JP2514713B2 - Transmission clutch drum - Google Patents

Description

TECHNICAL FIELD The present invention relates to a clutch drum of a transmission.

(B) Conventional Technology As a clutch drum of a conventional transmission, for example, Japanese Patent Laid-Open No.
There is one disclosed in Japanese Patent Laid-Open No. 64-30961. The clutch drum of the transmission shown therein has a sun gear spline-coupled to the input shaft, and a drum-shaped press member welded to the sun gear. The sun gear and the drum-shaped press member are connected to each other by electron beam welding the inner diameter portion of the drum-shaped press member at the end surface of the sun gear. The stopper mechanism for positioning the piston housed in the clutch drum in the returning direction is composed of a stopper portion on the bottom surface of the clutch drum and a projection portion of the piston. The axial support of the clutch drum is performed by a thrust bearing provided on the innermost diameter side of the clutch drum.

(C) Problems to be Solved by the Invention However, the clutch drum of the conventional transmission as described above is supported by the thrust bearing on the innermost diameter side and the stopper portion is arranged on the outer diameter side.
A large moment acts on the clutch drum by the force that always acts from the return spring of the piston. Therefore, the clutch drum needs to have a rigidity that can withstand a large moment. For this purpose, it is necessary to increase the thickness of the clutch drum. As a result,
Weight increases with increasing axial dimension. Further, since the thrust force acting on the sun gear is supported by the drum-shaped press member through the welded portion between the sun gear and the drum-shaped press member, the welded portion has not only the force in the rotational direction but also the force in the thrust direction. Will work,
The structure is disadvantageous in terms of strength of the welded part. The present invention aims to solve the above problems.

(D) Means for Solving the Problem The present invention provides a rotary shaft provided with a flange portion, a drum-shaped press member is welded to the outer periphery of the flange portion, and the stopper portion of the piston and the thrust bearing are supported on both surfaces of the flange portion. The above problem is solved by arranging the surfaces.
That is, the present invention is directed to a clutch drum (50) of a transmission in which a drum-shaped press member (51) and a rotary shaft (52) are integrated by welding. A flange portion (54) protruding in the radial direction is provided over the outer circumference, and welding is performed at the fitting portion between the outer diameter of the flange portion and the inner diameter of the drum-shaped press member, and the piston (56 is housed in the clutch drum. ) A drum side stopper (54a) for contacting and stopping the protrusion (56a) provided on the piston (56) is provided on the flange-like portion, and a thrust bearing (66) for axially supporting the clutch drum is provided. The supporting surface (54b) of (1) is provided on the surface of the flange opposite to the drum-side stopper portion arrangement position. The reference numerals in parentheses indicate the corresponding members in the embodiments described later.

(E) Action The stopper portion for stopping the piston and the support surface of the thrust bearing are arranged on both sides of the corresponding position of the flange portion of the rotary shaft. Therefore, the force from the piston does not act on the drum-shaped press member, and the rigidity of the drum-shaped press member can be reduced. Further, since the thrust force acting on the rotary shaft is supported by the thrust bearing via the flange portion, the thrust force does not act on the welded portion between the drum-shaped press member and the flange portion.

(F) Embodiment FIG. 2 shows a skeleton diagram of an automatic transmission (automatic transaxle). The automatic transmission coupled to the engine 10 mounted laterally with respect to the vehicle, that is, in a direction orthogonal to the vehicle front-rear direction, has a torque converter 12, a planetary gear speed change mechanism 14, a differential mechanism 16, and the like. Engine 10
The torque converter 12 to which the rotation from is input has a pump impeller 18, a turbine runner 20, a stator 22, and a lockup clutch 24. Turbine runner 20
Is connected to the input shaft 26 and lockup clutch 24
Pump impeller 18 to the input shaft 26
The rotational force is transmitted to the input shaft 26 via the fluid, and when the lockup clutch 24 is engaged, the rotational force is mechanically input to the input shaft 26. The lock-up clutch 24 operates by a differential pressure between the apply chamber T / A and the release chamber T / R. The torque converter 12 is configured to drive the oil pump 28. The planetary gear transmission 14 has a first planetary gear set G1 and a second planetary gear set G2, and the first planetary gear set G1 is
First sun gear S1, first internal gear R1, both gears
The first planetary gear set G2 includes a second sun gear S2, a second internal gear R2, and both gears. Second meshing with S2 and R2 at the same time
The second pinion carrier PC2 supports the pinion gear P2. The first sun gear S1 is always connected to the input shaft 26, and the first pinion carrier PC1 and the second internal gear R2 are always connected to the output shaft 30. The first internal gear R1 is a forward one-way clutch F / O and a forward clutch F that are arranged in series.
It is connectable to the second pinion carrier PC2 via / C and via the overrun clutch O / C arranged in parallel with these. The second sun gear S2 can be connected to the input shaft 26 via the reverse clutch R / C, and the second pinion carrier PC2 can be connected to the input shaft 26 via the high clutch H / C. The second sun gear S2 can be fixed to the stationary portion by a band brake B / B, and the second pinion carrier PC2 has a low one-way clutch L / O and a low and reverse brake L & R / B arranged in parallel with each other. It can be fixed to the stationary part via. An output gear 32 is provided integrally with the output shaft 30. An idler gear 34 is provided so as to mesh with the output gear 32, and a reduction gear 36 is connected to the idler gear 34 via an idler shaft 35 so as to rotate integrally. The reduction gear 36 meshes with the link gear 38 of the differential mechanism 16. Differential mechanism 16
Drive shafts 40 and 42 project left and right from this, to which the left and right front wheels are connected.

This planetary gear transmission 14 has clutch F / C, H / C, O / C
And R / C, brakes B / B and L & R / B, and one-way clutches F / O and L / O in various combinations to actuate each element (S1, S2, R1, R2) of the planetary gear set G1 and G2. , PC
It is possible to change the rotation state of 1 and PC2) to obtain 4 forward speeds and 1 reverse speed.

By the operation of the planetary gear speed change mechanism 14 as described above, the rotation of the input shaft 26 undergoes a predetermined speed change and is output to the output shaft 30.
The rotational force of the output shaft 30 is transmitted to the ring gear 38 of the differential mechanism 16 via the output gear 32, the idler gear 34, and the reduction gear 36. Thus, the left and right front wheels can be driven via the drive shafts 40 and 42. By doing so, it is possible to perform automatic forward four-speed shift with overdrive.

Next, FIG. 1 is an enlarged sectional view of a clutch drum portion of a transmission, which is directly related to the present invention, as an actual sectional view. The clutch drum 50 that constitutes the high clutch H / C includes a drum-shaped press member 51 and an input shaft 52 (rotary shaft) to which the rotational force from the torque converter 12 is input.
The input shaft 52 has a flange portion 54 protruding to the outer peripheral portion. A drum-shaped press member 51 is electron beam welded to the outer peripheral portion of the flange portion 54. A piston 56 is attached to a cylinder formed by the drum-shaped press member 51 and the shaft portion of the input shaft 52.
Are fitted together. The piston 56 has a protruding portion 56a at a position closer to the inner diameter portion, which is the first portion of the flange portion 54.
It is arranged so as to contact the side surface (stopper portion 54a) on the left side in the figure. The piston 5 is constantly receiving a rightward returning force in FIG. 1 from a spring 60 held by a spring retainer 58. The piston 56 can apply a pressing force to the plurality of clutch plates 62, whereby the drum-shaped press member 51 and the hub 64 can be connected or disconnected. The right end surface of the flange portion 54 in FIG. 1 (support surface 54
A thrust bearing 66 is arranged between b) and the left end surface of the oil pump housing 59 in FIG. A reverse clutch R / C is installed on the shaft of the oil pump housing 59.
The clutch drum 70 of is rotatably supported.

Next, the operation of this embodiment will be described. A torque is input to the input shaft 52 from the torque converter 12, and the drum-shaped press member 51 also rotates integrally with the input shaft 52. Piston 56
When a hydraulic pressure that pushes this to the left in FIG. 1 is applied, the clutch plate 62 is engaged by the frictional force, and the hub 64 is in a state of rotating integrally with the drum-shaped press member 51. When the hydraulic pressure does not act on the piston 56, the piston 56 is pushed back to the position shown in FIG. 1 by the spring 60. In this state, the piston 56 is in contact with the stopper portion 54a of the flange portion 54 at the protrusion 56a. Therefore,
The return force of the spring 60 does not act on the drum-shaped press member 5, but is directly supported by the flange portion 54. Therefore, the moment generated by the spring 60 does not act on the drum-shaped press member 51, and the rigidity of the drum-shaped press member 51 may be small.
The plate thickness of can be made relatively small. Also, the input shaft
An axial force (thrust force) acts on 52, but the thrust force to the right in FIG. 1 is supported by a thrust bearing 66. Therefore, the thrust force does not act on the drum-shaped press member 51, and the thrust force does not act on the welded portion between the flange portion 54 and the drum-shaped press member 51, which is advantageous in strength.

(G) Effects of the Invention As described above, according to the present invention, the rotary shaft is provided with the flange portion, the drum-shaped press member is welded to the outer periphery of the flange portion, and the piston is stopped on one surface of the flange portion. Since the thrust bearing is placed on the other surface side of the flange part as the stopper part, the force from the piston does not act on the drum-shaped press member, and the thrust force acting on the rotating shaft also acts on the flange part and the drum-shaped press member. Does not work on welded parts. This makes it possible to reduce the wall thickness of the drum-shaped press member and is advantageous in terms of strength of the welded portion.

[Brief description of drawings]

FIG. 1 is a diagram showing an embodiment of the present invention, and FIG. 2 is a diagram showing the entire transmission. 50 …… Clutch drum, 51 …… Drum-shaped press member, 52
...... Input shaft (rotary shaft), 54 …… Flange part, 54a …… Stopper part, 54b …… Support surface, 56 …… Piston, 66 …… Thrust bearing.

Claims (1)

(57) [Claims] 1. A clutch drum of a transmission in which a drum-shaped press member and a rotary shaft are integrally formed by welding, and a rotary shaft is provided with a flange portion that projects in the radial direction over the entire outer circumference of the rotary shaft. The welding is performed at the fitting portion between the outer diameter of the drum portion and the inner diameter of the drum-shaped pressing member, and the drum-side stopper portion that stops the piston accommodated in the clutch drum by contacting the projection portion provided on this piston is the flange portion. A clutch drum for a transmission, characterized in that a support surface of a thrust bearing which is provided on the flange and supports the clutch drum in an axial direction is provided on a surface of the flange portion opposite to a drum-side stopper portion arrangement position.