JP2018179272A - Supporting structure of retaining plate in automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten a length in a rotating shaft direction, of an automatic transmission.SOLUTION: In a supporting structure 1 of a retaining plate 45 in an automatic transmission in which a brake 4 disposed in a transmission case 10, has a piston 43 for pressing an inner diameter-side friction plate 41 and an outer diameter-side friction plate 42 in a rotating shaft X direction, and a retaining plate 45 on which the pressing force of the piston 43 is applied through the inner diameter-side friction plate 41 and the outer diameter-side friction plate 42, and a clutch drum 37 rotatable about a rotating shaft X is disposed in a state that a peripheral wall portion 38 of the clutch drum 37 is opposed to the retaining plate 45 at a side opposite to the piston 43 of the retaining plate 45 in the rotating shaft X direction, a washer 7 is disposed between a tip 38a of a peripheral wall portion 38 as an opposite part to the retaining plate 45, of the clutch drum 37 and the retaining plate 45.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a support structure of a retaining plate in an automatic transmission.

  In an automatic transmission for a vehicle, a friction engagement device (clutch and brake) having a plurality of friction plates is provided on a transmission path of a rotational drive force input from a drive source (for example, Patent Document 1).

Japanese Patent Application Laid-Open No. 05-071598

  As shown in FIG. 4, the brake 4, which is a friction fastening device of this type, rotates in the transmission case 10 with the inner friction plates 41 and the outer friction plates 42 alternately arranged in the rotation axis X direction. And a piston 43 movably provided in the direction of the axis X.

The radially inner friction plate 41 is spline-fitted to the outer periphery of the ring gear 51 of the planetary gear mechanism 5, and the radially inner friction plate 41 moves in the direction of the rotation axis X in a state where relative rotation with the ring gear 51 is restricted. It is possible.
The radially outer friction plate 42 is spline-fitted to the inner periphery of the transmission case 10, and the relative diameter between the radially outer friction plate 42 and the transmission case 10 is restricted. It is provided to be movable.

A retaining plate 45 positioned by a snap ring 48 is spline fitted on the inner periphery of the transmission case 10, and the inner friction plate 41 and the outer friction plate 42 are in the direction away from the piston 43. The movement range is specified.
Therefore, when the piston 43 is displaced in the direction of the rotation axis X, the radially inner friction plate 41 and the radially outer friction plate 42 are sandwiched between the piston 43 and the retaining plate 45, and the radially inner friction plate 41 and the outer diameter The relative rotation around the rotation axis X with the side friction plate 42 is regulated according to the pressing force of the piston 43.
When the relative rotation of the inner friction plate 41 and the outer friction plate 42 about the rotation axis X is completely restricted, the rotation of the ring gear 51 in which the inner friction plate 41 is spline-fitted is restricted.

Here, the pressing force of the piston 43 acts on the retaining plate 45 via the inner friction plate 41 and the outer friction plate 42.
However, since the snap ring 48 for positioning the retaining plate 45 is locked to the outer diameter side of the retaining plate 45, the inner diameter side of the retaining plate 45 is a direction away from the piston 43 rather than the outer diameter side. Can be greatly displaced.

  Therefore, as shown in FIG. 4, when the other rotating body (in FIG. 4, the peripheral wall 38 of the clutch drum 37) is located on the opposite side of the retaining plate 45 to the piston 43, in the rotational axis X direction. The inner diameter side of the displaced retaining plate 45 may interfere with other rotating bodies.

  Then, the rotation of the other rotating body is blocked by the retaining plate 45. Therefore, in the conventional automatic transmission, a gap C1 for avoiding interference with the displaced retaining plate is secured between the retaining plate and the rotating body, and the length of the automatic transmission in the rotational axis direction However, it has become long by the part | minute which provides the clearance gap C1.

  Therefore, it is required to be able to further shorten the length of the automatic transmission in the rotation shaft direction.

The present invention
The friction fastening device provided in the transmission case is
A piston that presses a plurality of friction plates in the rotational axis direction;
And a retaining plate which is provided on the side of the friction plate opposite to the piston in the rotational axis direction, and the pressing force of the piston acts through the plurality of friction plates.
In a supporting structure of a retaining plate in an automatic transmission, wherein a rotating body rotatable around the rotating shaft is disposed on the side opposite to the piston of the retaining plate in the rotating shaft direction. There,
A washer is interposed between the portion of the rotating body facing the retaining plate and the retaining plate.

According to the present invention, the displacement of the retaining plate in the direction away from the piston is restricted by the washer provided between the retaining plate and the rotating body.
Since the washer is allowed to rotate relative to the rotating body, the rotation of the rotating body is not impeded even if the retaining plate pressed by the pressure of the piston presses against the washer.
Accordingly, since the snap ring for positioning the retaining plate can be omitted, the length of the automatic transmission in the rotational axis direction can be shortened by the omission of the snap ring.

It is a figure explaining the support structure of a retaining plate. It is a figure explaining the support structure of a retaining plate. It is a figure explaining the support structure of the retaining plate concerning a modification. It is a figure explaining the support structure of the retaining plate concerning a prior art example.

  Hereinafter, an embodiment of the present invention will be described by taking an automatic transmission adopting the support structure 1 of the retaining plate 45 as an example.

FIG. 1 is a view for explaining the support structure 1 of the retaining plate 45. As shown in FIG.
FIG. 1A is a cross-sectional view around a friction engagement device (clutch 3, brake 4) provided in an automatic transmission for a vehicle. (B) of FIG. 1 is an enlarged view of a region A in (a) of FIG.
FIG. 2 is a view for explaining the support structure 1 of the retaining plate 45 and is a view schematically showing a cross section B-B in FIG. 1 (a).
In FIG. 2, a part of the washer 7 is cut away to show a recess 383 (bottom wall 383 b) provided in the peripheral wall 38 of the clutch drum 37. Furthermore, an outer diameter side friction plate 32 spline-fitted to the inner periphery of the peripheral wall portion 38 is shown by an imaginary line.

  As shown in FIG. 1, in the transmission case 10 of the automatic transmission, a plurality of friction coupling devices (for example, the clutch 3 and the brake 4) are provided on the transmission path of the rotational driving force input from a driving source not shown. Is provided.

[Brake 4]
The brake 4 includes an inner friction plate 41, an outer friction plate 42, and a piston 43.

The radially inner friction plate 41 is provided on the outer periphery of the ring gear 51 of the planetary gear mechanism 5 by spline fitting.
Each of the radially inner friction plates 41 is provided movable in the direction of the rotation axis X in a state in which relative rotation with the ring gear 51 in the circumferential direction around the rotation axis X is restricted.

The outer diameter side friction plate 42 is provided by spline fitting on the inner periphery of the transmission case 10.
Each of the outer diameter side friction plates 42 is provided movably in the rotation axis X direction in a state in which relative rotation with the transmission case 10 in the circumferential direction around the rotation axis X is restricted.

The dish plate 44 and the retaining plate 45 are spline fitted on the inner periphery of the transmission case 10, and the friction plate 41 on the inner side and the outer side between the dish plate 44 and the retaining plate 45 Friction plates 42 are alternately arranged.
The inner diameter side friction plate 41 and the outer diameter side friction plate 42 are provided such that the outer diameter side of the inner diameter side friction plate 41 and the inner diameter side of the outer diameter side friction plate 42 overlap when viewed from the rotation axis X direction. .

The pressing portion 431 of the piston 43 is positioned on one side in the rotation axis X direction where the dish plate 44 is positioned, as viewed from the inner diameter side friction plate 41 and the outer diameter side friction plate 42.
The piston 43 is provided movably in the rotation axis X direction in a recess 101 provided in the transmission case.
On the outer diameter side of the piston 43, a pressing portion 431 protruding toward the planetary gear mechanism 5 is provided. The pressing portion 431 extends along an imaginary line Ln parallel to the rotation axis X, and the pressing portion 431 has a tapered shape in which the thickness in the radial direction becomes thinner toward the tip end side.

An imaginary line Ln passing through the center of the pressing portion 431 in the radial direction intersects a region where the outer diameter side of the inner friction plate 41 and the inner diameter side of the outer friction plate 42 overlap.
The tip end of the pressing portion 431 is in contact with the inner diameter side of the dish plate 44 from the direction of the imaginary line Ln.

In the recess 101 of the transmission case 10, an oil chamber S1 is formed between the ring-shaped base 432 of the piston 43 and the side wall 102 on the transmission case 10 side.
The hydraulic pressure of the piston 43 is supplied to the oil chamber S1 via an oil passage (not shown).
When the hydraulic pressure is supplied to the oil chamber S1, the piston 43 pushed by the hydraulic pressure moves in a direction away from the side wall 102 (right direction in (a) of FIG. 1) to retain the dish plate 44. It is pressed against the plate 45 side.

As described above, the imaginary line Ln at which the pressing portion 431 of the piston 43 is located intersects a region where the outer diameter side of the inner friction plate 41 and the inner diameter side of the outer friction plate 42 overlap.
The radially inner friction plate 41 and the radially outer friction plate 42 are displaceable in the rotational axis X direction.
Furthermore, in view of the inner friction plate 41 and the outer friction plate 42, the retaining plate 45, which is located on the opposite side of the piston 43, moves away from the piston 43 by the washer 7 described later (in FIG. Movement is restricted.

Therefore, when the pressing portion 431 of the piston 43 presses the dish plate 44 to the retaining plate 45 side, the inner friction plate 41 and the outer friction plate 42 are gripped between the dish plate 44 and the retaining plate 45 Be done.
Then, the relative rotation of the inner friction plate 41 and the outer friction plate 42 about the rotation axis X is restricted in accordance with the pressing force applied from the piston 43.

  Then, when relative rotation between the inner friction plate 41 and the outer friction plate 42 is completely restricted, the outer friction plate 42 is spline-fitted to the inner periphery of the transmission case 10, and the inner diameter side Since the friction plate 41 is spline-fitted to the outer periphery of the ring gear 51 of the planetary gear mechanism 5, rotation of the ring gear 51 about the rotation axis X is blocked.

  The pressing force of the piston 43 acts on the retaining plate 45 through the region located on the imaginary line Ln in the dish plate 44, the inner friction plate 41, and the outer friction plate 42.

[Clutch 3]
In the transmission case 10, a clutch 3 is provided at a position adjacent to the planetary gear mechanism 5. The clutch 3 is on the opposite side to the piston 43 (in the rotational axis X direction) as viewed from the planetary gear mechanism 5. Provided on the other side).

  The clutch 3 has an inner diameter friction plate 31, an outer diameter friction plate 32, and a piston 33.

The radially inner friction plate 31 is provided on the outer periphery of the clutch hub 30 by spline fitting, and the clutch hub 30 is coupled to the carrier 52 of the planetary gear mechanism 5 so as to be integrally rotatable.
The outer diameter side friction plate 32 is provided by spline fitting on the inner periphery of the peripheral wall portion 38 of the clutch drum 37.
The clutch drum 37 has a cylindrical peripheral wall 38 and a bottom wall 39 extending radially inward from one end of the peripheral wall 38 in the rotational axis direction. In cross section, the clutch drum 37 has a bottomed cylindrical shape, and the clutch drum 37 is provided with an opening directed to the planetary gear mechanism 5 side.

  As shown in FIG. 2, the circumferential wall 38 has a spline peak 381 located on the outer diameter side and a spline valley 382 located on the inner diameter side in the circumferential direction around the rotation axis X when viewed from the rotation axis X direction. The splines are formed along the axial direction of the rotation axis X on the inner circumference and the outer circumference of the peripheral wall 38.

  As shown in FIG. 1, the dish plate 34 and the retaining plate 35 are spline fitted on the inner periphery of the peripheral wall 38, and the friction on the inner diameter side is established between the dish plate 34 and the retaining plate 35. The plates 31 and the outer diameter side friction plates 32 are alternately arranged.

Furthermore, on the inner periphery of the peripheral wall portion 38, a snap ring 36 for restricting the displacement of the retaining plate 35 in the direction away from the dish plate 34 is provided.
The snap ring 36 is provided at a position offset from the tip 38 a (see (b) of FIG. 1) of the peripheral wall 38 toward the bottom wall 39.

The end 38 a of the peripheral wall 38 in the axial direction of the rotation axis X is opposed to the retaining plate 45 with a clearance C between the retaining plate 45 and the brake 4.
A recess 383 recessed in the direction (right direction in the drawing) away from the retaining plate 45 is provided on the inner diameter side at the tip 38 a of the peripheral wall 38.

The recess 383 is open on the retaining plate 45 side (the brake 4 side) and the inner diameter side (the rotation axis X side), and the recess 383 has a ring shape when viewed from the rotation axis X direction.
When viewed from the rotation axis X direction, the outer periphery 383a of the recess 383 has an arc shape surrounding the rotation axis X at a predetermined interval, and the bottom wall 383b of the recess 383 in the rotation axis X direction is orthogonal to the rotation axis X It is flat.

  A ring-shaped washer 7 is internally fitted in the recess 383 from the direction of the rotation axis X, and an outer diameter side of the recess 383 supports the outer periphery 71 of the washer 7 on the tip 38 a side of the peripheral wall 38 It constitutes 381a.

The washer 7 is a ring-shaped flat washer, and the washer 7 is press-fitted to the inside of the annular wall 381 a of the peripheral wall 38 and provided in the recess 383.
In this state, the washer 7 is provided such that the end surface 7a on one side in the rotation axis X direction and the end surface 7b on the other side are orthogonal to the rotation axis X.
The washer 7 has a predetermined thickness (length L1) in the rotation axis X direction, and this length L1 is larger than the height (length L2) of the annular wall 381a in the rotation axis X direction. Is set (L1> L2).

Therefore, the end face 7b on the other side of the washer 7 protrudes from the tip 38a of the peripheral wall 38 to the retaining plate 45 by a predetermined length L3 (L3 = L1-L2).
The washer 7 is provided at a position intersecting the imaginary line Ln passing through the radial center of the pressing portion 431 (see FIG. 1A) of the piston 43. The imaginary line Ln is a straight line parallel to the rotation axis X, along the acting direction of the pressing force of the piston 43.

The outer periphery 71 of the washer 7 is located on the outer diameter side of the imaginary line Ln, and the washer 7 has a radial width W1 that intersects the imaginary line Ln from the inner diameter side to the outer diameter side.
The end surface 7b on the piston 43 side of the washer 7 is a flat surface orthogonal to the rotation axis X, and on this end surface 7b, the retaining plate 45 pressed by the pressing force of the piston 43 is from the rotation axis X direction. It comes in contact.

  In this embodiment, the supporting structure 1 of the retaining plate 45 to which the pressing force of the piston 43 acts is supported by the peripheral wall 38 of the clutch drum 37, the recess 383 provided on the tip 38a of the peripheral wall 38, and the recess 383 And a washer 7.

Hereinafter, the operation of the support structure 1 of the retaining plate 45 according to the embodiment will be described.
When the piston 43 moves to the clutch 3 side by the supply of the hydraulic pressure to the oil chamber S1, the inner friction plate 41 and the outer friction plate 42 exert pressure on the retaining plate 45 by the pressing force exerted from the piston 43. It is pushed.
Then, the retaining plate 45 moves toward the clutch drum 37 together with the radially inner friction plate 41 and the radially outer friction plate 42 and abuts against the washer 7 provided on the clutch drum 37 from the rotational axis X direction.

The washer 7 is press-fitted and supported by a recess 383 provided in the peripheral wall 38 of the clutch drum 37, and the movement in the radial direction is restricted by the annular wall 381a.
Furthermore, in the washer 7, the end surface 7a opposite to the retaining plate 45 is separated from the brake 4 by the bottom wall 383b of the recess 383 provided in the spline peak 381 and the spline valley 382 (FIG. 1 Movement to the right) is restricted.

  Therefore, the movement of the retaining plate 45 in the direction away from the piston 43 is restricted by the washer 7, and finally the inner friction plate 41 and the outer friction plate 42, the piston 43 and the retaining plate 45 It is fastened non-rotatably between them.

  In this state, the retaining plate 45 is in contact with only the washer 7 while the surface 45a opposite to the piston 43 avoids contact with the tip 38a of the peripheral wall 38 of the clutch drum 37.

Therefore, as the clutch drum 37 rotates around the rotation axis X, only the other end surface 7 b of the washer 7 slides on the surface 45 a of the retaining plate 45.
As a result, the sliding resistance acting as a load against the rotation of the clutch drum 37 can be suppressed to the minimum value determined in accordance with the radial width W1 of the washer 7, so the rotation of the clutch drum 37 around the rotation axis X is large. It is not blocked.

  Conventionally, in the case where the positioning of the retaining plate 45 is performed by the snap ring 48 (see FIG. 4), in consideration of the displacement on the inner diameter side of the retaining plate 45, the snap ring 48 and the peripheral wall 38 of the clutch drum 37. In addition, the clearance C1 in the rotation axis X direction is secured with a margin.

In this embodiment, the washer 7 provided on the peripheral wall portion 38 of the clutch drum 37 is used to position the retaining plate 45 on which the pressing force of the piston 43 acts, and the snap used for positioning the retaining plate 45 Abolished ring 48 (see Figure 4).
As a result, the peripheral wall 38 and the retaining plate 45 can be disposed closer to each other in the direction of the rotation axis X as much as the snap ring 48 is eliminated. Then, the gap C (see (b) in FIG. 1) between the peripheral wall 38 and the retaining plate 45 in the rotational axis X direction can be narrowed.
Therefore, the length in the rotational axis X direction of the automatic transmission can be shortened by the amount by which the gap is narrowed.

As described above, in the embodiment,
(1) The brake 4 (frictional fastening device) provided in the transmission case 10 is
An inner friction plate 41 and an outer friction plate 42 (a plurality of friction plates);
A piston 43 that presses the inner friction plate 41 and the outer friction plate 42 (a plurality of friction plates) in the direction of the rotation axis X;
Seen from the radially inner friction plate 41 and the radially outer friction plate 42, it is provided on the opposite side to the piston 43, and the pressing force of the piston 43 acts via the radially inner friction plate 41 and the radially outer friction plate 42. And a retaining plate 45,
A clutch drum 37 (rotary body) rotatable about the rotation axis X on the opposite side to the piston 43 of the retaining plate 45 in the rotation axis X direction makes the peripheral wall 38 of the clutch drum 37 the retaining plate 45 A supporting structure 1 of a retaining plate 45 in an automatic transmission disposed opposite to each other, comprising:
The washer 7 is interposed between the retaining plate 45 and the tip 38 a of the peripheral wall 38 which is a portion facing the retaining plate 45 in the clutch drum 37.

  With this configuration, the displacement of the retaining plate 45 in the direction away from the piston 43 is restricted by the washer 7 and the clutch drum 37. Thus, relative rotation between the inner friction plate 41 and the outer friction plate 42 can be restricted, and the brake 4 can be reliably engaged.

Further, in this state, the clutch drum 37 is allowed to rotate relative to the retaining plate 45 by the washer 7 interposed between the retaining plate 45 and the peripheral wall portion 38 of the clutch drum 37.
Therefore, even if the pressing force of the piston 43 is received by the peripheral wall 38 of the clutch drum 37 via the washer 7, the rotation of the clutch drum 37 is not significantly inhibited when the brake 4 is engaged.

Therefore, the positioning of the retaining plate 45 to which the pressing force of the piston 43 acts does not require the snap ring 48 (see FIG. 4) conventionally used.
Thus, the snap ring 48 can be abolished, and the length in the rotational axis X direction of the automatic transmission can be shortened by at least the length of the abolished snap ring 48 in the rotational axis X direction.

(2) The washer 7 is supported by the end 38a of the peripheral wall 38, and the washer 7 is provided so as to project from the end 38a of the peripheral wall 38 toward the retaining plate 45. The other end face 7b of the second side is positioned closer to the retaining plate 45 than the tip 38a of the peripheral wall 38.

According to this configuration, when the clutch drum 37 rotates around the rotation axis X, only the other end surface 7 b of the washer 7 slides on the surface 45 a of the retaining plate 45.
As a result, the sliding resistance acting as a load against the rotation of the clutch drum 37 can be suppressed to the minimum value determined in accordance with the radial width W1 of the washer 7, so the rotation of the clutch drum 37 around the rotation axis X is large. Not inhibited.

(3) The washer 7 is provided on an extension line (on the imaginary line Ln) of the pressing portion 431 of the piston 43 along the rotation axis X direction,
The washer 7 is provided radially across the virtual line Ln passing through the area from the inner diameter of the retaining plate 45, and the washer 7 is formed to have a predetermined width W1 in the radial direction.

According to this configuration, the washer 7 is disposed on the imaginary line Ln on which the pressing force of the piston 43 acts, across the imaginary line Ln from the inner diameter side to the outer diameter side.
As a result, the washer 7 can reliably support the area of the retaining plate 45 where the pressing force is applied to a large extent.
Therefore, the washer 7 can be positioned at a predetermined position in the direction of the rotation axis X while suitably preventing the washer 7 from being greatly inclined in the direction away from the piston 43 on the inner diameter side.

(4) The rotating body disposed opposite to the retaining plate 45 in the rotational axis X direction is a clutch drum of the clutch 3 (another frictional engagement device) disposed adjacent to the brake 4 (frictional fastening device) in the rotational axis X direction 37,
The clutch drum 37 has a cylindrical peripheral wall 38 disposed opposite to the retaining plate 45 in the rotational axis X direction,
The washer 7 is provided at the end 38 a (end) opposite to the retaining plate 45 in the peripheral wall 38.

  In this configuration, the peripheral wall 38 has a predetermined length in the rotational axis direction, and the rigidity in the rotational axis X direction is high. Therefore, the washer 7 can be positioned at a predetermined position in the rotational axis X direction by receiving the pressing force of the piston 43 acting on the retaining plate 45 while utilizing the rigidity and strength of the peripheral wall 38.

(5) The peripheral wall 38 alternately connects the spline peak 381 located on the outer diameter side and the spline valley 382 located on the inner diameter in the circumferential direction around the rotation axis X when viewed from the rotation axis X direction. Is formed,
The washer 7 is configured such that the end surface 7a opposite to the retaining plate 45 in the rotation axis X direction is supported at least by the spline valley portion 382.

  With this configuration, the washer 7 is reliably supported on the peripheral wall 38 side. Therefore, even if the retaining plate 45 is pressed against the washer 7 by the pressure of the piston 43, the inner diameter side of the retaining plate 45 is from the piston 43 The washer 7 can be positioned at a predetermined position in the direction of the rotation axis X while suitably preventing large inclination in the direction of separation.

(6) The end 38a of the peripheral wall 38 opposite to the retaining plate 45 is provided with an annular wall 381a into which the washer 7 is fitted and pressed in from the retaining plate 45 side.

With this configuration, the washer 7 can be reliably supported on the side wall portion 38 side. Further, as the clutch drum 37 rotates about the rotation axis X, only the other end surface 7 b of the washer 7 slides on the surface 45 a of the retaining plate 45.
As a result, the sliding resistance acting as a load against the rotation of the clutch drum 37 can be suppressed to the minimum value determined in accordance with the radial width W1 of the washer 7, so the rotation of the clutch drum 37 around the rotation axis X is large. It will not be inhibited.

(7) A recess 383 recessed in the direction away from the retaining plate 45 is provided on the inner diameter side at the tip 38 a of the peripheral wall 38,
The recess 383 is open on the retaining plate 45 side (the brake 4 side) and the inner diameter side (the rotation axis X side), and the outer diameter side of the recess 383 constitutes an annular wall 381 a that supports the outer periphery 71 of the washer 7. Yes,
The washer 7 is provided with one end face 7 a in the rotation axis X direction in contact with the bottom wall 383 b of the recess 383 orthogonal to the rotation axis X, and the other end face 7 b is from the tip 38 a of the peripheral wall 38 It is also configured to be located on the retaining plate 45 side.

With this configuration, the washer 7 can be supported in the recess 383 of the peripheral wall 38 in a state in which relative rotation with the peripheral wall 38 is restricted.
The surface 45 a of the retaining plate 45 opposite to the piston 43 can be in contact with the washer 7 only while avoiding contact with the tip 38 a of the peripheral wall 38 of the clutch drum 37.
As a result, it is possible to suppress the sliding resistance serving as a load for the rotation of the clutch drum 37.

FIG. 3 is a view for explaining a support structure 1A of the retaining plate 45 according to the modification.
Although the case where the washer 7 was supported by the clutch drum 37 side was illustrated in above-mentioned embodiment, this invention is not limited only to this aspect.
For example, a recess 451 recessed in a direction away from the clutch drum 37 is provided on the inner diameter side of the surface 45a on the clutch drum 37 side of the retaining plate 45, and the washer 7 is press-fitted in the recess 451 from the rotational axis X direction. It is good also as structure 1A.

  Also by doing this, the snap ring 48 (see FIG. 4) is abolished, and at least the length of the abolished snap ring 48 in the rotational axis X direction, the length of the automatic transmission in the rotational axis X direction Can be shortened.

1, 1A Support structure 3 Clutch (friction fastening device)
Reference Signs List 30 clutch hub 31 inner side friction plate 32 outer side friction plate 33 piston 34 dish plate 35 retaining plate 36 snap ring 37 clutch drum 38 peripheral wall 38a tip 381 spline peak 381a annular wall 382 spline valley 383 recess 383a outer periphery 383b Bottom wall 39 Bottom wall 4 Brake (friction fastening device)
Reference Signs List 41 inner diameter side friction plate 42 outer diameter side friction plate 43 piston 44 dish plate 45 retaining plate 48 snap ring 5 planetary gear mechanism 51 ring gear 52 carrier 7 washer 7a one end face 7b the other end face (surface on the retaining plate side)
71 outer circumference 10 transmission case 101 recessed portion 102 side wall 431 pressing portion 432 base C, C1 gap Ln virtual line S1 oil chamber W1 width X rotation axis

Claims (7)

The friction fastening device provided in the transmission case is
With multiple friction plates,
A piston for pressing the plurality of friction plates in a rotational axis direction;
And a retaining plate, wherein the pressing force of the piston acts through the plurality of friction plates.
In a supporting structure of a retaining plate in an automatic transmission, wherein a rotating body rotatable around the rotating shaft is disposed on the side opposite to the piston of the retaining plate in the rotating shaft direction. There,
A supporting structure for a retaining plate in an automatic transmission, wherein a washer is interposed between a portion of the rotating body facing the retaining plate and the retaining plate.   The automatic transmission according to claim 1, wherein the washer is supported by the facing portion, and the washer is provided so as to protrude from the facing portion toward the retaining plate. Plate support structure. The washer is provided on an extension of the piston along the rotational axis direction,
The supporting structure of a retaining plate in an automatic transmission according to claim 2, wherein the washer is provided radially across the extension line. The rotating body is a clutch drum of another friction fastening device disposed adjacent to the friction fastening device in the rotation axis direction,
The clutch drum has a cylindrical peripheral wall portion disposed opposite to the retaining plate in the rotation axis direction,
The automatic transmission as set forth in any one of claims 1 to 3, wherein the washer is provided at an end portion of the peripheral wall portion facing the retaining plate. Support structure. When viewed from the rotation axis direction, the peripheral wall portion is formed by alternately connecting a spline peak portion located on the outer diameter side and a spline valley portion located on the inner diameter side in the circumferential direction around the rotation axis.
5. The retaining plate of an automatic transmission according to claim 4, wherein the washer is supported at least by the spline valley in a surface opposite to the retaining plate in the rotational axis direction. Support structure.   The annular wall which the said washer fits inside from the said retaining plate side is provided in the edge part which opposes the said retaining plate of the said surrounding wall part, The said claim is characterized by the above-mentioned. Support structure for retaining plate in automatic transmission.   The retaining plate in an automatic transmission according to claim 6, wherein a surface on the retaining plate side of the washer in the rotational axis direction is located on the retaining plate side with respect to the annular wall. Support structure.

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