JPH0433462Y2 - - Google Patents

Description

[Detailed explanation of the idea]

[Industrial Field of Application] The present invention relates to a clutch structure in an automatic transmission for a vehicle, and is particularly suitable for a clutch structure in which the axial length can be shortened, which is suitable when two clutches are placed one on top of the other in the radial direction. Regarding structure. [Prior Art] In general, automatic transmissions for vehicles include a speed change gear device consisting of planetary gears, and an input path switching device having a plurality of clutches and brakes for selectively inputting the output from a torque converter to the device. It is equipped with Automatic transmissions for vehicles are generally required to be as compact as possible due to the narrow installation space, but especially for vehicles with transverse engines, automatic transmissions with as short an axial length as possible are required. is requested. Therefore, the inventors of the present invention have developed a clutch structure in which two clutches are placed one on top of the other in the radial direction as an automatic transmission that can shorten the above-mentioned axial length. In this clutch structure, a friction plate is arranged between an outer drum and a hub, and an outer piston is provided to bring the friction plates into pressure contact with each other, thereby forming an outer clutch, which is arranged inside the outer hub. A friction plate is disposed between the inner outer drum and the hub, and an inner piston for driving is provided within the outer piston, thereby forming an inner clutch. In the clutch structure according to the above development, since the two clutches are overlapped in the radial direction, the two clutches are overlapped in the radial direction.
The length in the axial direction is shorter than that in which two clutches are arranged along the axial direction, and the above-mentioned demand for miniaturization can be met. [Problems to be solved by the invention] By the way, in the above-mentioned clutch device, it is necessary to provide a biasing spring for biasing each piston to its rearward end position. Depending on the situation, the axial length may become longer. In particular, when two clutches are arranged doubly in the radial direction as described above, it becomes difficult to secure space for each biasing spring, so the biasing springs have no choice but to be arranged along the axial direction. Easy,
Although each drum and each piston are arranged in duplicate to reduce the axial length, this shortening effect may be impaired by the biasing spring. Therefore, in view of the above-mentioned concerns, the purpose of the present invention is to secure an arrangement space in which, for example, when two clutches are arranged one above the other in the radial direction, the biasing springs also overlap in the radial direction. An object of the present invention is to provide a clutch structure for an automatic transmission for a vehicle in which the length in the axial direction is not increased due to the arrangement of springs. [Means for solving the problem] The present invention includes a speed change gear device consisting of a planetary gear,
In a clutch structure in an automatic transmission for a vehicle, which includes an input path switching device having a plurality of clutches for selectively inputting an output from a torque converter to the transmission gear device, the tip portion of an input member having a cylinder portion. A flange is formed at the rear end of a hub member having a smaller diameter than the input member, and a number of friction plates are disposed between the hub member and the outer drum, and a piston for actuating the clutch is connected to the rear end of the hub member having a smaller diameter than the input member. Pressure bosses are disposed within the cylinder portion and protrude from the peripheral edge of the piston at predetermined pitches to face the friction plate through the through holes of the flange portion. The present invention is characterized in that a biasing spring is disposed between the flange portion and the piston to bias the piston to the rearward end position. [Function] In the clutch structure of the present invention, bosses are provided protruding from the peripheral edge of the clutch actuating piston at predetermined pitches, and biasing springs are provided between the bosses, so that the clutch actuating piston For example, even when the above-mentioned clutches are arranged in duplicate, the space for the biasing springs can be secured so that they overlap in the radial direction, and as a result, the clutch area The axial length of can be effectively shortened. [Example] Hereinafter, an example of the present invention will be described with reference to the drawings. 1 to 4 show a clutch structure of a Ravigneau type 4-speed automatic transmission according to an embodiment of the present invention. In the figure, the automatic transmission 30 of the present embodiment includes a torque converter 1 with a lock-up mechanism, a Ravigneaux gear train consisting of first and second sun gears S1 and S2, first and second pinion gears P1 and P2, and a ring gear 9. The input path switching device 3 mainly consists of first to third clutches C1 to C3. The torque converter 1 is disposed in a converter housing 1c, and a pump impeller 1f is connected to a converter case 1e connected to a clutch shaft 1d of the engine, and a turbine runner 1a is disposed opposite to this. 1g stator between
are arranged rotatably via a one-way clutch 1h. Note that the input shaft 1b connected to the clutch 1h and the turbine runner 1a
is a support member 18 fixed to the transmission case 13
It is rotatably supported by. Also, 1i
is a lockup clutch. The transmission gear device 2 and the input path switching device 3 are arranged within the transmission case 13.
The second sun gear S2 of the transmission gear device 2 is rotatably arranged around an output shaft 14 coaxially arranged with the input shaft 1b, and the second sun gear S2
The first sun gear S1 is rotatably disposed on the second boss portion 5a. Further, a boss portion 8a of the carrier 8 is spline-fitted to the output shaft 14. The first and second pinion gears P1 and P2 are rotatably supported by the carrier 8, and the second pinion gear P2 is connected to the second sun gear S2, and the first pinion gear P1 is connected to the first sun gear S1 and the second sun gear S2. The two piston gears mesh with the two piston gears P2, respectively. Further, a one-way clutch C4 and a second brake B2 are provided on the outer peripheral portion 8b of the carrier 8. Note that 16a is a piston for operating the brake B2. Furthermore, a boss portion 9b of a ring gear clutch meshed with the first pinion gear P1 is rotatably mounted on the boss portion 8a of the carrier 8.
b is connected to the transmission case 13 via the bearing 13a.
It is supported by a shaft. Further, a reduction gear 9a is spline-fitted to an axial end portion of the boss portion 9b. The reduction gear 9a meshes with the input gear 21a of the counter shaft 21, and its output gear 21b meshes with the ring gear 2 of the differential gear device 22.
It meshes with 2a. Further, a wheel is attached to the tip of the output shaft 22b of the differential gear device 22. The first clutch C of the input path switching device 3
1 is a first member fixedly formed on a dish-shaped input member 17 whose bottom wall portion 17b is fixed to the input shaft 1b.
A large number of friction plates 10c are arranged between the hub 10a and the first outer drum 10b which is rotatably supported by the support member 18, and a first piston for actuating the clutch is disposed in the bottom of the outer drum 10b which functions as a cylinder. 10d are arranged so as to be slidable in the axial direction. Further, a cylindrical transmission member 10e is connected to the outer drum 10b, and its tip is spline-fitted to the first sun gear S1. Note that B1 is a first brake that stops the rotation of the transmission member 10e. The second clutch (outer clutch) C2 has a large number of friction plates 11b disposed between a hub 20a formed at the tip of the hub member 20 and an outer drum 11a disposed outwardly. A second piston 11c for pressing is arranged opposite to the friction plate 11b. The outer drum 11a
A front end portion of the sun gear S2 is spline-fitted to the boss portion 5a of the second sun gear S2. In addition, the hub member 2
A flange portion 20b extending outward is integrally formed on the rear end of the input member 17, and the engaging claw formed at the tip of the input member 17 is engaged with the engaging groove of the flange portion 20b. , fixedly supported by a hole snap spring. The second piston 11c is disposed within the cylinder portion 17a of the input member 17,
Pressing boss portions 11d are protruded from the peripheral edge of the piston 11c at regular pitches. This pressing boss portion 11d is the flange portion 20b of the hub member 20.
The friction plate 1 is inserted through the through hole 20c formed in the
I am facing 1b. Furthermore, an annular spring receiving plate 23a is disposed inside the flange portion 20b, and a large number of second biasing springs 2 cylinders a are disposed between this and the second piston 11c. ing. The biasing springs 24a are for biasing the second piston 11c to the rearward end position, and two biasing springs 24a are arranged between each of the pressing boss portions 11d. Further, the third clutch (inner clutch) C3 has a large number of clutches between the inner circumferential surface of the hub 20a of the hub member 20 and the inner inner drum 12a, which is disposed inward of the hub 20a and fixed to the output shaft 14. Inner friction plate 1
2b, and further a third piston 12c is disposed within the second piston 11c. Further, a large number of third biasing springs 24b are disposed between a spring receiving plate 23b disposed at the end of the input shaft 1b and the third piston 12c. This is to urge the to the rearward end position. The third biasing spring 24b and the second biasing spring 24a form concentric circles and substantially overlap in the radial direction. Next, the effects of this embodiment will be explained. In the automatic transmission 30 of this embodiment, each clutch,
By operating the brakes and the like in the combinations shown in Table 1, the output from the torque converter 1 is selectively input to either the sun gear or the carrier, thereby realizing each gear.

[Effect of idea]

As described above, according to the clutch structure of an automatic transmission for a vehicle according to the present invention, a hub member having a flange portion is attached to the input member, and the flange portion is attached to the periphery of the clutch actuation piston disposed on the input member. The press bosses facing the friction plate through the through holes are arranged at predetermined pitches, and between the press bosses,
In addition, since the biasing spring is disposed between the flange and the piston, the biasing spring can be placed by effectively utilizing the peripheral edge of the piston, which was previously unused. This has the effect of solving the problem of elongation of the axial length and promoting miniaturization of the clutch.

[Brief explanation of the drawing]

1 to 4 are diagrams for explaining the clutch structure of a Ravigneau 4-speed automatic transmission according to an embodiment of the present invention, and FIG. 1 is a cross-sectional side view of the main parts thereof, and FIG. FIG. 1 is a sectional view taken along the line 1, FIG. 3 is a sectional plan view of an automatic transmission to which the clutch structure is applied, and FIG. 4 is a schematic diagram thereof. In the figure, 1 is a torque converter, 1b is an input shaft, 2 is a transmission gear, 3 is an input path switching device, 8 is a carrier, 9 is a ring gear, 11a is an outer drum, 11b is a friction plate, 11c is a second piston (clutch) 11d is a pressing boss portion, 17 is an input member, 17a is a cylinder portion,
20 is a hub member, 20b is a flange, 20c is a through hole, 24a is a second biasing spring, C1 to C3 are first to third clutches, P1 and P2 are first and second pinion gears, S1 and S2 are third 1. Second sun gear.

Claims (1)

[Scope of utility model registration request] A vehicle equipped with a transmission gear device consisting of 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 pivotally supports a sun gear or a pinion gear of the transmission gear device. In a clutch structure for an automatic transmission, an input member having a cylinder portion is fixed to an input shaft, a hub member having a smaller diameter than the cylinder portion is disposed in front of the input member, and a flange is formed at the rear end of the hub member. A clutch actuating piston is connected to the tip of the input member, a large number of friction plates are disposed between the hub member and an outer drum disposed outside the hub member, and a clutch actuating piston is connected to the hub member to press the friction plates against each other. Pressure bosses are disposed within the cylinder portion of the input member, and protrude from the peripheral edge of the piston at predetermined pitches to face the friction plate through the through holes formed in the flange portion. 1. A clutch structure for an automatic transmission for a vehicle, characterized in that a biasing spring for biasing the piston to a rearward end position is disposed between the parts and between the flange part and the piston.