JPH0650352A - Clutch drum - Google Patents

Abstract

PURPOSE:To improve the strength of a stopper and dissolve the partial contact of a clutch plate and the seizure of a clutch by forming an inwardly directed flanged by shaping a drum edge part on the opposite side to a piston accommodation part to a hook shape and forming this flange to the stopper for the clutch plate. CONSTITUTION:A drum 1 has a spline 2 in the inner peripheral surface axis line direction, and a clutch plate 3 allow the tooth shape of the peripheral edge part to be meshed with the spline 2, and is shiftable in the axis line direction, and is pressurized by a hydraulic piston 4, and frictionally engaged. The edge part on the opposite side to the piston of the drum 1 as the stopper for the clutch plate 3 is shaped to a hook shape, and an inwardly directed flange 5 is formed, and the drum 1 and the inwardly directed flange 5 are formed to an integral press-molded structure. Accordingly, the dimension of the drum edge part is contracted to the dimension cprresponing to the thickness of the inwardly directed flange 5. Accordingly, the strength of a stopper can be improved, and the clutch plate can be supported in stable manner, and the trouble of the tilt of a snap ring and the cut of the edge of the drum opening can be dissolved effectively.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch drum of a transmission device for a vehicle.

[0002]

2. Description of the Related Art In JP-A-52-41750, as shown in FIG. 8, an axial spline 2 is formed on the inner peripheral surface of a drum 1 and a plurality of clutch plates 3 are fitted in the drum. A clutch drum made of sheet metal is shown which is movable in the axial direction of the spline 2 and meshes with the clutch plate 3 by a hydraulic piston provided at the inner bottom of the drum to obtain frictional engagement. Cage,
In this clutch drum, two upper and lower cuts are formed in the convex tooth portion of the spline, and the gaps between the two cuts are extruded outward to form the slots 5 that are intermittently arranged on the inner peripheral surface of the drum opening end. The snap ring 4 is fitted, the retaining plate 6 is engaged with the snap ring 4, and the clutch plate 3 is engaged via the retaining plate 6.

Further, the drum is integrally press-molded into a cup shape having an opening at one end and a bottom plate at the other end, a clutch plate or the like is incorporated from the opening, and the snap ring is fitted to the opening end as described above. The piston is housed inside the bottom plate.

[0004]

However, in the structure in which the snap ring 4 is fitted into the slot 5 formed by cutting the convex teeth as in the conventional example, the snap ring 4 is strongly pushed up by the piston. As a result, a proper surface contact with the surface of the retaining plate 6 cannot be obtained, and the retaining ring 6 is repeatedly impacted against the retaining plate 6 in a state where the snap ring 4 is bent or inclined, resulting in clutch burning. I have a problem.

In the conventional method of forming the slot 5 by cutting, there is a limit to the depth of the slot, and the projecting size of the snap ring 4 which is naturally fitted in the slot 5, that is, the effective contact area with the retaining plate 6 is sufficient. Have problems that cannot be secured.

Further, the opening end 1a of the drum 1 has a problem that the strength is reduced by half due to the notch formed in the convex tooth portion, and the load is repeatedly applied to the opening end 1a, causing the end of the drum to be cut off.

Since a large number of mechanical parts are complicatedly incorporated in the limited space of the transmission structure, the clutch drum is required to be as small as possible (reduction of occupied space) and as light as possible. I am here. However, due to this demand for downsizing, the dimension between the cut slot into which the snap ring is fitted and the end of the drum cannot be sufficiently secured, and the rigidity of the end of the drum is reduced, resulting in the problem of the above end cutting being promoted.

Further, in the conventional example, since the snap ring has a small amount of engagement, it is essential to have a structure in which the clutch plate 3 is brought into uniform contact with the thick retaining plate 6 having a high rigidity. With the interposition of the plate 6, the drum

[0009]

SUMMARY OF THE INVENTION The present invention provides a clutch drum which solves the above-mentioned problems. As its means, the drum end is shaped like a hook to form an inward flange. The clutch of the clutch plate is formed by the inward flange.

[0010]

The present invention eliminates the conventional structure in which the convex tooth portion at the opening end of the drum is cut and the snap ring is fitted as described above, and the drum end portion is formed into a hook shape so that the inward flange (clutch plate stopper). ) Is formed, the strength of the stopper can be remarkably improved, and the overhanging dimension of the inward flange can be freely increased to provide a stopper that can stably support the clutch plate. It effectively solves the problem of the inclination of the drum and the end of the drum opening. At the same time, it is a useful one that makes the drum smaller and lighter.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in FIGS. The reference numerals are used regardless of FIG.

The drum 1 has an axially extending spline 2 on its inner peripheral surface, and a plurality of clutch plates 3 fitted in the drum. The clutch plate 3 is movable in the drum axial direction by engaging the tooth profile formed on the peripheral edge thereof with the spline 2 and is frictionally engaged with each other by being pressurized by a hydraulic piston 4 provided on the inner bottom of the drum. Has become.

As a means for preventing the clutch plate 3 from popping out, that is, as a stopper, the end of the drum 1 opposite to the piston is shaped like a hook to form an inward flange 5. That is, the drum 1 and the inward flange 5 have an integral press-molding structure without mechanical connection. Such an inward flange 5 is obtained by subjecting a circular plate to upsetting by a press, punching a bottom plate formed by this into a smaller diameter than a drum, and forming a composition by the remaining portion. The inward flange 5 can be formed by upsetting the drum and then bending the open end of the drum inward.

The present invention also includes a case where the bottomed drum is upset, and then a shaft hole required for inserting the transmission shaft 6 is punched out at the center of the drum bottom plate to form the inward flange 5. Therefore, the inward flange 5 has its diametrical dimension freely set, and the clutch plate 3
Can sufficiently secure the supporting area. Therefore, as shown in FIGS. 1, 2 and 7, the clutch plate 3 can be directly supported by the inward flange 5, that is, the retaining plate can be removed. As a result, the dimension of the drum end required to form the stopper of the clutch plate 3

According to the present invention, depending on the embodiment, the clutch plate may be fitted to the inward flange 5 via the retaining plate.
It is also possible to reduce the end of the drum by using the retaining plate, including the case of engaging with.

Reference numeral 7 denotes a clutch hub which is spline-engaged on the inner diameter side of the clutch plate 3.

The inner splined drum 1 is made of a steel plate or the like, and is composed of a sheet metal pulley formed by press forming. As described above, the inward flange 5 is formed by punching a hole in the bottom plate during this press working, or by subsequently inwardly bending the drum opening end. Alternatively, the drum 1 with the inner spline is integrally formed from an aluminum extrusion molded product, and the inward flange 5 is formed by internally bending the open end.

On the other hand, a sheet metal piston accommodating pan 9 made of a press-molded product made of a steel plate is formed, and the piston accommodating pan 9 is at an end portion on the side opposite to the side where the inward flange 5 of the drum 1 is formed. The piston 4 is fitted in the opening and assembled integrally with the drum 1, and the piston 4 is housed inside thereof.

As an example, the piston accommodating pan 9 has a bottom plate 10 concentric with the drum 1 and a rim portion 11 raised from the peripheral edge of the bottom plate 10 in an annular shape, as shown in FIGS. As described above, a thick flange 11b is formed at the open end of the rim portion 11, and a tooth profile 11a corresponding to the spline 2 is formed on the outer peripheral surface of the flange 11b. The portion 11 is fitted in the drum opening portion, and the inner spline 2 and the tooth profile 11a are engaged with each other to bring the both 1 and 9 into a combined state (co-rotating state) with respect to the rotational direction. That is, the rim portion 11 cooperates with the bottom plate 10 to form a torque transmission means for transmitting the rotational drive of the transmission shaft 6 to the drum 1.

As another example, as shown in FIGS. 3 and 4, the tooth profile 11a is formed over the entire width of the outer peripheral surface of the rim portion 11 of the piston housing pan 9 and is meshed with the spline 2 in the same manner. The piston accommodating pan 9 is integrally press-molded at the center thereof, that is, the center of the bottom plate 10, with a boss portion 12 for axially coupling the transmission shaft 6, and the inner wall of the shaft hole 13 and the transmission shaft 6 are spline-connected or key-connected. .

As a means for attaching the piston accommodating pan 9 to the drum 1, as described above, the spline 2 and the tooth profile 11 are used.
1a and 2a to stop rotation, and as shown in FIGS. 1 and 2, the lower surface of the flange 11b of the piston housing pan 9 is engaged with the snap ring 15 to prevent movement in the axial direction.

As another example, as shown in FIGS. 3 and 4,
The snap rings 14 and 15 engage the upper and lower peripheral portions of the rim portion 11 of the piston housing pan 9 to prevent movement in the axial direction. For example, the snap rings 14 and 15 are fitted to the inner peripheral surface of the drum 1, one of the snap rings 14 is engaged with one end of the rim portion 11, and the other snap ring 15 is used for the rim portion 11.
Engages with the other end to prevent axial movement.

The snap rings 14 and 15 have grooves formed on the inner peripheral surface of the drum, for example, the convex teeth of the spline 2, and are removably fitted into the grooves. Since the piston housing pan 9 shown in FIG. 3 and FIG. 4 is supported by a double-supported structure on the snap ring side (outer peripheral end) and the transmission shaft side (inner peripheral end).
Since the axial load during piston operation is distributed to both supporting portions, the same load is not applied only to the snap ring 15, and the stopper of the clutch plate in the conventional example is used.
It does not cause the problem of tilting or drum scraping, such as the snap ring that forms the drum.

In addition to the above-mentioned double-supported structure, the piston housing pan 9 shown in FIGS. 1 and 2 can be fitted with the snap ring 15 engaging with the flange 11b at a position sufficiently inwardly separated from the end surface of the drum 1. Therefore, it is possible to more effectively eliminate the above-mentioned concern about the end of the edge.

As another example, FIG. 5 shows that the spline 2 is not formed on the inner peripheral surface of one opening end of the drum, that is, the spline 2 is terminated at a position that does not reach the end surface of the opening end of the drum. A case is shown in which the piston housing pan 9 is fitted inside, and the end 2a of the spline 2 is prevented from moving inward, and the snap ring 15 is prevented from moving outward. Therefore, one snap ring 15 is sufficient as in FIGS. 1 and 2. The piston accommodating pan 9 and the drum 1 can be connected in the rotational direction by key connection instead of spline engagement, welding, caulking or other concavo-convex connection, or press fitting (tight fit).

As yet another example, the above-mentioned piston accommodating pan 9
As shown in FIG. 6, the drum 1 can be externally fitted and attached to one open end of the drum 1. In this external fitting margin, the both 1, 9 are integrated by caulking, key connection, spline connection, press fitting, or the like.

[0027]

According to the present invention, the end portion of the drum is shaped like a hook to form an inward flange, and this is used as the stopper structure of the clutch plate, so that the strength of the stopper is significantly improved. In addition, it is possible to provide a stopper that can properly secure the overhanging dimension of the inward flange and can stably support the clutch plate, the inclination of the snap ring in the conventional example, and the partial contact of the clutch plate. It is possible to solve the problem of clutch burning and effectively solve the problem of the end of the drum opening.

Further, according to the present invention, the axial dimension of the stopper forming portion of the clutch plate can be reduced as much as possible, and the axial width of the entire drum can be shortened to reduce the size and weight of the drum. Effectively contribute to the design of.

[Brief description of drawings]

FIG. 1 is an exploded perspective view of a drum and a clutch housing pan showing an embodiment of the present invention.

FIG. 2 is an assembled sectional view of the drum, a clutch plate, and a clutch housing pan.

FIG. 3 is an exploded perspective view of a drum and a clutch housing pan showing another example.

FIG. 4 is a sectional view of a clutch drum in which the drum, the clutch housing pan, and the clutch plate are assembled.

FIG. 5 is a sectional view of a drum showing another example of a structure for mounting a clutch housing pan.

FIG. 6 is a sectional view of a main part of a drum showing still another example of the mounting structure.

FIG. 7 is a cross-sectional view of an essential part of a stopper portion of the clutch plate in FIGS. 1 to 4.

FIG. 8 is a sectional view of a main part of a stopper portion of a clutch plate in a conventional example.

[Explanation of symbols]

 1 Drum 2 Spline 3 Clutch plate 4 Piston 5 Inward flange 9 Piston housing pan

Claims (2)

[Claims] 1. A clutch drum in which a plurality of clutch plates slidably fitted in the drum are pressed by a hydraulic piston provided on the inner bottom portion of the drum to be frictionally engaged with each other. A clutch drum, wherein an end portion of the side drum is shaped like a hook to form an inward flange, and the inward flange serves as a stopper for the clutch plate. 2. A clutch drum according to claim 1, wherein a piston accommodating pan is fitted and attached to an opening on the side opposite to the side on which the inward flange of the drum is formed.