JP2007016915A - Centrifugal hydraulic cancellation mechanism for hydraulic engaging device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cancellation plate structure in a centrifugal hydraulic cancellation mechanism for a hydraulic engaging device preventing positional deviation of a spring by a simple composition. <P>SOLUTION: Since a spring guide 41 is formed by bending an inner diameter side end of a cancellation plate 20, and a position of the wave spring is held by the spring guide 41, the cancellation plate 20 and the spring guide 41 can be formed by the same member, and there is no need to separately use a member for fixing the wave spring. By this, deviation of the position of the wave spring can be prevented while reducing manufacturing costs by a simple composition. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a centrifugal hydraulic pressure canceling mechanism of a hydraulic fastening device in an automatic transmission, and more particularly to a structure of a cancel plate serving as a side wall of a centrifugal canceling oil chamber.

As a hydraulic fastening device of an automatic transmission, there are a multi-plate clutch and a multi-plate brake. In these, hydraulic oil as an engagement pressure is guided to the clutch oil chamber at the time of engagement, and hydraulic oil is drained from the clutch oil chamber at the time of release.
However, even when the hydraulic fastening device is released, the hydraulic oil is not completely drained from the clutch oil chamber, and if the hydraulic fastening device rotates at a high speed, centrifugal oil pressure is generated by the hydraulic oil remaining in the clutch oil chamber. In some cases, a hydraulic fastening device that should be kept released may be fastened by centrifugal hydraulic pressure.
In order to prevent this, a centrifugal oil pressure cancel chamber is formed at a position facing the clutch oil chamber across the piston in order to cancel the force due to the centrifugal oil pressure acting on the piston from the clutch oil chamber side. There is a hydraulic fastening device with a centrifugal canceling chamber that stores the water.
An example of a hydraulic fastening device having such a centrifugal hydraulic pressure cancellation chamber is disclosed in Patent Document 1.

For example, in the clutch shown in FIG. 4, the clutch drum 111 includes a disk-shaped side wall, an inner cylinder extending from the inner peripheral edge of the side wall, and an outer cylinder extending from the outer peripheral edge of the side wall in the same direction as the inner cylinder. A clutch piston 100 disposed between an inner cylinder and an outer cylinder of the clutch drum 111 and movable in the axial direction; a clutch oil chamber 101 formed between the clutch piston 100 and the clutch drum 111; and a clutch piston. 100, a cancel plate 104 disposed on the opposite side to the side where the clutch oil chamber 101 is formed, and a centrifugal cancel oil chamber 103 formed by the clutch piston 100 and the cancel plate 104. .
The clutch oil chamber 101 and the centrifugal cancel oil chamber 103 are adjacent to each other with the clutch piston 100 interposed therebetween.
A wave spring 106 is provided between the cancel plate 104 and the clutch piston 100, and the wave spring 106 reduces the clutch piston 100 on the side where the volume of the clutch oil chamber 101 is reduced (releasing the bias of the friction plate by the clutch piston 100). Side).

The cancel plate 104 is restricted from moving in the axial direction by the urging force of the wave spring 106 by a snap ring 105 disposed on the axial center side.
Oil is supplied to the centrifugal cancellation oil chamber 103 via an axial oil passage 107 formed inside the shaft 102 and a radial oil passage 108 that connects the axial oil passage 107 and the centrifugal cancellation oil chamber 103. .
A discharge hole 109 formed by a notch is formed on the inner peripheral side of the ring-shaped cancel plate 104, and excess oil in the centrifugal cancel oil chamber 103 is discharged from the discharge hole 109.
A lip seal 110 is attached to the outer peripheral edge of the cancel plate 104, and the lip seal 110 is slidably in contact with the inner peripheral surface of the clutch piston 100.
Japanese Patent Laid-Open No. 11-173343

  However, in the conventional hydraulic fastening device provided with the centrifugal canceling oil chamber, the cancel plate 104 itself does not have a guide function to prevent the position of the wave spring 106 from being shifted, and the position of the wave spring 106 is shifted in the radial direction so that the peripheral member Or when the wave spring 106 rides on the step 112 formed by protruding the inner diameter portion of the cancel cover 104 to the centrifugal cancel oil chamber 103 side, the spring constant of the wave spring 106 changes, and the fastening mechanism There was a problem that the operating characteristics would change.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a cancel plate structure in a centrifugal hydraulic pressure canceling mechanism of a hydraulic fastening device that prevents the displacement of a spring with a simple configuration.

  In the present invention, a drum having an inner cylinder is rotatably supported by a drum support on the transmission case side on the inner circumferential surface of the inner cylinder, a piston is provided in the drum, and a piston oil chamber is formed between the drum and the piston. A biasing means is provided on the inner cylinder on the opposite side of the piston from the piston oil chamber to form a centrifugal cancel chamber between the piston and the piston between the piston and the cancel plate. In the centrifugal hydraulic pressure canceling mechanism of the hydraulic fastening device in which is arranged, the cancel plate includes a main body portion formed in a disc shape and a holding guide formed by bending a part of the inner diameter side end portion of the main body portion toward the centrifugal cancel chamber. And the radial position of the biasing means is regulated by the holding guide portion.

  According to the present invention, the holding guide portion is formed by bending the inner diameter side end portion of the cancel plate, and the position of the urging means is held by the holding guide portion. They can be formed by the same member, and there is no need to separately use a member for fixing the biasing means. Therefore, the position of the biasing means is prevented from shifting while the manufacturing cost is reduced with a simple configuration, and the biasing means interferes with the peripheral member, or the spring constant of the biasing means changes to change the operating characteristics of the fastening mechanism. Can be prevented from changing.

Next, embodiments of the present invention will be described by way of examples.
FIG. 1 is a view showing the periphery of a hydraulic fastening element of an automatic transmission to which this embodiment is applied.
In this embodiment, a clutch will be described as an example of a fastening element.
A transmission case 1 of an automatic transmission that performs engine speed conversion accommodates an engagement element such as a planetary gear mechanism 23, a multi-plate brake, and a multi-plate clutch 12.
The planetary gear mechanism 23 includes a sun gear 3 connected to the input shaft 2 disposed on the shaft center side, a pinion gear 4 that meshes with the sun gear 3, a pinion carrier 5 that supports the pinion gear 4, and an outer peripheral side of the pinion gear 4. And a ring gear 6 that meshes with the pinion gear 4.

The input shaft 2 is connected to a torque converter (not shown), and the rotational driving force of the engine is input to the input shaft 2 via the torque converter.
The rotational driving force transmitted to the sun gear 3 is transmitted to the ring gear 6 through the pinion gear 4.
The outer peripheral side of the ring gear 6 is covered with an outer cylinder portion 14 </ b> A of the clutch drum 14.
A multi-plate clutch 12 is provided between the outer cylinder 14 </ b> A and the ring gear 6.
The multi-plate clutch 12 is provided on the outer diameter side of a drive plate 9 in which teeth provided on the inner diameter side mesh with a spline formed on the outer peripheral surface of the ring gear 6 and on a spline formed on the inner peripheral surface of the outer cylinder 14A. The driven plate 8 with which the received teeth mesh is alternately overlapped.

The clutch drum 14 includes a disk-shaped drum side wall 14C, an inner cylinder 14B that extends from the inner peripheral edge of the drum side wall 14C and serves as the shaft of the clutch drum 14, and an outer cylinder that extends from the outer peripheral edge of the drum side wall 14C in the same direction as the inner cylinder 14B. It is comprised with the pipe | tube 14A.
The inner cylinder 14 </ b> B is rotatably supported by a drum support 13 coupled to the transmission case 1.
A clutch piston 17 that urges the multi-plate clutch 12 is provided inside the U-shape of the clutch drum 14.

A clutch oil chamber 16 (piston oil chamber) is formed between the clutch piston 17 and the clutch drum 14.
When hydraulic pressure is supplied to the clutch oil chamber 16, the clutch piston 17 moves leftward in FIG. 1 and presses the multi-plate clutch 12 by the piston tip portion 17 </ b> A at the tip of the outer cylinder portion of the clutch piston 17.
A cancel plate 20 is disposed on the opposite side of the clutch piston 17 where the clutch oil chamber 16 is formed.
A centrifugal cancel chamber 15 is formed between the cancel plate 20 and the clutch piston 17.
Thereby, the centrifugal cancel chamber 15 and the clutch oil chamber 16 are adjacent to each other with the clutch piston 17 interposed therebetween.

  A wave spring 24 (biasing means) is provided between the cancel plate 20 and the clutch piston 17, and the side of the clutch piston 17 that reduces the volume of the clutch oil chamber 16 by the wave spring 24 (multi-plate clutch by the clutch piston 17). 12 to release the urging of 12).

Next, the details around the cancel plate 20 will be described with reference to FIG.
The drum support 13 rotatably supports the inner cylinder 14B via a sliding bush 34 at the tip end of the inner cylinder 14B (the end opposite to the side connected to the drum side wall 14C).
An annular oil groove 35 is formed on the outer peripheral surface of the drum support 13 at a position corresponding to the centrifugal cancel chamber 15 in the axial direction.
An axial oil passage 18 is formed in the drum support 13 in the axial direction, and the axial oil passage 18 communicates with the annular oil groove 35.

A bush hole 36 and a cancel chamber communication hole 37 for communicating the annular oil groove 35 and the centrifugal cancel chamber 15 are formed in the sliding bush 34 and the inner cylinder 14B, respectively.
A cancel chamber radial oil passage 38 is formed by the annular oil groove 35, the bush hole 36 and the cancel chamber communication hole 37, and the oil flowing through the axial oil passage 18 is centrifuged through the cancel chamber radial oil passage 38. 15 is supplied.

The cancel plate 20 includes a disc-shaped main body 20A and a spring guide 41 (holding guide) formed on the inner diameter side of the main body 20A.
A lip seal 30 is attached to the outer peripheral edge of the main body 20A.
The lip seal 30 has a lip 30A (protruding portion) that protrudes from the outer peripheral edge toward the centrifugal cancel chamber 15 side.
In a state where the cancel plate 20 is disposed in the clutch piston 17, the lip seal 30 contacts the inner surface of the cylindrical piston tip portion 17A. In this state, the clutch piston 17 can be moved in the axial direction, and the centrifugal cancel is performed. The liquid tightness in the chamber 15 is maintained.

Further, an annular oil groove 19 is formed on the outer peripheral surface of the drum support 13 at a position corresponding to the clutch oil chamber 16 in the axial direction.
The annular oil groove 19 communicates with an axial oil passage 25 (see FIG. 1) formed in the axial direction inside the drum support 13.
A clutch oil chamber communication hole 39 for communicating the annular oil groove 19 and the clutch oil chamber 16 is formed in the inner cylinder 14B.
As a result, the hydraulic pressure supplied from the axial oil passage 25 formed in the drum support 13 is supplied into the clutch oil chamber 16 via the annular oil groove 19.
The hydraulic pressure supplied into the clutch oil chamber 16 becomes an operating hydraulic pressure that operates the clutch piston 17.

A seal ring 31 is provided at a sliding portion of the clutch piston 17 with the outer cylinder 14A, and a seal ring 32 is provided at a sliding portion of the clutch piston 17 with the inner cylinder 14B.
Accordingly, the fluid tightness of the clutch oil chamber 16 is maintained while the clutch piston 17 can be moved in the axial direction in the clutch drum 14.

On the inner peripheral side of the cancel plate 20, the spring guide 41 is formed by bending a claw formed by cutting the end portion on the inner peripheral side in the radial direction toward the centrifugal cancel chamber 15.
When the wave spring 24 is fitted in the outer peripheral side of the spring guide 41 with a predetermined minute gap, even when the position of the wave spring 24 is displaced in the radial direction, the inner peripheral surface of the wave spring 24 is kept in the spring guide. It is supported by 41 and the deviation beyond a predetermined is prevented.
By forming the spring guide 41, when the cancel plate 20 is viewed from the axial direction, the inner peripheral side of the cancel plate 20 is notched, and the notched portions are the centrifugal cancel chamber 15 and the centrifugal cancel chamber 15. It becomes the discharge hole 40 which connects with the outside.

A snap ring 22 is fitted on the outer peripheral surface of the distal end portion of the inner cylinder 14B.
The snap ring 22 is engaged with an end portion on the inner peripheral side of the cancel plate 20 and restricts movement when the cancel plate 20 is urged by the wave spring 24.

Next, details of the cancel plate 20 will be described.
FIG. 3 (a) shows a front view of the cancel plate, and FIG. 3 (b) shows a cross-sectional view taken along line AA in FIG. 3 (a).
Four pairs of cutout portions 42 are provided on the inner peripheral edge of the cancel plate 20, and claw portions 43 are formed between the pair of cutout portions 42 as indicated by broken lines in FIG. .
The claw portion 43 is bent perpendicularly to the main body portion 20A of the cancel plate 20 as shown in FIG.
The cancel plate 20 is formed from a single metal plate, and the cutout portion 42 and the spring guide 41 are formed by pressing.
The tip of the notch 42 is formed round.
Thereby, when the spring guide 41 is formed by bending, the stress does not concentrate on the front end portion of the notch portion 42 and the main body portion 20A is not broken.

The cancel plate 20 is arranged in the clutch piston 17 so that the side of the cancel plate 20 on which the spring guide 41 is formed (the rising side of the claw portion 43) faces the clutch piston 17 side.
In this embodiment, four spring guides 41 are formed at equal intervals in the circumferential direction on the inner peripheral edge of the cancel plate 20.
Note that three or more spring guides 41 may be formed at equal intervals in the same radial direction on the inner peripheral edge of the cancel plate 20.
As shown in FIG. 3B, the lip 30A on the distal end side of the lip seal 30 protrudes in the same direction as the spring guide 41 from the surface of the main body portion 20A from which the spring guide 41 protrudes. Yes.

The rising height of the spring guide 41 from the main body portion 20A is higher than the height at which the lip 30A protrudes from the surface of the main body portion 20A where the spring guide 41 protrudes, and hydraulic pressure is supplied into the clutch oil chamber 16. Thus, the height is set so as not to interfere with the clutch piston 17 even when the clutch piston 17 moves.
On the inner peripheral side of the cancel plate 20, the gap formed by forming the spring guide 41 and the notch 42 constitute the discharge hole 40.

Next, the positional relationship between the discharge hole 40 and the snap ring 22 will be described with reference to FIG.
A part of the snap ring 22 is shown in FIG.
In order to restrict the movement of the cancel plate 20, the inner peripheral edge side of the cancel plate 20 is in contact with the snap ring 22.
The snap ring 22 is located on the back side of the cancel plate 20 in FIG.
The discharge hole 40 is closed at the inner peripheral end of the cancel plate 20 by the snap ring 22.

As shown in FIG. 2, when oil pressure is supplied into the clutch oil chamber 16 in a state where oil has accumulated in the centrifugal cancel chamber 15, the direction in which the clutch piston 17 engages the multi-plate clutch 12 (in FIG. 2). Move to the left).
At this time, the clutch piston 17 pushes and contracts the wave spring 24 to reduce the volume of the centrifugal cancel chamber 15.
As the volume decreases, the oil in the centrifugal cancel chamber 15 is discharged from the discharge hole 40.
When the supply of hydraulic pressure to the clutch oil chamber 16 is stopped, the wave spring 24 biases the clutch piston 17 to the right side in FIG. 2 and releases the engagement of the multi-plate clutch 12.

In this embodiment, the spring guide 41 is formed by bending the inner diameter side end of the cancel plate 20, and the position of the wave spring 24 is held by the spring guide 41. The plate 20 and the spring guide 41 can be formed of the same member, and there is no need to separately use a member for fixing the wave spring 24.
Accordingly, the radial displacement of the wave spring 24 can be prevented while reducing the manufacturing cost with a simple configuration, and the step portion 25 formed by projecting the inner diameter portion of the cancel plate 20 toward the centrifugal cancel chamber 15 (FIG. 3). (See (b)), the wave spring 24 does not ride on, so that it is possible to prevent the operating constant of the multi-plate clutch 12 from changing due to a change in the spring constant of the wave spring 24.

Further, since the radial displacement of the wave spring 24 is prevented, the wave spring 24 does not interfere with the inner peripheral surface (see FIG. 2) of the piston drum portion 17B of the clutch piston 17, and the durability of the clutch piston 17 is improved. Can be prevented.
For example, when the wave spring 24 is guided using a spring retainer, the axial dimension increases by the thickness of the spring retainer, but the spring guide 41 and the cancel plate 20 are formed of the same member. Therefore, an increase in the axial dimension can be prevented. (Effects corresponding to claim 1 above)

  Further, by forming the discharge hole 40 between the spring guide 41 and the inner cylinder 14B that supports the cancel plate 20 while bending the inner diameter side end portion of the cancel plate 20 to form the spring guide 41, the spring guide 41 and It can be formed simultaneously with the discharge hole 40, and the number of manufacturing steps can be reduced. (Effects corresponding to claim 2)

In general, the wave spring 24 has low lateral rigidity, and is easily displaced in the radial direction when compressed.
Accordingly, the rising height of the spring guide 41 is formed so that the lip seal 30 is higher than the height at which the lip seal 30 protrudes from the main body portion 20A of the cancel plate 20, so that the lip seal in the axial direction out of the deviation of the wave spring 24. The portion corresponding to 30 is prevented from being displaced beyond a predetermined range by the spring guide 41 so that the wave spring 24 does not interfere with the lip seal 30, and deterioration of the durability of the lip seal 30 can be prevented. (Effects corresponding to claims 3 and 4)

  Further, since three or more spring guides 41 are formed at equal intervals in the same radial direction on the inner peripheral edge of the cancel plate 20, the wave spring 24 can be reliably and stably provided on the inner peripheral side by the spring guide 41. Can be positioned. (Effects corresponding to claim 5)

  The cancel plate 20 is made of a metal plate, a pair of notches 42 are formed at the inner diameter side end of the cancel plate 20, and the claw portions 43 formed between the notches 42 are raised so as to raise the spring guide 41. Therefore, the spring guide 41 and the discharge hole 40 can be easily formed by press processing that is inexpensive and highly productive. (Effects corresponding to claims 6 and 7)

  Further, by rounding the front end portion of the notch portion 42, when the spring guide 41 is formed so as to be pressable, stress is concentrated on the front end portion of the notch portion 42 to prevent the main body portion 20A from being broken. be able to. (Effect corresponding to claim 8)

  In this embodiment, the wave spring 24 is disposed as the urging means between the clutch piston 17 and the cancel plate 20, but the wave spring 24 is not limited to the wave shape, and is attached to the concentric circular shape by elastic deformation. Any biasing member may be used as long as it generates a force. For example, one coil spring or a plurality of springs arranged in a ring shape may be used.

It is a figure which shows the cross section of the automatic transmission to which the present Example was applied. It is a figure which shows the detail of the cancellation plate integrated in the automatic transmission. It is a figure which shows a cancellation plate. It is a figure which shows the detail of the conventional cancellation plate.

Explanation of symbols

1 Transmission Case 12 Multi-plate Clutch 13 Drum Support 14 Clutch Drum (Drum)
14A outer cylinder 14B inner cylinder 14C drum side wall 15 centrifugal cancel chamber 16 clutch oil chamber (piston oil chamber)
17 Clutch piston (piston)
20 Cancel plate 22 Snap ring 23 Planetary gear mechanism 24 Wave spring (biasing means)
30 Lip seal 30A Lip (protrusion)
34 Sliding bush 40 Discharge hole 41 Spring guide (holding guide)
42 Notch 43 Claw

Claims (8)

A drum having an inner cylinder is rotatably supported by a drum support on the transmission case side on the inner circumferential surface of the inner cylinder, and a piston is provided in the drum and a piston oil chamber is formed between the drum and the piston. A cancel plate that forms a centrifugal cancel chamber between the piston and the piston oil chamber is provided on the inner cylinder, and the piston is disposed between the piston and the cancel plate. In the centrifugal hydraulic pressure canceling mechanism of the hydraulic fastening device in which the biasing means for pushing back the piston is arranged,
The cancel plate has a main body part formed in a disc shape, and a holding guide part formed by bending a part of the inner diameter side end of the main body part to the centrifugal cancel chamber side,
A centrifugal hydraulic pressure canceling mechanism for a hydraulic fastening device, wherein the holding guide portion restricts a radial position of the urging means. The innermost diameter portion of the holding guide portion is formed to have a larger diameter than the innermost diameter portion of the main body portion,
2. The centrifugal hydraulic pressure of the hydraulic fastening device according to claim 1, wherein a discharge hole that connects the centrifugal cancel chamber and the outside of the centrifugal cancel chamber is formed between the holding guide portion and the inner cylinder. Cancel mechanism. A lip seal is provided at the outer diameter side end of the main body,
The lip seal has a protruding portion protruding toward the centrifugal cancel chamber,
The cancellation plate is
The height at which the holding guide portion protrudes from the main body portion toward the centrifugal cancel chamber is higher than the height at which the protrusion protrudes from the main body portion toward the centrifugal cancel chamber. The centrifugal hydraulic pressure canceling mechanism of the hydraulic fastening device according to claim 1 or 2. 2. The biasing means is disposed on an outer peripheral side of the inner cylinder, has a concentric continuous shape, and a radial position of the inner diameter side is regulated by the holding guide portion. The centrifugal hydraulic pressure canceling mechanism of the hydraulic fastening device according to any one of 1 to 3. 5. The centrifugal hydraulic pressure canceling mechanism for a hydraulic fastening device according to claim 1, wherein three or more holding guide portions are provided at equal intervals in the same radial direction. The centrifugal canceling mechanism for a hydraulic fastening device according to any one of claims 1 to 5, wherein the cancel plate is made of a metal plate, and the holding guide portion is formed by pressing. The holding guide part is
7. The cancel plate is formed by forming a pair of notches arranged in parallel in the same radial direction at an inner diameter side end portion of the cancel plate, and bending a claw portion between the notches. A centrifugal hydraulic pressure canceling mechanism of the hydraulic fastening device described. The centrifugal hydraulic pressure canceling mechanism for a hydraulic fastening device according to claim 7, wherein the notch has a rounded tip end.

Images