque is output by rotating the turbine.

Further, the torque converter has a lock-up device. When the lockup device is turned on, the torque from the front cover is mechanically transmitted to the turbine and output to the input shaft of the transmission.

For example, the torque converter described in Patent Document 1 has a lockup clutch piston. The power transmission efficiency is improved by frictionally engaging the piston with the converter cover in the high-speed transmission range.

Further, in the torque converter described in Patent Document 1, in order to operate the piston reliably, a lip seal is provided outside the clutch facing in the radial direction. This lip seal ensures that the front-rear differential pressure of the piston is generated.

Japanese Unexamined Patent Publication No. 5-296313

In the above-mentioned configuration, it is required to improve the responsiveness of the piston. Therefore, an object of the present invention is to improve the responsiveness of the piston.

The torque converter according to the first aspect of the present invention includes a front cover, an impeller, a turbine, a piston, and a sealing mechanism. The impeller is fixed to the front cover. The turbine is placed facing the impeller. The piston is arranged so as to be axially movable between the front cover and the turbine. The piston is configured to be frictionally engageable with the front cover. The sealing mechanism is configured to radially divide the hydraulic chamber defined between the front cover and the piston.

In the torque converter according to the present invention, the sealing mechanism divides the hydraulic chamber in the radial direction. Therefore, the hydraulic oil in the outer hydraulic chamber located radially outside the sealing mechanism is discharged radially outward, and the hydraulic oil in the inner hydraulic chamber radially inside the sealing mechanism is discharged radially inward. In this way, since the hydraulic oil in the hydraulic chamber is discharged separately in two directions, the hydraulic oil can be quickly discharged from the hydraulic chamber between the piston and the front cover. As a result, the torque converter according to the present invention can improve the responsiveness of the piston. Further, when the speed ratio between the front cover and the turbine is 1 or more, the responsiveness of the piston generally deteriorates, but in the torque converter according to the present invention, the piston is reliably operated even when the speed ratio is 1 or more. Can be made to respond to. The speed ratio of 1 or more means that the rotation speed of the turbine is equal to or higher than the rotation speed of the front cover.

Preferably, the sealing mechanism is arranged at a position that divides the pressure receiving area of the piston in the radial direction.

Preferably, the sealing mechanism is arranged at a position below the radius that divides the pressure receiving area of the piston into two equal parts.

Preferably, the sealing mechanism divides the hydraulic chamber into an inner hydraulic chamber and an outer hydraulic chamber. The sealing mechanism allows the flow of hydraulic oil from the inner hydraulic chamber to the outer hydraulic chamber.

Preferably, the sealing mechanism blocks the flow of hydraulic oil between the outer hydraulic chamber and the inner hydraulic chamber when the hydraulic pressure in the outer hydraulic chamber is higher than the hydraulic pressure in the inner hydraulic chamber. Then, the sealing mechanism allows the flow of the working flow between the outer hydraulic chamber and the inner hydraulic chamber when the hydraulic pressure in the inner hydraulic chamber is higher than the hydraulic pressure in the outer hydraulic chamber.

Preferably, the sealing mechanism has an annular groove and a sealing ring. The annular groove is formed on one of the front cover and the piston. The seal ring is arranged so as to be movable in the direction of approaching or moving away from the inner hydraulic chamber in the annular groove. The annular groove is defined by a bottom surface, a first inner wall surface on the inner hydraulic chamber side, and a second inner wall surface on the opposite side of the first inner wall surface. The seal ring has a first side surface facing the first inner wall surface, a second side surface facing the second inner wall surface, an inner peripheral surface facing the bottom surface, and an outer peripheral surface facing the other of the piston and the turbine. One of the second inner wall surface and the second side surface has an oil groove.

Preferably, the torque converter further comprises a friction material attached to the outer peripheral end of the piston.

The power transmission device according to the second aspect of the present invention includes a rotating member, a piston, and a sealing mechanism door. The piston is arranged so as to be movable in the axial direction so as to face the rotating member. Further, the piston is configured to be frictionally engaged with the rotating member. The sealing mechanism is configured to radially divide the hydraulic chamber defined between the rotating member and the piston. The rotating member is, for example, a front cover.

According to the present invention, the responsiveness of the piston can be improved.

Sectional view of the torque converter. Sectional view of the lockup device. Sectional drawing of the sealing mechanism. Sectional drawing of the torque converter which shows each hydraulic chamber. Sectional drawing of the sealing mechanism.

[overall structure]
FIG. 1 is a cross-sectional view of a torque converter 100 according to an embodiment of the present invention. In the following description, the "axial direction" means the direction in which the rotation axis O of the torque converter 100 extends. Further, the "radial direction" means the radial direction of the circle centered on the rotation axis O, and the "circumferential direction" means the circumferential direction of the circle centered on the rotation axis O. Although not shown, the engine is arranged on the left side of FIG. 1, and the transmission is arranged on the right side of FIG. 1.

The torque converter 100 can rotate about the rotation axis O. The torque converter 100 includes a front cover 2, an impeller 3, a turbine 4, a stator 5, and a lockup device 10.

[Front cover 2]
Torque from the engine is input to the front cover 2. The front cover 2 has a disk portion 21 and a first cylindrical portion 22. The first cylindrical portion 22 extends axially from the outer peripheral end portion of the disk portion 21 toward the impeller 3 side.

The disk portion 21 has a first protruding portion 211 in the central portion. The first protruding portion 211 protrudes toward the piston 6, which will be described later, in the axial direction. As shown in FIG. 3, the first protrusion 211 has a first facing surface 212. The first facing surface 212 faces the second facing surface 612, which will be described later. The first facing surface 212 faces in the radial direction. Specifically, the first facing surface 212 faces inward in the radial direction.

[Impeller 3]
As shown in FIG. 1, the impeller 3 is fixed to the front cover 2. The impeller 3 has an impeller shell 31, a plurality of impeller blades 32, and an impeller hub 33. The impeller shell 31 is fixed to the front cover 2 by welding, for example.

The impeller blade 32 is fixed to the inner surface of the impeller shell 31. The impeller hub 33 is fixed to the inner peripheral end of the impeller shell 31 by welding or the like.

[Turbine 4]
The turbine 4 is arranged to face the impeller 3. The turbine 4 has a turbine shell 41, a plurality of turbine blades 42, and a turbine hub 43. The turbine blade 42 is fixed to the inner surface of the turbine shell 41 by brazing or the like.

The turbine hub 43 is fixed to the inner peripheral end of the turbine shell 41 by, for example, a rivet. The turbine hub 43 is formed with a spline hole 431. The transmission input shaft (not shown) is spline-fitted into the spline hole 431.

[Stator 5]
The stator 5 is configured to rectify the hydraulic oil returning from the turbine 4 to the impeller 3. The stator 5 is rotatable around the rotation axis O. Specifically, the stator 5 is supported by a fixed shaft (not shown) via a one-way clutch 101. The stator 5 is arranged between the impeller 3 and the turbine 4.

The stator 5 has a disk-shaped stator carrier 51 and a plurality of stator blades 52 attached to the outer peripheral surface thereof. A first thrust bearing 102 is arranged between the stator 5 and the impeller 3, and a second thrust bearing 103 is arranged between the stator 5 and the turbine 4.

[Lockup device 10]
The lockup device 10 mechanically transmits torque from the front cover 2 to the turbine 4, and is arranged between the front cover 2 and the turbine 4 in the axial direction. As shown in FIG. 2, the lockup device 10 includes a piston 6, a damper mechanism 7, and a seal mechanism 8.

[Piston 6]
The piston 6 is arranged so as to be movable in the axial direction between the front cover 2 and the turbine 4. Specifically, the piston 6 is arranged so as to be slidable in the axial direction on the outer peripheral surface of the turbine hub 43. Further, the piston 6 can rotate relative to the turbine hub 43.

The piston 6 is configured to be frictionally engaged with the front cover 2. Specifically, the piston 6 is configured to be frictionally engaged with the front cover 2 at the outer peripheral end portion. The piston 6 has a disk portion 61, a second cylindrical portion 62, and a sliding portion 63.

The friction material 9 is fixed to the disk portion 61 at the outer peripheral end portion. The disk portion 61 is configured to press the disk portion 21 of the front cover 2 via the friction material 9. As the disk portion 61 presses the front cover 2 via the friction material 9 in this way, the piston 6 is frictionally engaged with the front cover 2. The friction material 9 may be fixed to the front cover 2 instead of the piston 6. The friction material 9 is annular.

The disk portion 61 has a second protruding portion 611 at the central portion. The second protruding portion 611 projects toward the front cover 2 in the axial direction. As shown in FIG. 3, the second protrusion 611 has a second facing surface 612. As described above, the second facing surface 612 faces the first facing surface 212 of the first protruding portion 211 of the front cover 2. The second facing surface 612 faces in the radial direction. Specifically, the second facing surface 612 faces outward in the radial direction.

As shown in FIG. 2, the second cylindrical portion 62 extends in the axial direction from the outer peripheral end portion of the disk portion 61. The second cylindrical portion 62 extends in a direction away from the front cover 2. The outer peripheral surface of the second cylindrical portion 62 is arranged at a distance from the inner peripheral surface of the first cylindrical portion 22 of the front cover 2.

The sliding portion 63 has a cylindrical shape. The sliding portion 63 extends in the axial direction from the inner peripheral end portion of the disk portion 61. The sliding portion 63 extends in a direction away from the front cover 2. The sliding portion 63 is slidably supported on the outer peripheral surface of the turbine hub 43. A seal member 105 is provided on the outer peripheral surface of the turbine hub 43, and the seal member 105 seals between the inner peripheral surface of the sliding portion 63 of the piston 6 and the outer peripheral surface of the turbine hub 43.

[Damper mechanism 7]
The damper mechanism 7 is arranged between the piston 6 and the turbine 4 in the axial direction. The damper mechanism 7 elastically connects the piston 6 and the turbine 4. The damper mechanism 7 has a drive plate 71, a torsion spring 72, and a driven plate 73.

The drive plate 71 is formed in a disk shape. The drive plate 71 is fixed to the piston 6. Specifically, the inner peripheral end portion of the drive plate 71 is fixed to the piston 6 by a rivet or the like. The outer peripheral end of the drive plate 71 is engaged with the torsion spring 72.

The driven plate 73 is fixed to the turbine 4. Specifically, the driven plate 73 is fixed to the turbine 4 by welding or the like. The driven plate 73 is engaged with the torsion spring 72.

With the above configuration, the torque input to the piston 6 is transmitted to the turbine 4 via the drive plate 71, the torsion spring 72, and the driven plate 73.

[Seal mechanism]
As shown in FIG. 4, the seal mechanism 8 is configured to radially divide the first hydraulic chamber S1 defined between the front cover 2 and the piston 6. Specifically, the seal mechanism 8 divides the first hydraulic chamber S1 into an inner hydraulic chamber Sa and an outer hydraulic chamber Sb. The first hydraulic chamber S1 corresponds to the hydraulic chamber of the present invention. Further, in the following description, the second hydraulic pressure chamber S2 is a hydraulic pressure chamber excluding the first hydraulic pressure chamber S1 from the hydraulic pressure chamber defined by the front cover 2 and the impeller shell 31.

The sealing mechanism 8 is arranged inside the friction material 9 in the radial direction. The sealing mechanism 8 is arranged at a position where the pressure receiving area of the piston 6 is divided in the radial direction. Preferably, the sealing mechanism 8 is arranged at a position having a radius R or less that divides the pressure receiving area of the piston 6 into two equal parts. That is, the radius of the outer peripheral surface of the sealing mechanism 8 is equal to or less than the radius R. In the present embodiment, the radius of the outer peripheral surface of the seal ring 82 of the seal mechanism 8 is equal to or less than the radius R.

The pressure receiving area of the piston 6 means the projected area of the portion of the piston 6 that receives hydraulic pressure from the first hydraulic chamber S1 and the second hydraulic chamber S2 with respect to the plane orthogonal to the rotation axis O. The piston 6 can receive the hydraulic pressure in the second hydraulic chamber S2 not only on the inner side in the radial direction from the seal mechanism 8 but also on the outer side in the radial direction from the seal mechanism 8. For example, the piston 6 does not have a through hole for communicating the first hydraulic chamber S1 and the second hydraulic chamber S2 on the outer side in the radial direction from the sealing mechanism 8.

The seal mechanism 8 blocks the flow of hydraulic oil between the outer hydraulic chamber Sb and the inner hydraulic chamber Sa when the hydraulic pressure in the outer hydraulic chamber Sb is higher than the hydraulic pressure in the inner hydraulic chamber Sa. That is, the seal mechanism 8 blocks the flow of hydraulic oil from the outer hydraulic chamber Sb to the inner hydraulic chamber Sa. On the other hand, when the hydraulic pressure of the inner hydraulic chamber Sa is higher than the hydraulic pressure of the outer hydraulic chamber Sb, the seal mechanism 8 allows the flow of the working flow between the outer hydraulic chamber Sb and the inner hydraulic chamber Sa. That is, the seal mechanism 8 allows the hydraulic oil to flow from the inner hydraulic chamber Sa to the outer hydraulic chamber Sb.

As shown in FIG. 3, the sealing mechanism 8 has an annular groove 81 and a sealing ring 82. The annular groove 81 is formed in the piston 6. Specifically, the annular groove 81 is formed on the second facing surface 612 of the second protruding portion 611 of the piston 6.

The annular groove 81 is defined by a first inner wall surface 811, a second inner wall surface 812, and a bottom surface 813. The first inner wall surface 811 is an inner wall surface on the inner hydraulic chamber Sa side. The first inner wall surface 811 faces the piston 6 side. That is, the first inner wall surface 811 is a surface facing the right side in FIG.

The second inner wall surface 812 is an inner wall surface opposite to the first inner wall surface 811. The second inner wall surface 812 faces the front cover 2 side. That is, the second inner wall surface 812 is a surface facing the left side in FIG. The first inner wall surface 811 and the second inner wall surface 812 face each other in a state where the seal ring 82 is removed. The bottom surface 813 extends between the first inner wall surface 811 and the second inner wall surface 812. The bottom surface 813 faces outward in the radial direction.

The seal ring 82 is annular and is arranged in the annular groove 81. The seal ring 82 is arranged so as to be movable in a direction toward and away from the inner hydraulic chamber Sa. In the present embodiment, the seal ring 82 is arranged so as to be movable in the axial direction in the annular groove 81.

The outer peripheral surface 823 of the seal ring 82 is in contact with the first facing surface 212 of the first protruding portion 211 of the front cover 2. Therefore, when the seal ring 82 moves in the axial direction, the seal ring 82 slides on the first facing surface 212 of the first protrusion 211.

The seal ring 82 has a rectangular cut surface orthogonal to the circumferential direction. The seal ring 82 has a first side surface 821 and a second side surface 822. The first side surface 821 faces the first inner wall surface 811 of the annular groove 81. That is, the first side surface 821 faces the front cover 2 side (left side in FIG. 3) in the axial direction. Further, the second side surface 822 faces the second inner wall surface 812 of the annular groove 81. That is, the second side surface 822 faces the piston 6 side (right side in FIG. 3) in the axial direction.

The inner peripheral surface 824 of the seal ring 82 faces the bottom surface 813 of the annular groove 81. The inner peripheral surface 824 of the seal ring 82 is arranged at a distance from the bottom surface 813 of the annular groove 81. Therefore, the hydraulic oil can flow in the space between the inner peripheral surface 824 of the seal ring 82 and the bottom surface 813 of the annular groove 81.

The second side surface 822 has a plurality of oil grooves 83. The oil grooves 83 are arranged so as to be spaced apart from each other in the circumferential direction. Each oil groove 83 extends radially on the second side surface 822. Each oil groove 83 is open to the outer hydraulic chamber Sb. Further, each oil groove 83 is also open to a space between the inner peripheral surface 824 of the seal ring 82 and the bottom surface 813 of the annular groove 81. The seal ring 82 is made of resin.

[motion]
Next, the operation of the torque converter 100 configured as described above will be described with reference to FIG. In the torque converter operating region where torque is transmitted from the impeller 3 to the turbine 4 via the hydraulic oil, the hydraulic oil supplied from the first oil passage P1 is the inner hydraulic chamber Sa → the outer hydraulic chamber Sb → the second hydraulic chamber S2 →. It circulates in the route of the second oil passage P2. In this case, the torque input from the front cover 2 to the impeller 3 is output to the input shaft of the transmission via the turbine 4.

In the above torque converter operating region, the lockup device 10 is in an off state (a state in which torque transmission is cut off). When the lockup device 10 is in the off state, the hydraulic pressure of each part is
1st hydraulic chamber S1 (inner hydraulic chamber Sa)> 2nd hydraulic chamber S2
It has become a relationship. Therefore, the piston 6 is not frictionally engaged with the front cover 2. That is, the piston 6 does not press the front cover 2 via the friction material 9. Therefore, the torque from the front cover 2 is not transmitted to the piston 6.

As described above, when the hydraulic pressure of the first hydraulic chamber S1, particularly the inner hydraulic chamber Sa, is higher than the hydraulic pressure of the second hydraulic chamber S2, the seal mechanism 8 has the flow of hydraulic oil from the inner hydraulic chamber Sa to the outer hydraulic chamber Sb. Tolerate. Specifically, the seal ring 82 moves in the annular groove 81 in a direction away from the inner hydraulic chamber Sa (see FIG. 5). The second side surface 822 of the seal ring 82 is in contact with the second inner wall surface 812 of the annular groove 81. Here, since the second side surface 822 of the seal ring 82 has an oil groove 83, the hydraulic oil flows from the inner hydraulic chamber Sa to the outer hydraulic chamber Sb through the oil groove 83. In this way, the hydraulic oil circulates in the path of the first oil passage P1 → the first hydraulic chamber S1 → the second hydraulic chamber S2 → the second oil passage P2, so that the inside of the torque converter 100 can be cooled.

Next, when the rotation speed of the torque converter 100 increases to a predetermined rotation speed or higher, the supply of hydraulic oil from the first oil passage P1 to the first hydraulic chamber S1 is stopped, and the second oil passage P2 to the second oil passage P2. 2 Supply hydraulic oil to the hydraulic chamber S2. Then, the hydraulic pressure of the second hydraulic pressure chamber S2 becomes higher than the hydraulic pressure in the first hydraulic pressure chamber S1, particularly the inner hydraulic pressure chamber Sa, and the piston 6 moves to the front cover 2 side. As a result, the piston 6 and the front cover 2 are frictionally engaged with each other, and the lockup device 10 is turned on. As a result, the torque from the front cover 2 is transmitted to the turbine 4 via the piston 6 and the damper mechanism 7.

As described above, when the hydraulic pressure in the outer hydraulic chamber Sb is higher than the hydraulic pressure in the inner hydraulic chamber Sa, the seal mechanism 8 blocks the flow of hydraulic oil between the outer hydraulic chamber Sb and the inner hydraulic chamber Sa. Specifically, the seal ring 82 is moved to the inner hydraulic chamber Sa side in the annular groove 81 by the hydraulic pressure in the outer hydraulic chamber Sb. The first side surface 821 of the seal ring 82 is in contact with the first inner wall surface 811 of the annular groove 81 (see FIG. 3). Therefore, the flow of hydraulic oil from the outer hydraulic chamber Sb to the inner hydraulic chamber Sa is blocked, and the hydraulic pressure of the second hydraulic chamber S2 can be maintained higher than the hydraulic pressure of the inner hydraulic chamber Sa. As a result, good responsiveness of the piston 6 can be ensured.

Further, since the sealing mechanism 8 divides the first hydraulic chamber S1 into the inner hydraulic chamber Sa and the outer hydraulic chamber Sb, the hydraulic oil in the first hydraulic chamber S1 is supplied from two directions, the inner side and the outer side in the radial direction. Can be discharged. As a result, the responsiveness of the piston 6 can be improved.

[Modification example]
Although the embodiments of the present invention have been described above, the present invention is not limited thereto, and various modifications can be made without departing from the spirit of the present invention.

(A) In the above embodiment, the oil groove 83 is formed on the second side surface 822 of the seal ring 82, but the configuration of the oil groove 83 is not limited to this. For example, the oil groove 83 may be formed on the second inner wall surface 812 of the annular groove 81.

(B) In the above embodiment, a plurality of oil grooves 83 are formed, but the number of oil grooves 83 is not limited to this, and only one oil groove 83 may be formed.

(C) In the above embodiment, the inner peripheral surface 824 of the seal ring 82 and the bottom surface 813 of the annular groove 81 are not in contact with each other, but the inner peripheral surface 824 of the seal ring 82 and the bottom surface 813 of the annular groove 81 are in contact with each other. You may be doing it. In this case, another oil groove communicating with the oil groove 83 can be formed on the inner peripheral surface 824 of the seal ring 82.

(D) The sealing mechanism 8 is not limited to the above embodiment. For example, the seal mechanism 8 may be configured by a lip seal, a reed valve, or the like. In this case, it is preferable that the radius of the outer peripheral surface of the member constituting the seal mechanism 8, for example, the lip seal or the reed valve, is equal to or less than the radius R that divides the pressure receiving area of the piston 6 into two equal parts.

2: Front cover 3: Impeller 4: Turbine 6: Piston 8: Seal mechanism 81: Circular groove 811: First inner wall surface 812: Second inner wall surface 813: Bottom surface 82: Seal ring 821: First side surface 822: Second side surface 823: Outer peripheral surface 824: Inner peripheral surface 83: Oil groove 9: Friction material 100: Torque converter S1: First hydraulic chamber (example of hydraulic chamber)
Sa: Inner hydraulic chamber Sb: Outer hydraulic chamber
Sb: Outer hydraulic chamber

Claims (10)

With the front cover
The impeller fixed to the front cover and
A turbine arranged facing the impeller and
A piston that is axially movable between the front cover and the turbine and is configured to be frictionally engaged with the front cover.
A sealing mechanism configured to radially divide the hydraulic chamber defined between the front cover and the piston.
Equipped with
The sealing mechanism divides the hydraulic chamber into an inner hydraulic chamber and an outer hydraulic chamber.
The sealing mechanism allows the flow of hydraulic oil from the inner hydraulic chamber to the outer hydraulic chamber.
Torque converter.
The sealing mechanism is arranged at a position that divides the pressure receiving area of the piston in the radial direction.
The torque converter according to claim 1.
The sealing mechanism is arranged at a position below a radius that divides the pressure receiving area of the piston into two equal parts.
The torque converter according to claim 2.
When the oil pressure in the outer hydraulic chamber is higher than the oil pressure in the inner hydraulic chamber, the sealing mechanism blocks the flow of hydraulic oil between the outer hydraulic chamber and the inner hydraulic chamber, and the hydraulic pressure in the inner hydraulic chamber is prevented. Allows the flow of working flow between the outer hydraulic chamber and the inner hydraulic chamber when is higher than the oil pressure in the outer hydraulic chamber.
The torque converter according to any one of claims 1 to 3 .
The sealing mechanism includes an annular groove formed in one of the front cover and the piston, and a sealing ring that can move in the annular groove in a direction toward and away from the inner hydraulic chamber.
The torque converter according to any one of claims 1 to 4 .
The annular groove is defined by a bottom surface, a first inner wall surface on the inner hydraulic chamber side, and a second inner wall surface on the opposite side of the first inner wall surface.
The seal ring has a first side surface facing the first inner wall surface, a second side surface facing the second inner wall surface, an inner peripheral surface facing the bottom surface, and an outer periphery abutting the other of the piston and the turbine. Has a face,
One of the second inner wall surface and the second side surface has an oil groove.
The torque converter according to claim 5 .
Further comprising a friction material attached to the outer peripheral end of the piston.
The torque converter according to any one of claims 1 to 6 .
With the front cover
The impeller fixed to the front cover and
A turbine arranged facing the impeller and
A piston that is axially movable between the front cover and the turbine and is configured to be frictionally engaged with the front cover.
A sealing mechanism configured to radially divide the hydraulic chamber defined between the front cover and the piston.
Equipped with
The sealing mechanism has an annular groove formed in one of the front cover and the piston, and a sealing ring that can move in the annular groove in a direction toward and away from the inner hydraulic chamber.
Torque converter.
With rotating members,
A piston that is movably arranged in the axial direction so as to face the rotating member and is configured to be frictionally engaged with the rotating member.
A sealing mechanism configured to radially divide the hydraulic chamber defined between the rotating member and the piston.
Equipped with
The sealing mechanism divides the hydraulic chamber into an inner hydraulic chamber and an outer hydraulic chamber.
The sealing mechanism allows the flow of hydraulic oil from the inner hydraulic chamber to the outer hydraulic chamber.
Power transmission device.
With rotating members,
A piston that is movably arranged in the axial direction so as to face the rotating member and is configured to be frictionally engaged with the rotating member.
A sealing mechanism configured to radially divide the hydraulic chamber defined between the rotating member and the piston.
Equipped with
The sealing mechanism has an annular groove formed in the rotating member and a sealing ring that can move in a direction of approaching or moving away from the inner hydraulic chamber in the annular groove.
Power transmission device.

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