JPH0641003Y2 - Friction plate support structure of clutch in automatic transmission for vehicle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a structure for supporting a friction plate of a clutch in an automatic transmission for a vehicle, and more particularly to a friction arranged between an outer drum and an inner drum. The present invention relates to a structure in which, when a snap ring that regulates the axial position of a plate is attached to the outer peripheral surface of an inner drum, the ring can be prevented from coming off due to centrifugal force.

[Conventional technology]

Generally, an automatic transmission for a vehicle includes a speed change gear device including a planetary gear and an input path switching device having a plurality of clutches and brakes for selecting and inputting an output from a torque converter to the device. Further, each of the above-mentioned clutches is configured by disposing a large number of friction plates between the outer drum and the hub, and further disposing a drive piston for pressing the friction plates so as to face the friction plates.

By the way, when the friction plates are mounted between the outer drum and the hub, it is necessary to prevent the friction plates from moving in the direction opposite to the piston. Conventionally, a snap ring has been used for this purpose. . When this snap ring is mounted, the clutch rotates at a high speed due to its structure, and therefore the snap ring may be disengaged by centrifugal force. To prevent this, it is common to mount the snap ring on the inner peripheral surface of the outer drum. Target.

[Problems to be solved by the invention]

However, since the vehicle clutch has a small mounting space, it must be miniaturized as much as possible. Therefore, the outer drum, the hub, the friction plate and the like need to be arranged in a very narrow space in consideration of the assemblability. is there. Therefore, it is not always possible to arrange the snap ring on the outer drum side, and it may be necessary to mount the snap ring on the outer peripheral surface of the hub in some cases. In such a case, a snap ring disengagement prevention structure is required separately, but depending on the design, this disengagement prevention structure may be complicated and the assembling property may be deteriorated.

Therefore, the object of the present invention is, in view of the problem that is caused when the snap ring is mounted on the outer peripheral surface of the hub, an automatic transmission for a vehicle in which the snap ring is prevented from coming off due to a centrifugal force with a simple structure. Is to provide a friction plate support structure for the clutch.

[Means for solving problems]

The present invention relates to an automatic transmission for a vehicle including a transmission gear device including a planetary gear and an input path switching device having a plurality of clutches for selectively inputting an output from a torque converter to the transmission gear device. In the friction plate supporting structure of the clutch, the clutch is configured by disposing a large number of friction plates between the outer drum and a hub member arranged inside the outer drum, and the clutch is provided with a recess on the outer peripheral surface of the hub member. A shaft snap ring for restricting axial movement of the friction plate is fitted and mounted in the formed ring groove, and an inner peripheral edge portion of the friction plate adjacent to the snap ring covers the outer peripheral surface of the snap ring. The feature is that a stop recess is formed.

[Action]

In the clutch friction plate support structure of the present invention, the snap ring is attached to the outer peripheral surface of the hub member, and the friction plate adjacent to the hub ring prevents the snap ring from being disengaged. Not only the outer drum but also the hub can be mounted, that is, the mounting position of the snap ring can be freely selected, and the degree of freedom in design can be expanded accordingly. Moreover, the friction plate adjacent to the snap ring is formed with a locking recess that covers the outer peripheral surface of the snap ring, thereby preventing the snap ring from spreading outward, so that a separate member can be used to prevent disengagement. It does not have to be adopted, and the structure does not become complicated.

[Embodiment] An embodiment of the present invention will be described below with reference to the drawings.

1 to 3 show a friction plate supporting structure of a clutch in a Ravigneaux type four-speed automatic transmission according to one embodiment of the present invention.

In the figure, an automatic transmission 30 according to the present embodiment includes a torque converter 1 with a lockup mechanism, first and second sun gears S1, S.
2, a first and second pinion gears P1 and P2, and a transmission gear train 2 including a Ravigneaux gear train including a ring gear 9 and an input path switching device 3 mainly including first to third clutches C1 to C3. ing.

The torque converter 1 is arranged in a converter housing 1c, a pump impeller 1f is connected to a converter case 1e connected to a crankshaft 1d of an engine, and a turbine runner 1a is arranged opposite to the pump impeller 1f. A stator 1g and a one-way clutch 1h are rotatably arranged in between. The input shaft 1b connected to the clutch 1h and the turbine runner 1a is rotatably supported by a support member 18 fixed to the transmission case 13. 1i is a lockup clutch.

The transmission gear device 2 and the input path switching device 3 are arranged in the transmission case 13. The transmission gear device 2
The second sun gear S2 is rotatably arranged around the output side shaft 14 coaxially arranged with the input shaft 1b.
The first sun gear S1 is rotatably arranged on the boss portion 5a of the sun gear S2. The boss portion 8a of the carrier 8 is spline-fitted to the output side shaft 14. The carrier 8 rotatably supports the first and second pinion gears P1 and P2, and the second pinion gear P2 is the second pinion gear P2.
The sun gear S2 and the first pinion gear P1 are the first sun gears.
The gears mesh with S1 and the second piston gear P2. A one-way clutch C4 and a second brake B2 are arranged on the outer peripheral portion 8b of the carrier 8. 16a is a piston for operating the brake B2. Furthermore,
The boss portion 8a of the carrier 8 has the first pinion gear.
A boss portion 9b of an output take-out ring gear 9 meshing with P1 is rotatably mounted, and the boss portion 9b is axially supported by the transmission case 13 via a bearing 13a. A reduction gear 9a is spline-fitted to the axial end of the boss 9b.

The reduction gear 9a is in mesh with the input gear 21a of the counter shaft 21, and the output gear 21b thereof is in mesh with the ring gear 22a of the differential gear device 22. A wheel is attached to the tip of the output shaft 22b of the differential gear device 22.

The first clutch C1 of the input path switching device 3 is a dish-shaped input member 1 having a bottom wall 17b fixed to the input shaft 1b.
A large number of friction plates 10c are arranged between the first hub 10a fixedly formed to the 7 and the first outer drum 10b rotatably supported by the support member 18, and further, in the outer drum 10b functioning as a cylinder. First piston for clutch operation 1
0d is arranged so as to be slidable in the axial direction. A cylindrical transmission member 10e is connected and fixed to the outer drum 10b, and a tip end portion of the cylindrical transmission member 10e is spline-fitted to the first sun gear S1. In addition, B1 is the transmission member 10e
Is a first brake that stops the rotation of the.

As shown in FIG. 1, the second clutch (outer clutch) C2 has a large number of drives between a hub 20a formed in the front portion of the hub member 20 and an outer drum 11a arranged outside the hub 20a. The driven friction plates 25a, 25b are alternately arranged, and the second piston 11c for pressing the driven friction plates 25a, 25b is arranged so as to face the friction plate 25a at the rear end. The front end of the outer drum 11a is spline-fitted to the boss 5a of the second sun gear S2.

The second piston 11c is arranged in the bottom portion of the input member 17 functioning as a cylinder, and pressing boss portions 11d are provided on the peripheral portion of the outer piston 11c at regular intervals. The pressing boss portion 11d faces the friction plate 25a through a through hole 20c formed in a flange portion 20b extending outward at the rear end of the hub member 20. Furthermore, an annular spring receiving plate 23a is arranged on the rear end surface of the flange portion 20b, and a large number of second biasing springs 24a are arranged between this and the second piston 11c. There is. This bias spring 2
Two 4a are arranged between the pressing bosses 11d, and are for urging the second piston 11c to the retracted end position.

A dog groove 20d formed at the rear end of the flange portion 20b of the hub member 20 is engaged with a dog claw 17a protruding from the outer periphery of the input member 17, and these are snap rings for holes 26.
It is fixed at. Also, the inner circumference of each of the friction plates 25a, 25b,
The protrusions formed on the outer circumference are the hub 20a and the outer drum, respectively.
It engages with the engagement groove formed in 11a. Also, the hub 20a
A ring groove 27c is provided at the front end of the outer peripheral surface of the
A shaft snap ring 27a is fitted and attached to this. The snap ring 27a is located in a locking recess 25c formed in the friction plate 25a at the front end adjacent to the snap ring 27a, and the inner peripheral surface of the recess 25c covers the outer peripheral surface of the snap ring 27a.

Here, as shown in FIG. 2, the gap A between the flange portion 20b and the friction plate 25a is wider than the depth B of the locking recess 25c, and this depth B is different from that of the friction plate 25a. It is deeper than the clearance C with the pressing boss portion 11d.

The third clutch (inner clutch) C3 is the hub member described above.
A large number of drives are provided between the inner peripheral surface of the hub 20a of 20 and the inner hub 12a arranged on the inner side of the hub 20a and fixed to the output side shaft 14,
A driven friction plate 12b is arranged, a hole snap ring 27b is attached to the inner peripheral surface of the hub 20a, and a third piston 12c is arranged in the second piston 11c. A large number of third biasing springs 24b are arranged between the spring receiving plate 23b arranged at the end of the input shaft 1b and the third piston 12c. It is for urging to the backward end position.

Next, the function and effect of this embodiment will be described.

Second and third clutches C2, C in the automatic transmission 30 of this embodiment
In the assembly of 3, for the convenience of assembly, first, the friction plates of the second clutch C2 and the third clutch C3 are attached to the hub member 20, and this assembly is attached to the input member 17. The rings 27a and 27b are attached to the outer peripheral surface and the inner peripheral surface of the hub 20a.

First, the procedure for assembling the two clutch parts will be described. The inner friction plate 12b is formed in the inner peripheral surface of the hub 20a of the hub member 20.
Insert and attach the snap ring 27b for holes. Then, the outer friction plates 25a, 25b are fitted on the outer peripheral surface of the hub 20a. At this time, since the clearance A between the friction plate 25a at the rear end and the flange portion 20a is wider than the depth B of the locking recess 25c, when the friction plate is brought into contact with the surface of the flange portion 20b, the ring groove 27c is formed. Will be located outside the friction plate 25a at the front end. Therefore, in this state, the shaft snap ring 27a can be mounted in the ring groove 27c, whereby an assembly of the hub member 20 and each friction plate can be obtained. In parallel with this, the second piston 11c is inserted into the input member 17, and the third piston 12c is inserted into the second piston 11c. In this state, the assembly is mounted so that the dog claw 17a of the input member 17 is engaged in the dog groove 20d of the flange portion 20b thereof, and the hole snap ring 26 is provided at the rear end portion of the flange portion 20b. Fit and install. In this case, since the depth B of the locking recess 25c is formed deeper than the gap C between the friction plate and the tip of the pressing boss portion 11d of the second piston 11c, the shaft snap ring 27a is always provided with the depth. The outer peripheral surface is covered by the locking recess 25c, the outward spreading of the snap ring 27a is prevented, and the snap ring 27a is not disengaged by centrifugal force.

The automatic transmission 30 of the present embodiment selects and inputs the output from the torque converter 1 to any sun gear or carrier by operating the above-mentioned clutches, brakes, etc. in the combinations shown in Table 1. Then, each shift speed is realized by this.

For example, in the case of low speed such as the first speed and the second speed, only the second clutch C2 is operated and the one-way clutch C4 is operated.
Alternatively, the first brake B1 is operated, and in the case of the third speed, the first brake B1 is released from the state of the second speed, and
The third clutch C3 is also activated, and in the case of the 4th speed,
Only the third clutch C3 is activated and the first brake B1 is activated. As a result, the rotation from the torque converter 1 is selectively input to the first and second sun gears S2 and S2 or the carrier 8 via the input member 17 and the first to third clutches C1 to C3, depending on each shift speed. A reduced gear ratio can be obtained.

As described above, in this embodiment, in the second clutch C2, the shaft snap ring 27a is mounted on the outer peripheral surface of the hub 20a. It can be attached to 17 and these assembly work can be done easily and surely.

In this case, as a structure for preventing the shaft snap ring 27a from coming off due to the centrifugal force, a friction plate 25a adjacent to the structure is provided.
A locking recess 25c is formed on the snap ring 27a with the friction plate.
Since the structure that prevents the outward expansion of the is adopted, the detachment prevention structure can be realized very easily.

In the above embodiment, the case where the third clutch is arranged inside the second clutch has been described, but the present invention can be applied to a clutch arranged independently, and in this case, the same as the above embodiment. The effect of is obtained.

[Effect of device]

As described above, according to the friction plate supporting structure of the clutch in the automatic transmission for a vehicle according to the present invention, the snap ring for preventing the axial movement of the friction plate is attached to the outer peripheral surface of the hub, and the snap plate is attached to the friction plate. Since the locking recess that covers the outer peripheral surface of the ring is formed, it has the effect of preventing the snap ring from coming off with a simple structure, and the snap ring can be freely mounted on both the outer drum and the hub, and that is the only reason for the mounting position. This has the effect of increasing the degree of freedom in design.

[Brief description of drawings]

1 to 4 are views for explaining a friction plate supporting structure of a clutch in a Ravigneaux type four-speed automatic transmission according to one embodiment of the present invention, and FIG. 1 is a sectional side view of a main part thereof, FIG. 2 is a schematic view showing the dimensional relationship, FIG. 3 is a sectional plan view of an automatic transmission to which the clutch structure is applied, and FIG.
The figure is a schematic diagram thereof. In the figure, 1 is a torque converter, 2 is a speed change gear device, 3 is an input path switching device, 8 is a carrier, 11a is an outer drum, 20a is a hub, 25a and 25b are friction plates, 25c is a locking recess, and 27a is a snap ring. , 27c is a ring groove, 30 is an automatic transmission, C1 to C3 are first to third clutches, and P1 and P2 are first and first clutches.
The second pinion gears S1 and S2 are the first and second sun gears.

Claims (1)

[Scope of utility model registration request] 1. A transmission gear device comprising a planetary gear, and an input path switching device having a plurality of clutches for selectively inputting an output from a torque converter to a carrier that axially supports a sun gear or a pinion gear of the transmission gear device. In a structure for supporting a friction plate of a clutch in an automatic transmission for a vehicle, the clutch is constituted by arranging a large number of friction plates between an outer drum and a hub member arranged inside thereof. An axial snap ring for restricting axial movement of the friction plate is fitted into a ring groove formed in the outer peripheral surface of the hub member, and an inner peripheral edge portion of the friction plate adjacent to the snap ring. A friction plate support structure for a clutch in an automatic transmission for a vehicle, characterized in that an engaging recess is formed on the outer peripheral surface of the snap ring.