JP2021017912A - Friction fastening device of automatic transmission - Google Patents

Abstract

To supply a sufficient quantity of lubricants to friction plates, in a friction fastening device in which a position of an oil hole for supplying the lubricants to the friction plates and a spline part are offset with respect to each other in an axial direction.SOLUTION: A friction fastening device CL2 has an inside member 20, an outside member 30, a plurality of friction plates 40, a piston 50, a fastening hydraulic chamber 61 and a centrifugal balance chamber 62. The centrifugal balance chamber 62 is defined by an extension part 52 extending to an internal peripheral side from a pressing part 51 of the piston 50, and a seal plate 100. The inside member 20 comprises a vertical wall part 22 extending toward the internal peripheral side from a spline part 21. A lubricant passage X for supplying lubricants to the friction plates 40 has an oil path X1 in a radial direction between the vertical wall part 22 and the seal plate 100, and a guide oil path X2 communicating with the oil path X1 in the radial direction, and guiding the lubricants from one side to the other side in an axial direction along an internal peripheral side of the spline part 21 by a guide part 103 which is arranged at the seal plate 100.SELECTED DRAWING: Figure 3

Description

The present invention relates to a friction fastening device for an automatic transmission and belongs to the technical field of a transmission for a vehicle such as an automobile.

Automatic transmissions mounted on vehicles such as automobiles generally include a plurality of planetary gear sets (planetary gear mechanisms) and a plurality of friction fastening devices such as clutches and brakes, and these friction fastening devices are selectively selected by hydraulic control. By fastening the gears, the power transmission path via each planetary gear set can be switched to realize a plurality of forward gears and usually one reverse gear.

For example, the clutch has an outer member coupled to a predetermined rotating element such as a constituent member of a planetary gear mechanism or a rotating shaft, and an inner member coupled to another predetermined rotating element. Spline portions are provided on the inner peripheral side of the outer member and the outer peripheral side of the inner member, and each spline portion alternates between a friction plate having a spline portion on the inside and a friction plate having a spline portion on the outside. Is located in.

It is known that such a friction fastening device has a piston for fastening a plurality of friction plates and a fastening hydraulic chamber for supplying hydraulic oil for fastening that urges the piston in the fastening direction. Has been done.

Further, the piston of such a friction fastening device is rotating even at the time of release, and a centrifugal force is generated in the hydraulic oil in the fastening hydraulic chamber, and the piston is pressed in the fastening direction by the centrifugal force even though no hydraulic pressure is applied. There is. On the other hand, in order to cancel the pressing force in the fastening direction, a centrifugal balance chamber for supplying hydraulic oil may be provided on the anti-fastening hydraulic chamber side of the piston.

By the way, when the friction fastening device is engaged, it temporarily goes through the slip state during the transition from the released state to the fastened state. In this slip state, frictional heat is generated in the friction plate, and it is preferable to supply sufficient lubricating oil to ensure the durability of the friction plate.

For example, in the friction fastening device (clutch) described in Patent Document 1, an oil hole for supplying hydraulic oil that is closed at the time of release and supplied to the centrifugal balance chamber at the time of fastening to a friction plate provided on the outer peripheral side is provided. It has an open configuration.

Japanese Unexamined Patent Publication No. 2006-336728

However, as described in Patent Document 1, due to the layout, when the centrifugal balance chamber is arranged axially offset from the spline portion of the inner member with which the friction plate is spline-engaged, lubricating oil is supplied. The oil holes will be arranged on one side of the spline portion in the axial direction. In this case, the lubricating oil is not directly supplied to the friction plate from the oil hole, and in particular, the friction plate on the anti-centrifugal balance chamber side (the other side) is not sufficiently lubricated and is arranged from one side in the axial direction to the other side. There is a risk that the lubricating oil will not be evenly supplied to the friction plate.

An object of the present invention is to evenly supply lubricating oil to a friction plate in a friction fastening device in which the positions of oil holes for supplying lubricating oil to the friction plate and the spline portion are offset in the axial direction.

In order to solve the above problems, the present invention is characterized in that it is configured as follows.

The friction fastening device for an automatic transmission according to the invention according to claim 1 of the present application is
An inner member, an outer member, a plurality of friction plates arranged between the inner member and the outer member, a piston for fastening the plurality of friction plates, and a hydraulic oil for urging the piston in the fastening direction. Has a fastening hydraulic chamber to which the piston is supplied, and a centrifugal balance chamber to which the hydraulic oil for urging the piston in the release direction is supplied.
An automatic transmission in which the centrifugal balance chamber is defined by an extension portion extending inward from a pressing portion that presses the friction plate on the piston and a seal plate arranged to face the extension portion. Friction fastening device
The inner member
A cylindrical spline portion in which the plurality of friction plates are spline-engaged on the outer peripheral side thereof,
It is provided with a vertical wall portion extending from the spline portion toward the inner peripheral side and arranged on the anti-centrifugal balance chamber side of the seal plate.
The lubricating oil passage for supplying the lubricating oil to the plurality of friction plates is formed by the seal plate and the inner member.
The lubricating oil passage communicates with the radial oil passage for supplying lubricating oil from the radial inside to the outside between the vertical wall portion of the inner member and the seal plate, and also communicates with the radial oil passage. It is characterized by having a guide oil passage for guiding lubricating oil from one side in the axial direction to the other side along the inner peripheral side of the spline portion of the inner member by a guide portion provided on the seal plate. To do.

The invention according to claim 2 is the invention according to claim 1.
The inner peripheral side of the spline portion of the inner member is provided with a recess recessed from one side in the axial direction to the other side along the spline portion.
The guide portion of the seal plate is formed so as to extend from one side in the axial direction to the other side.
The guide oil passage is characterized in that the guide portion of the seal plate is formed by plunging into a recess of the inner member.

The invention according to claim 3 is the invention according to claim 2.
Ribs extending in the radial direction are provided between the inner peripheral surface and the outer peripheral surface of the concave portion of the inner member.
A notch is provided at the tip of the guide portion of the seal plate.
It is characterized in that the rib and the notch portion are engaged with each other.

The invention according to claim 4 is the invention according to claim 3.
One of the seal plate and the vertical wall portion of the piston is provided with an engaging convex portion, and the other is provided with an engaging concave portion.
The engaging convex portion and the engaging concave portion are engaged with each other.

The invention according to claim 5 is the invention according to any one of claims 2 to 4.
A space is provided inside the concave portion of the inner member in the radial direction.
A component member constituting another friction fastening device is arranged in the space portion.

First, according to the invention of claim 1,
Lubricating oil is supplied from the inside to the outside in the radial direction through between the seal plate and the vertical wall portion of the inner member by the radial oil passage and the guide oil passage forming the lubricating oil passage, and the inner member. It is guided from one side in the axial direction to the other side along the inner peripheral side of the spline portion of. Thereby, for example, when the spline portion is provided with a plurality of oil holes penetrating the spline portion in the radial direction, the lubricating oil can also be supplied to the friction plate arranged on the other side in the axial direction. ..

As a result, in the friction fastening device in which the position of the radial oil passage for supplying the lubricating oil to the friction plate and the spline portion are offset in the axial direction, the lubricating oil can be supplied to the friction plate by using the seal plate. Can be even.

According to the invention of claim 2.
Since the guide portion of the seal plate is inserted into the recess of the inner member, the lubricating oil supplied from the radial oil passage to the inner member side is connected to the guide portion of the seal plate and the inner peripheral surface of the spline portion of the inner member. In between, it is guided from the other side in the axial direction to one side. As a result, the lubricating oil is supplied to the plurality of friction plates from the other side in the axial direction toward one side, so that the lubricating oil can be evenly supplied to the plurality of friction plates.

According to the invention of claim 3,
By engaging the notch provided in the guide portion of the seal plate with the rib provided in the recess of the inner member, the relative rotation of the seal plate with respect to the inner member is prevented. As a result, when the inner member and the seal plate are in contact with each other, the relative rotation of the seal plate suppresses the obstruction of the flow of the lubricating oil.

According to the invention of claim 4,
By engaging the engaging protrusion of the seal plate with the engaging recess of the piston, the relative rotation of the piston with respect to the seal plate is prevented. Since the seal plate is restrained from rotating relative to the inner member, the relative rotation between the piston and the inner member is suppressed. As a result, for example, when a spring for urging the piston to the release side is arranged between the piston and the seal plate and the inner member, the spring due to the relative rotation of the piston, the seal plate and the inner member. The collapse of the piston is suppressed. As a result, it is possible to suppress problems such as hindering the operation of the piston due to the fall of the spring.

According to the invention of claim 5.
Since the constituent members constituting the other friction fastening device are arranged on the inner peripheral side of the inner member, compared with the case where the inner member and the constituent members of the other friction fastening device are arranged so as to be offset in the axial direction. Therefore, the axial dimension can be compactly configured.

It is a skeleton diagram of the automatic transmission which concerns on embodiment of this invention. It is a fastening table of friction fastening elements of an automatic transmission. It is sectional drawing of the clutch of an automatic transmission and its periphery. It is a single perspective view of a seal plate. It is a single perspective view of a hub member.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is an outline diagram of an automatic transmission according to an embodiment of the present invention. The automatic transmission 10 is connected to a drive source such as an engine without a fluid transmission device such as a torque converter. The automatic transmission 10 is arranged in a transmission case 11 with an input shaft 12 connected to a drive source and arranged on the drive source side (left side in the figure) and on the opposite drive source side (right side in the figure). It has an output shaft 13. The automatic transmission 10 is a vertically installed type for front engine / rear drive vehicles, etc., in which the input shaft 12 and the output shaft 13 are arranged on the same axis.

On the axis of the input shaft 12 and the output shaft 13, from the drive source side, the first, second, third, and fourth planetary gear sets (hereinafter, simply "first, second, third, and fourth gear sets"". PG1, PG2, PG3, PG4 are arranged.

In the transmission case 11, the first clutch CL1 is arranged on the drive source side of the first gear set PG1, the second clutch CL2 is arranged on the drive source side of the first clutch CL1, and the drive source of the second clutch CL2. A third clutch CL3 is arranged on the side. Further, the first brake BR1 is arranged on the drive source side of the third clutch CL3, and the second brake BR2 is arranged on the drive source side of the third gear set PG3 and on the anti-drive source side of the second gear set PG2.

The first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are all single pinion types in which the pinion supported by the carrier directly meshes with the sun gear and the ring gear. The first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 have sun gears S1, S2, S3, S4, ring gears R1, R2, R3, R4, and carriers C1, C2, respectively, as rotating elements. , C3, and C4.

The first gear set PG1 is a double sun gear type in which the sun gear S1 is divided into two in the axial direction. The sun gear S1 has a first sun gear S1a arranged on the drive source side and a second sun gear S1b arranged on the opposite drive source side. The first and second sun gears S1a and S1b have the same number of teeth and mesh with the same pinion supported by the carrier C1. As a result, the first and second sun gears S1a and S1b always rotate in the same rotation.

In the automatic transmission 10, the sun gear S1 of the first gear set PG1, specifically, the second sun gear S1b and the sun gear S4 of the fourth gear set PG4 are always connected, and the ring gear R1 of the first gear set PG1 and the sun gear of the second gear set PG2 are always connected. S2 is always connected, carrier C2 of the second gear set PG2 and carrier C4 of the fourth gear set PG4 are always connected, and carrier C3 of the third gear set PG3 and ring gear R4 of the fourth gear set PG4 are always connected. ..

The input shaft 12 is always connected to the carrier C1 of the first gear set PG1 through between the first sun gear S1a and the second sun gear S1b, and the output shaft 13 is always connected to the carrier C4 of the fourth gear set PG4.

The first clutch CL1 is disposed between the input shaft 12 and the carrier C1 of the first gear set PG1 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect the first clutch CL1. It is arranged between the ring gear R1 of the first gear set PG1 and the sun gear S2 of the second gear set PG2 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect them. The third clutch CL3 is the second gear set. It is arranged between the ring gear R2 of the PG2 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect them.

The first brake BR1 is disposed between the transmission case 11 and the sun gear S1 of the first gear set PG1, specifically, the first sun gear S1a so as to connect and disconnect the first brake BR1. Is disposed between the transmission case 11 and the ring gear R3 of the third gear set PG3 so as to connect and disconnect them.

With the above configuration, the automatic transmission 10 has D as shown in FIG. 2 by combining the engaged states of the first clutch CL1, the second clutch CL2, the third clutch CL3, the first brake BR1, and the second brake BR2. The 1st to 8th speeds in the range and the backward speeds in the R range are formed.

In the automatic transmission 10, the second clutch CL2 corresponds to the friction fastening device of the automatic transmission according to the present invention. Hereinafter, the second clutch CL2 will be described.

As shown in FIG. 3, the second clutch CL2 is housed in a transmission case 11 formed in a substantially cylindrical shape, is connected to the sun gear S3 of the third gear set PG3, and is connected to the first, second, and third clutches. One of the pair of internal and external rotating members of CL1, CL2, and CL3 is arranged on the outer peripheral side of the integrated power transmission member 14.

The power transmission member 14 is arranged on the outer peripheral side of the power transmission member 15 that connects the sun gear S1 of the first gear set PG1 and the rotating member of the first brake BR1, and the power transmission member 15 is the outer circumference of the input shaft 12 of the transmission. It is located on the side.

The second clutch CL2 is a hub member 20 as an inner member coupled to the power transmission member 14, and a ring gear R1 of the first gear set PG1 and a sun gear S2 of the second gear set PG2 arranged on the opposite drive source side of the hub member 20. On the anti-drive source side of the drum member 30 as an outer member, the plurality of friction plates 40 arranged axially between the hub member 20 and the drum member 30, and the plurality of friction plates 40. It has a piston 50 that is arranged and fastens a plurality of friction plates 40.

The second clutch CL2 has a fastening hydraulic chamber 61 to which fastening hydraulic oil for urging the piston 50 in the fastening direction is supplied radially inside the hub member 20. Further, the second clutch CL2 has a centrifugal balance chamber 62 arranged so as to face the fastening hydraulic chamber 61 with the piston interposed therebetween.

The second clutch CL2 also includes a plurality of return springs 71 ... 71 that exert an urging force on the piston 50 in the release direction as an urging member that urges the piston 50 radially inside the hub member 20.

As shown in FIGS. 3 and 4, the hub member 20 of the second clutch CL2 has a spline portion 21 formed in a cylindrical shape and a plurality of friction plates 40 are spline-engaged on the outer peripheral side thereof, and a spline portion 21. A vertical wall portion 22 extending from the inner peripheral side to a substantially disk shape, and a cylindrical boss portion 23 extending axially from the inner peripheral end portion of the vertical wall portion 22 and being connected to the power transmission member 14. It has.

The inner peripheral side of the spline portion 21 of the hub member 20 is recessed along the spline portion 21 on the anti-drive source side (the other side in the claims) in the axial direction and the drive source side (one side in the claims). ) Is provided with a recess 24. The recess 24 extends in the circumferential direction and is formed in an annular shape. The recess 24 extends axially on the inner peripheral side of the spline portion 21 to a position where the friction plate arranged on the opposite drive source side is arranged when the plurality of friction plates 40 are in the fastened state.

The outer peripheral surface 24a of the recess 24 is inclined so that the drive source side is located above the anti-drive source side. The inner peripheral surface 24b of the recess 24 is formed so as to be inclined so that the anti-drive source side is located above the drive source side. A plurality of ribs 25 ... 25 extending in the radial direction are provided between the outer peripheral surface 24a of the recess 24 and the inner peripheral surface 24b of the recess 24.

The drum member 30 of the second clutch CL2 has a spline portion 31 which is formed in a cylindrical shape and on the inner peripheral side thereof, a plurality of friction plates 40 are spline-engaged. In the present embodiment, the spline portion 31 extends from the spline portion 31 toward the anti-drive source side in the axial direction and is connected to the ring gear R1 of the first gear set PG1 and the sun gear S2 of the second gear set PG2 (FIG. It is integrally formed with the power transmission unit 32 connected to (see 1).

The piston 50 of the second clutch CL2 is located on the drive source side of the plurality of friction plates 40, and the pressing portion 51 that presses the plurality of friction plates 40 toward the anti-drive source side in the axial direction and the pressing portion 51 It is provided with an extension portion 52 extending inward in the radial direction.

Axial drive between the bulging portion 53, which bulges toward the drive source side and the anti-drive source is recessed, and the pressing portion 51 and the bulging portion 53, on the radial inner peripheral side of the extension portion 52. It has an eaves portion 54 extending from the source side to the anti-drive source side. On the anti-drive source side of the bulging portion 53, a recessed portion 55 facing the vertical wall portion 22 of the hub member 20 extends in the circumferential direction and is formed in an annular shape.

The fastening hydraulic chamber 61 of the second clutch CL2 is defined between the piston 50 and the fastening hydraulic chamber component 80 arranged on the outer peripheral side of the bulging portion 53 of the piston 50.

The fastening hydraulic chamber component 80 extends from the vertical wall portion 81 facing the drive source side surface of the bottom surface 55a of the bulging portion 53 of the piston 50 and the outer peripheral end portion of the vertical wall portion 81 to the anti-drive source side. An outer cylinder portion 82 and an inner cylinder portion 83 extending from an end portion on the inner peripheral side of the vertical wall portion 81 to the anti-drive source side are provided.

The fastening hydraulic chamber component 80 is press-fitted into the boss portion 23 of the hub member 20. The fastening hydraulic chamber component 80 is prevented from coming off from the boss portion 23 of the hub member 20 by, for example, a snap ring or the like.

The outer cylinder portion 82 of the fastening hydraulic chamber component 80 is arranged so as to overlap with the upper surface portion 53a of the bulging portion 53 of the piston 50 in the axial direction. A seal member 91 is arranged between the outer cylinder portion 82 and the upper surface portion 53a of the bulging portion 53. The inner cylinder portion 83 of the fastening hydraulic chamber component 80 is formed so as to extend from the inner end portion of the piston 50 toward the anti-drive source side in the axial direction. A seal 92 is arranged between the inner end portion of the piston 50 and the inner cylinder portion 83 of the fastening hydraulic chamber component 80.

The end portion 83a of the inner cylinder portion 83 of the fastening hydraulic chamber component 80 on the opposite drive source side in the axial direction is formed shorter than the axial position of the vertical wall portion 22 of the hub member 20. The inner cylinder portion 83 of the fastening hydraulic chamber component 80 has an oil supply hole extending in the axial direction from the shaft member on the inner peripheral side of the second clutch CL2 to supply hydraulic oil for fastening to the fastening hydraulic chamber 61. 84 is provided. The supply oil passage for supplying hydraulic oil will be described later.

The centrifugal balance chamber 62 of the second clutch CL2 is defined as a whole by the piston 50 and the seal plate 100 arranged to face the surface of the piston 50 on the anti-drive source side.

The seal plate 100 is arranged to face each other between the extending portion 52 of the piston 50 and the vertical wall portion 22 of the hub member 20. As shown in FIGS. 3 and 5, the seal plate 100 has a substantially disk-shaped main body 101 and a cylindrical guide portion extending from the upper end of the main body 101 in the axial direction from the drive source side to the anti-drive source side. 103 and.

The main body 101 is arranged so as to be in contact with the vertical wall 22 of the hub member 20. A step for fitting the seal plate 100 into the recess 24 of the hub member 20 (the surface on the inner peripheral side of the recess 24 of the hub member 20) in the radial intermediate portion of the surface of the main body 101 on the opposite drive source side. A portion 101a is provided.

On the surface of the main body 101 on the drive source side, three engaging protrusions 102 protruding toward the drive source in the axial direction are provided at equal intervals in the circumferential direction. The recessed portion 55 of the piston 50 is provided with a plurality of land portions 57 ... 57 that partition the recessed portion 55 in the circumferential direction, arranged at equal intervals in the circumferential direction. Each land portion 57 is formed with an engaging concave portion 58 that is recessed on the drive source side to engage with the engaging convex portion 102 of the seal plate 100. In the present embodiment, the land portion 57 and the engaging recesses 58 are provided at three locations at equal intervals in the circumferential direction.

By engaging each engaging convex portion 102 of the seal plate 100 with each engaging concave portion 58 of the piston 50, the relative rotation of the seal plate 100 with respect to the piston 50 is regulated.

The guide portion 103 extends from the drive source side (one side) in the axial direction to the anti-drive source side (the other side) along the inner peripheral surface of the spline portion 21 of the hub member 20. The tip portion 103a of the guide portion 103 is provided with a plurality of notched portions 104 ... 104 at different positions in the circumferential direction. The guide portion 103 is inserted into the recess 24 of the spline portion 21 of the hub member 20.

Each notch 104 of the guide 103 is provided at a position corresponding to each rib 25 of the recess 24 of the hub member 20, and is engaged with each rib 25. As a result, the relative rotation between the hub member 20 and the seal plate 100 is restricted.

The upper end of the main body 101 of the seal plate 100 is provided so as to extend to a position corresponding to the radial position of the lower surface 54a of the eaves 54 of the piston 50. A seal member 93 is arranged between the upper end of the main body 101 of the seal plate 100 and the lower surface 54a of the eaves 54 of the piston 50.

As described above, the centrifugal balance chamber 62 is composed of a surface of the extension portion 52 of the piston 50 on the opposite drive source side, a lower surface 54a of the eaves portion 54, and a surface of the seal plate 100 on the drive source side of the main body portion 101. Has been done.

A plurality of return springs 71 ... 71 of the second clutch CL2 are provided in the centrifugal balance chamber 62. Each return spring 71 is attached to each protrusion 56 extending from the bottom surface 55a of the recessed portion 55 of the piston toward the axially opposite drive source side. A plurality of protrusions 56 ... 56 are provided side by side in the circumferential direction. The end of each return spring 71 on the drive source side is supported by the bottom surface 55a of the piston 50, and the end on the anti-drive source side is on an annular spring seat 72 arranged on the surface of the seal plate 100 on the drive source side. It is supported. The piston 50 is urged to the release side by a plurality of return springs 71 ... 71.

As described above, as a result of restricting the relative rotation of the seal plate 100 and the piston 50 and the relative rotation of the seal plate 100 and the hub member 20, the relative rotation of the piston 50 and the hub member 20 is prevented. To. As a result, the return spring 71 arranged between the hub member 20 and the piston 50 is prevented from falling. As a result, it is possible to suppress problems such as hindering the operation of the piston 50 due to the fall of the return spring 71.

Next, the fastening hydraulic chamber 61 of the second clutch CL2, the fastening hydraulic chamber oil passage 61A for supplying hydraulic oil to the centrifugal balance chamber 62, and the centrifugal balance chamber oil passage 62A will be described.

The fastening hydraulic chamber oil passage 61A includes a fastening chamber axial oil passage 61a communicated with a control valve (not shown) provided in the transmission case 11, and the fastening chamber axial oil passage 61a and the fastening hydraulic chamber 61. It is provided with radial oil passages 61b, 61c, 84 for fastening to communicate with each other.

The fastening chamber axial oil passage 61a is fixed to the transmission case 11 and has a first sleeve member 11a having a groove 11c that extends radially outward and has a diameter of the first sleeve member 11a. It is formed between the second sleeve member 11b that is press-fitted outward in the direction. The fastening radial oil passages 61b and 61c are bossed so as to communicate with the first fastening radial oil passage 61b that penetrates the second sleeve member 11b in the radial direction and the first fastening radial oil passage 61b. It has a second radial oil passage 61c for fastening that penetrates 23 in the radial direction, and an oil supply hole 84 in the inner cylinder portion 83 of the fastening hydraulic chamber component 80.

As a result, the hydraulic oil for fastening passes through the fastening chamber axial oil passage 61a, the first fastening radial oil passage 61b, the second fastening radial oil passage 61c, and the oil supply hole 84. , Is supplied to the fastening hydraulic chamber 61.

Similar to the fastening hydraulic chamber oil passage 61A, the centrifugal balance chamber oil passage 62A includes a centrifugal balance chamber axial oil passage 62a communicated with a control valve (not shown) provided in the transmission case 11 and the centrifugal balance chamber. It is provided with radial oil passages 62b and 62c for a centrifugal balance chamber that communicate with the axial oil passage 62a, and an inflow portion G1 that communicates the radial oil passages 62b and 62c for the centrifugal balance chamber and the centrifugal balance chamber 62. There is.

The axial oil passage 62a for the centrifugal balance chamber is fixed to the transmission case 11 and opens radially outward extending in the axial direction at a circumferential position different from the axial oil passage 61a for the fastening chamber (not shown). ), And the second sleeve member 11b press-fitted to the outside in the radial direction of the first sleeve member 11a.

The radial oil passages 62b and 62c for the centrifugal balance chamber are the radial oil passages 62b for the first centrifugal balance chamber and the radial oil passages 62b for the first centrifugal balance chamber so as to penetrate the second sleeve member 11b in the radial direction. It has a second centrifugal balance chamber radial oil passage 62c that penetrates the boss portion 23 in the radial direction so as to communicate with the boss portion 23.

The inflow portion G1 is formed between the end portion 83a of the inner cylinder portion 83 of the fastening hydraulic chamber component 80, the base end portion of the vertical wall portion 22 of the hub member 20, and the lower end portion 101b of the main body portion 101 of the seal plate 100. Has been done.

As a result, the hydraulic oil for the centrifugal balance chamber flows into the axial oil passage 62a for the centrifugal balance chamber, the radial oil passage 62b for the first centrifugal balance chamber, and the radial oil passage 62c for the second centrifugal balance chamber. It is supplied to the centrifugal balance chamber 62 through the portion G1.

In addition to the above configuration, the present invention includes a lubricating oil supply passage X for supplying lubricating oil to the plurality of friction plates 40 of the second clutch CL2. The lubricating oil supply passage X is provided between the seal plate 100 and the hub member 20. The seal plate 100 constituting the lubricating oil supply passage X and the hub member 20 will be described below.

The lubricating oil supply passage X communicates with the centrifugal balance chamber 62 and extends along the plurality of radial oil passages X1 ... X1 for lubricating oil extending from the inside to the outside in the radial direction and the inner peripheral side of the spline portion 21 of the hub member 20. It includes guide oil passages X2 and X3 that guide the lubricating oil from one side in the axial direction to the other side, and a plurality of oil holes 29 formed in the spline portion 21 of the hub member 20.

As shown in FIG. 3, the radial oil passage X1 for lubricating oil includes a radial groove portion 26 provided on the surface of the vertical wall portion 22 of the hub member 20 on the seal plate 100 side, and a main body portion 101 of the seal plate 100. It is formed by a surface on the hub member 20 side.

Each radial groove portion 26 is formed so as to extend radially inward from the end portion of the recess 24 of the hub member 20 on the drive source side to a position on the inner peripheral side of the inner end of the main body portion 101 of the seal plate 100. .. As a result, the radial groove portion 26 is covered as a whole by the main body portion 101 of the seal plate 100, while the centrifugal balance chamber 62 and the radial oil passage X1 for lubricating oil are provided at the inner end portion of the radial groove portion 26. A gap G2 to be communicated is formed.

As shown in FIG. 4, at the radial inner end of each radial groove 26, a circumferential groove 27 extending on both sides in the circumferential direction with the radial groove 26 interposed therebetween is formed. The centrifugal balance chamber 62 communicates with the radial groove portion 26 of the hub member 20 via the circumferential groove 27.

The guide oil passages X2 and X3 are formed by the guide portion 103 of the seal plate 100 being inserted into the recess 24 of the hub member 20. The guide oil passages X2 and X3 include a first guide oil passage X2 and a second guide oil passage X3. The first guide oil passage X2 is formed between the inner peripheral surface 103b of the guide portion 103 of the seal plate 100 and the inner peripheral surface 24b of the recess 24 of the hub member 20. The second guide oil passage X3 is formed between the outer peripheral surface 103c of the guide portion 103 of the seal plate 100 and the inner peripheral surface 21a (outer peripheral surface 24a of the recess) of the spline portion 21 of the hub member 20.

Further, in the present embodiment, as shown in FIG. 4, a groove 28 extending from the bottom 24c of the recess 24 toward the drive source side is formed in the inner peripheral portion of the spline portion 21 of the hub member 20 in the axial direction. .. A plurality of grooves 28 are provided at intervals in the circumferential direction of the hub member 20.

Each oil hole 29 is formed so as to penetrate each groove 28 and the tooth bottom 21b of the spline portion 21 in the radial direction. In the plurality of grooves 28 arranged in the circumferential direction, the plurality of oil holes 29 are arranged side by side in the circumferential direction.

The first oil hole 29a is formed in the first groove 28a, the second oil hole 29b is formed in the second groove 28b, the third oil hole 29c is formed in the third groove 28c, and the fourth oil hole 29d. Is formed in the fourth groove 28d. The first to fourth oil holes 29a to 29d are arranged side by side at different positions in the axial direction.

The axial positions of the first to fourth oil holes 29a to 29d are provided corresponding to the positions where the facings are arranged in the fastened state of the friction plates. The first to fourth oil holes 29a to 29d are repeatedly formed in the circumferential direction.

The inner peripheral surface 21a (outer peripheral surface 24a of the recess 24) of the spline portion 21 of the hub member 20 is inclined outward in the radial direction toward the drive source side in the axial direction. Similarly, each groove 28 is inclined outward in the radial direction toward the drive source side. In the present embodiment, the hub member 20 is formed by casting (for example, an aluminum die casting method), and the die cutting direction is set to the axial direction. Therefore, the inclination of the recess 24 and the groove 28 of the hub member 20 can be easily formed by the draft of the mold.

The supply of lubricating oil to the friction plate 40 in the second clutch CL2 having the above configuration will be described.

As shown in FIG. 3, the lubricating oil supplied into the centrifugal balance chamber 62 is supplied from the inflow portion G1 to the lubricating radial oil passage X2 via the gap G2. The lubricating oil supplied to the lubricating radial oil passage X1 reaches the inner peripheral surface 24b of the recess 24 of the hub member 20.

Next, the lubricating oil supplied to the recess 24 of the hub member 20 is the first guide oil passage X2 (between the inner peripheral surface 24b of the recess 24 and the inner peripheral side surface 103b of the guide portion 103 of the seal plate 100). Through, it reaches the bottom 24c of the recess 24.

The lubricating oil that has reached the bottom 24c of the recess 24 of the hub member 20 moves radially outward by centrifugal force and reaches the outer peripheral surface 24a of the recess 24 of the hub member 20. The lubricating oil that has reached the outer peripheral surface 24a of the recess 24 is held in the groove 28 by the plurality of grooves 28 on the outer peripheral surface 24a of the recess 24 acting as a weir. Since the groove 28 is inclined outward in the radial direction toward the drive source side in the axial direction, the lubricating oil held in the groove 28 moves to the drive source side by centrifugal force.

The lubricating oil that moves in the axial direction in each groove 28 moves to the outer peripheral side of the hub member 20 through each oil hole 29 and is supplied to the friction plate 40. As a result, the friction plate 40 is lubricated and cooled by the lubricating oil.

As described above, the lubricating oil is radially inside through between the seal plate 100 and the vertical wall portion 22 of the hub member 20 by the radial oil passages X1 and the guide oil passages X1 and X2 constituting the lubricating oil passage X. Supplied outward from.

The lubricating oil supplied to the guide oil passages X2 and X3 is guided from the counter-drive source side in the axial direction to the drive source side along the inner peripheral side of the spline portion 21 of the hub member 20. As a result, the lubricating oil can be supplied to the friction plate 40 arranged on the anti-drive source side in the axial direction through the plurality of oil holes 29 ... 29 provided in the spline portion 21.

Therefore, in the friction fastening device CL2 in which the position of the radial oil passage X1 for supplying the lubricating oil to the friction plate 40 and the spline portion 21 are offset in the axial direction, the seal plate 100 is used to reach the friction plate 40. Lubricating oil supply can be even.

Since the guide portion 103 of the seal plate 100 is inserted into the recess 24 of the hub member 20, the lubricating oil supplied from the radial oil passage X1 to the hub member 20 side is radially inside the guide portion 103 of the seal plate 100. It passes between the surface 103b and the inner peripheral surface 24b of the recess 24 of the hub member 20, and is guided to the anti-drive source side of the hub member 20. The lubricating oil guided to the opposite drive source side of the hub member 20 is the radial outer surface 103b of the guide portion 103 of the seal plate 100 and the inner peripheral surface 21a of the spline portion 21 of the hub member 20 (outer peripheral surface 24a of the recess 24). ), It is guided from the anti-drive source side to the drive source side.

As a result, the lubricating oil is supplied to the plurality of friction plates 40 from the oil holes 29 ... 29 provided in the spline portion 21 of the hub member 20 from the anti-drive source side to the drive source side, so that the plurality of friction plates Lubricating oil can be evenly supplied to 40.

Further, in the present embodiment, as shown in FIG. 3, a space portion S is provided inside the recess 24 of the hub member 20 in the radial direction. In the space portion S, hydraulic chambers 161 and 162 of the first clutch CL1 are arranged as components constituting another friction fastening device. Here, the first clutch CL1 will be described. In the present embodiment, the drum member 130 of the first clutch CL1 is integrally formed with the hub member 20 of the second clutch CL2 by the aluminum die casting method.

Like the second clutch CL2, the first clutch CL1 has a hub member 120, a drum member 130, a plurality of friction plates 140, a piston 150 that presses the plurality of friction plates 140, and the piston 150 in the fastening direction. It includes a fastening hydraulic chamber 161 for supplying urging hydraulic oil, and a centrifugal balance chamber 162 arranged opposite to the fastening hydraulic chamber 161 with a piston interposed therebetween.

The fastening hydraulic chamber 161 of the first clutch CL1 is provided on the surface of the vertical wall portion 22 of the hub member 20 of the second clutch CL2 on the opposite drive source side, the boss portion 23, and the inside of the concave portion 24 of the hub member 20 in the radial direction. It is defined by a portion and a bulging portion 153 of the piston 150 of the first clutch CL1.

The centrifugal balance chamber 162 of the first clutch CL1 includes a surface of the piston 150 of the first clutch CL1 on the anti-fastening chamber side, an upper cylindrical portion 153a of the bulging portion 153 of the piston 150, and a boss portion 23. , It is defined between the seal plate 200 arranged between the boss portion 23 and the upper cylindrical portion 153a.

As described above, in the space portion S inside the concave portion 24 of the second clutch CL2 in the radial direction, the fastening hydraulic chamber 161 of the first clutch CL1, the centrifugal balance chamber 162, the bulging portion 153 inside the radial direction of the piston 150, and the like are provided. Have been placed.

As a result, the axial dimensions can be made more compact than in the case where the hub member 20 of the second clutch CL2 and the hydraulic chambers 161 and 162 of the first clutch CL1 are arranged so as to be offset in the axial direction. ..

The present invention is not limited to the configuration described in the above embodiment, and various modifications can be made.

For example, in the present embodiment, the radial groove portion 26 constituting the radial oil passage X1 is provided on the vertical wall portion 22 of the hub member 20, but the radial groove portion is the main body portion of the seal plate 100. It may be provided in 101, or both may be provided with a radial groove portion.

For example, in the present embodiment, in order to suppress the relative rotation between the seal plate 100 and the piston 50, the seal plate 100 is provided with an engaging convex portion, and the piston 50 is provided with an engaging concave portion. The engaging convex portion may be provided on the piston 50, and the engaging concave portion may be provided on the seal plate 100.

For example, in the present embodiment, the component of another friction fastening device arranged in the space S inside the recess 24 of the hub member 20 of the second clutch CL2 is a hydraulic chamber. A member, a drum member, and a friction plate may be arranged.

Further, for example, in the present embodiment, the hub member 20 of the second clutch CL2 and the drum member 130 of the first clutch CL1 are integrally formed by casting, but the hub of the second clutch CL2 has been described. The member 20 and the drum member 130 of the first clutch CL1 may be press-molded.

Further, for example, in the present embodiment, each oil hole 29 of the hub member 20 of the second clutch CL2 is formed in a direction perpendicular to the axial direction, but each oil hole has an obtuse angle in the axial direction. It may be formed so as to be inclined. In this case, it is preferable to incline so that the downstream side of the flow of the lubricating oil supplied to the guide oil passage X3 of the oil hole is located upward.

Further, for example, in the present embodiment, the inner peripheral surface 24b of the recess 24 of the hub member 20 of the second clutch CL2 is formed so as to be inclined so that the anti-drive source side is located above the drive source side. However, the inner peripheral surface 24b of the recess 24 may be formed parallel to the axis.

As described above, according to the present invention, the friction plate is sufficient in the friction fastening device of the automatic transmission in which the position of the oil hole for supplying the lubricating oil to the friction plate and the spline portion are offset in the axial direction. Since it supplies various lubricating oils, it may be suitably used in this kind of manufacturing technology field.

10 Automatic transmission 20 Hub member (inner member)
21 Spline portion 22 Vertical wall portion 24 Recession 24a Outer peripheral surface of the recess 24b Inner peripheral surface of the recess 25 Rib 30 Drum member (outer member)
40 Multiple friction plates 50 Piston 51 Pressing part 52 Extension part 58 Engagement recess 61 Engagement hydraulic chamber 62 Centrifugal balance chamber 100 Seal plate 102 Engagement convex part 103 Guide part 103a Tip part of guide part 104 Notch part CL2 No. 2 clutch (friction fastening device)
161 and 162 Flood control chamber for fastening, centrifugal balance chamber (requires configuration to configure other friction fastening devices)
X Lubricating oil passage X1 Radial oil passage X2, X3 Guide oil passage

Claims (5)

An inner member, an outer member, a plurality of friction plates arranged between the inner member and the outer member, a piston for fastening the plurality of friction plates, and a hydraulic oil for urging the piston in the fastening direction. Has a fastening hydraulic chamber to which the piston is supplied, and a centrifugal balance chamber to which the hydraulic oil for urging the piston in the release direction is supplied.
An automatic transmission in which the centrifugal balance chamber is defined by an extension portion extending inward from a pressing portion that presses the friction plate on the piston and a seal plate arranged to face the extension portion. Friction fastening device
The inner member
A cylindrical spline portion in which the plurality of friction plates are spline-engaged on the outer peripheral side thereof,
It is provided with a vertical wall portion extending from the spline portion toward the inner peripheral side and arranged on the anti-centrifugal balance chamber side of the seal plate.
The lubricating oil passage for supplying the lubricating oil to the plurality of friction plates is formed by the seal plate and the inner member.
The lubricating oil passage communicates with the radial oil passage for supplying lubricating oil from the radial inside to the outside between the vertical wall portion of the inner member and the seal plate, and also communicates with the radial oil passage. It is characterized by having a guide oil passage for guiding lubricating oil from one side in the axial direction to the other side along the inner peripheral side of the spline portion of the inner member by a guide portion provided on the seal plate. Lubrication fastening device for automatic transmissions. The inner peripheral side of the spline portion of the inner member is provided with a recess recessed from one side in the axial direction to the other side along the spline portion.
The guide portion of the seal plate is formed so as to extend from one side in the axial direction to the other side.
The friction fastening device for an automatic transmission according to claim 1, wherein the guide oil passage is formed by inserting a guide portion of the seal plate into a recess of the inner member. Ribs extending in the radial direction are provided between the inner peripheral surface and the outer peripheral surface of the concave portion of the inner member.
A notch is provided at the tip of the guide portion of the seal plate.
The friction fastening device for an automatic transmission according to claim 2, wherein the rib and the notch are engaged with each other. One of the seal plate and the vertical wall portion of the piston is provided with an engaging convex portion, and the other is provided with an engaging concave portion.
The friction fastening device for an automatic transmission according to claim 3, wherein the engaging convex portion and the engaging concave portion are engaged with each other. A space is provided inside the concave portion of the inner member in the radial direction.
The friction fastening device for an automatic transmission according to any one of claims 2 to 4, wherein a component member constituting another friction fastening device is arranged in the space portion.

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