JPH0464751A - Automatic transmission - Google Patents

Abstract

PURPOSE:To prevent a snap ring from being enlarged, by locking locking pieces horizontally extending from the outer peripheral edge of a washer disposed between the end faces of a first and a second rotary member, to positions near the outer peripheral edge of the snap ring, to the second rotary member. CONSTITUTION:There is provided a snap ring 156 in order to prevent the engagement between a ring gear R2 and a flange part 131a from being released. Locking pieces 158 are arranged at positions on washer 150 disposed between the ring gear R2 and one end part of an outer race F0a of a one-way clutch F0, being extended horizontally from the outer peripheral edge of the washer 150, near to the outer peripheral edge of the snap ring 156. Further, locking holes 159 are formed in the flange part 131a of a clutch drum 131 at positions corresponding to the locking pieces 131 which are locked thereinto. Accordingly, the enlargement of the snap ring 156 caused by a centrifugal force effected at the ring gear R2 is limited by the locking pieces 158 which abuts against the ring gear.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an automatic transmission having a snap ring expansion prevention device.

(Prior Art) Conventionally, automatic transmissions for automobiles have a plurality of planetary gear sets and friction engagement elements such as brakes and clutches connected to each element of the planetary gear sets. Each gear stage is achieved by selectively engaging the gears.

When the frictional engagement elements are engaged, torque is transmitted between various elements such as between the planetary gear set element and the input shaft, and between the planetary gear set element and the output shaft, but the shafts are mutually tilted between each element. Even in such cases, each element may be spline-fitted in order to transmit torque smoothly.

In that case, while the two elements are transmitting torque through spline fitting, the two elements may move relative to each other in the axial direction and come off. Therefore, a snap ring is fixed to one of the two elements to prevent the other element from being removed.

However, if the snap ring is fixed to the outside of one of the elements, the snap ring may spread and come off from the one element due to the centrifugal force generated as the element rotates.

Therefore, the thickness and width of the snap ring are increased to prevent it from spreading due to centrifugal force during rotation.

(Secret B to be Solved by the Invention) However, in the automatic transmission with the above configuration, the snap ring expansion prevention device is a snap ring.

The plate thickness and plate width of the puller are increased to prevent it from spreading due to centrifugal force during rotation, which is effective for snap rings with small diameters, but as the diameter increases, it is necessary to increase the plate thickness and plate width. There are limits to this, and it is not possible to completely prevent spread due to centrifugal force.

Furthermore, when the thickness and width of the plate are increased, the ease of assembly becomes worse.

The present invention solves the problems of the snap ring spreading prevention device in the conventional automatic transmission described above, and provides an automatic transmission that is easy to assemble and prevents the snap ring from spreading and coming off due to centrifugal force. The purpose is to

(Means for Solving the Problems) For this purpose, the automatic transmission of the present invention includes a first rotating member that is rotatably supported, and a spline fitting on the outside in the radial direction near the end face of the first rotating member. It has a second rotating member that is coupled together, and a third rotating member that is disposed adjacent to the first rotating member so as to be relatively rotatable.

and a snap ring disposed in contact with the second rotating member on the outer periphery of the first rotating member to restrict movement of the second rotating member in the axial direction; The washer has a washer disposed between both end faces of the second rotating member, and the washer has a locking piece extending horizontally from the outer periphery close to the outer periphery of the snap ring,
The locking piece is locked to the second rotating member.

(Operations and Effects of the Invention) According to the present invention, the first rotating member rotatably supported as described above, and the first rotating member spline-fitted on the radially outer side near the end face of the first rotating member. and a third rotating member disposed adjacent to the first rotating member so as to be relatively rotatable, and the second rotating member is arranged on the outer periphery of the first rotating member. a snap ring disposed in abutment to restrict axial movement of the second rotating member; and a washer disposed between both end surfaces of the first rotating member and the second rotating member. The washer has a locking piece extending horizontally from an outer peripheral edge close to the outer peripheral edge of the snap ring, and the locking piece is configured to be locked to the second rotating member. Because of this, the locking piece is located on the outer periphery of the snap ring! I will do it.

Therefore, it is possible to prevent the snap ring from expanding due to centrifugal force.

Moreover, since the locking piece of the washer is locked to the second rotating member, it is possible to prevent the snap ring from spreading while also positioning the washer.

Furthermore, since the locking piece of the one-shoe extends horizontally close to the outer periphery of the snap ring, if the snap ring is not securely fitted into the specified position, the snap ring may get in the way and cause the locking piece to cannot be locked to the second rotating member.

That is, it is possible to prevent defects in assembling the snap ring.

(Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings.

Fig. 1 is a detailed view of the snap ring spreading prevention device in the automatic transmission of the present invention, Fig. 2 is a diagram of the locking state of the washer, Fig. 3 is a sectional view of the automatic transmission of the invention, and Fig. 4 is It is an operation diagram of an automatic transmission.

In the automatic transmission shown in FIG. 3, a transmission section 200 composed of a planetary gear transmission mechanism is disposed between a fluid transmission device 100 and a differential gear 300, and the transmission section 200 is connected to the fluid transmission device 100 side. First transmission section 110
and a second transmission section 120 connected to the differential gear 300 side.

The fluid transmission device 100 includes a front cover 102 connected to an engine output shaft 101, a pump impeller 103 connected to the front cover 102, and a turbine runner 1.
05, a stator 107 connected to the automatic transmission case via a one-way clutch 106, and a direct coupling clutch 108.
It is a torque converter consisting of.

The first transmission section 110 has the output shaft of the fluid transmission device, that is, the input shaft 10 of the transmission, and a sleeve section 10a is fixed to the rear end of the input shaft 10. Further, a ring-shaped clutch drum 12 is fixed to the sleeve portion 10a.

A first movable member 15 is arranged in an oil-tight manner on the inner circumferential surface of the clutch drum 2, and the drum 12 and the movable member 15 are used for a first clutch (forward clutch) C4, which will be described later. A hydraulic actuator 16 is configured. Further, a second movable member 17 is arranged in an oil-tight manner on the inner peripheral surface of the first movable member 15.
, and the second movable member 17 to connect a second clutch (described later).
A hydraulic actuator 19 for the reverse clutch (reverse clutch) C2 is configured.

On the other hand, a rear cover (case) 11 is fixed to the tip of the transaxle case 14 with bolts or the like, and an annular step 11b is formed on the rear cover 11. Sleeve part 20
is fixed.

Further, a piston member 22 is installed on the inner circumferential surface of the cylinder member 21 in an oil-tight manner, and the cylinder member 21 and the piston member 22 form a third clutch (overdrive clutch 7) C0 and C0, which will be described later. Fifth clutch (F0
This constitutes a hydraulic actuator 23 for clutches) C, .

On the other hand, a planetary gear unit 30 housed in the transaxle case 14 includes a single planetary gear 31 and a dual planetary gear 32. The single planetary gear 31 includes a sun gear S, a ring gear R, and a carrier CR that supports a binion that meshes with these gears.
The dual planetary gear 32 consists of a carrier CR that supports a sun gear S, a ring gear R1, a first pinion P1 that meshes with the sun gear S, and a second pinion (not shown) that meshes with the ring gear R2 so as to mesh with each other. Become.

Both of these planetary gears 31 and 32 consist of a single gear with the same number of teeth, and the sun gear S is formed on a hollow shaft, and
The carrier CR is integrally constructed, and one of the pinions is constructed as a long pinion.

The first clutch C1 is connected to the clutch drum 12.
and the ring gear R5 of the single planetary gear 31, and the second clutch C2 is interposed between the clutch drum 1 and the ring gear R5 of the single planetary gear 31.
2 and sun gear S.

Further, the third clutch C0 is interposed between the clutch drum 12 and a drum member 26 extending from the ring gear R2 of the dual planetary gear 32, and the fifth clutch Con is interposed between the drum member 26 and the single planetary gear 3J. A one-way clutch F0 is interposed between the ring gear R1 and the ring gear R1.

Note that a third clutch C0 is provided along the inner circumferential surface of the drum 26.
A connecting member 25 is disposed between the third and fifth clutches C, , and thereby the third and fifth clutches Co+
Coa is actuated simultaneously by the above-mentioned hydraulic actuators 23.

A hub portion 11a is formed on the rear cover 11, and a sleeve portion 10a fixed to the rear end portion of the input shaft 10 is fitted into the hub portion 11a. Furthermore, the hub portion 11
An oil passage 11c is formed in a, and the core oil passage 11c supplies hydraulic pressure to the actuator 16.19 and the lubricating oil hole 10b in the input shaft 10 through an oil hole formed in the sleeve portion 10a.

Further, the ring gear R2 is connected to the transaxle case 14 via a third brake B and a one-way clutch F2. The sun gear S extends to the front side and is connected to the transaxle case 14 via a one-way clutch, a first brake B, and a second brake B2, and is also connected to the transaxle case 14 via a first brake B. be done.

Furthermore, the carrier CR has a counter drive gear 1.
12 is attached.

The second transmission section 120 has a countershaft 121 disposed parallel to the input shaft 10 of the first transmission section 110, and a rotatably external part of the countershaft 21 on the fluid transmission device 100 side. The fourth gear is fitted and engaged with or releases the output shaft 123 supported by the countershaft 121, the planetary gear unit 24, and the planetary gear unit 124 to perform underdrive of the two forward stages. The counter drive gear 1 of the first transmission section 110 is located at the end of the counter shaft 121.
A counter driven gear 122 that meshes with the output shaft 123 is attached, and an output gear 125 is formed on the output shaft 123.

The differential gear 300 is the second transmission section 12
It is composed of a large driving gear 301 that meshes with an output gear 125 of 0, a gear box 302, a differential gear 303, and output shafts 304 and 305 that are connected to an axle.

Next, details of the snap ring expansion prevention device will be explained with reference to FIGS. 1 and 2.

In the figure, a sleeve portion 10a is fixed to the rear end side of the input shaft 10, that is, the side facing away from the engine, and a clutch drum 12 is further fixed to the sleeve portion 10a, which are integrated with the input shaft 10. It is designed to rotate.

On the other hand, the rear cover 11 is formed with a hub portion 11a and a lid, the hub portion 11a supports the sleeve portion 10a of the input shaft 10, and the hub portion 11d supports the sleeve support member 20.
The sleeve portion 20 of the cylinder member 21 is fitted through the hole a.

The cylinder member 21, which is formed integrally with the sleeve portion 20 and extends, has a clutch drum 131 at its outer peripheral edge.
The connection is fixed. And the clutch drum 1
31 and the clutch drum 12 are engaged and disengaged by a third clutch C0. The third clutch C8 is formed by a plurality of H diaphragms 132,
An end of the piston member 22 is disposed opposite to the friction plate 132 so as to be movable toward and away from the friction plate 132.

Then, when oil is supplied to the hydraulic actuator 23 formed by the cylinder member 21 and the piston member 22,
The piston member 22 moves to engage the friction plate 132, thereby transmitting the torque of the input shaft 10 to the clutch drum 12, the friction plate 32, and the clutch drum 131.

At this time, the friction plate 132 moves via the connecting member 25 and is transmitted to the fifth clutch C0s.
0, are engaged at the same time. Therefore, the torque of the clutch drum 12 is simultaneously transmitted to the one-way clutch F0 via the fifth clutch C0.

On the other hand, the hydraulic actuator 16 for the first clutch CI
The first movable member 15 constituting the hydraulic actuator 16 moves by supplying oil to the hydraulic actuator 16 to engage the first clutch C1. At this time, the torque of the input shaft 10 is transmitted to the ring gear R1 via the first clutch C1. The ring gear R is also the inner race of the one-way clutch F0.

Here, in the R range, the second clutch C2 is engaged as shown in FIG. 4, the torque of the input shaft 1o is transmitted to the sun gear S, and the ring gear R2 is fixed by the operation of the third brake B3. Therefore, ring gear R
Reverse 3. Therefore, the outer race F on of the one-way clutch F0 is placed in a rotating state.

Therefore, the outer race F of the one-way clutch Fo. There is a relative rotation between , and ring gear R2,
A washer 150 is disposed between both end faces.

Further, the counter drive gear 112 is rotatably supported by a partition wall 152 formed in the axle case 151 via a double-chip bar ring 153.
Moreover, the boss portion is connected to the carrier CR. The outer race of the above-mentioned double Cheebird bearing 153 is
The inner race Fzb of the one-way clutch F2 is spline-fitted to the inner peripheral surface of the partition wall 152, and the inner race Fzb of the one-way clutch F2 is similarly spline-fitted to the outer peripheral surface of the extension of the outer race. The outer race F2m of the one-way clutch F2 is fixed to the ring gear R2 and rotates integrally with the ring gear R2.

A third brake B3 is disposed between the ring gear R2 and the axle case 151. The third brake B3 is engaged and disengaged by a hydraulic actuator 154 formed on one side of the partition wall 152.

The ring gear R2 is spline-engaged with the flange portion 131a of the clutch drum 131 at the outer peripheral edge near the end on the one-way clutch F0 side, and transmits the torque transmitted to the clutch drum 131 to the ring gear. In order to prevent the ring gear R2 and the flange portion 131a from moving relatively in the axial direction and disengaging from the spline engagement between the two, the ring gear R2 is snapped onto the outer peripheral edge of the ring gear R2 at a position adjacent to the flange portion 131a. ring 1
56 are arranged.

The snap ring 156 has a normal horseshoe shape and is snapped onto the ring gear R2. Above, clutch drum 131 and ring gear R
2, when the third clutch C0 is engaged, it rotates at the same high speed as the engine, so the centrifugal force generated in the snap ring 156 is high, causing the snap ring 156 to expand.
It may come off.

Therefore, a locking piece 158 extending horizontally from the outer peripheral edge of the washer 150 disposed at the end of the outer race Fox of the ring gear R2 and the one-way clutch F is integrally formed. The locking pieces 158 are provided at several locations on the circumference of the washer 150 and extend close to the outer peripheral edge of the snap ring 156. And the clutch drum 131
A locking hole 159 is formed at a location corresponding to the locking piece 158 of the flange portion 131a.
8 is locked.

Therefore, when the snap ring 156 tries to expand due to the centrifugal force generated in the ring gear R2, it hits the locking piece 58 and its movement is restricted.

Note that the present invention is not limited to the above embodiments,
Various modifications are possible based on the spirit of the present invention, and these are not excluded from the scope of the present invention.

[Brief explanation of the drawing]

Fig. 1 is a detailed view of the snap ring spreading prevention device in the automatic transmission iR of the present invention, Fig. 2 is a diagram of the locking state of the washer, Fig. 3 is a sectional view of the automatic transmission of the present invention, and Fig. 4 is an operational diagram of an automatic transmission. DESCRIPTION OF SYMBOLS 1... Automatic transmission, 131... Clutch drum (second rotating member'), 150... Washer, 156...
... Snap ring, 158... Locking piece, 159...
・Latching hole, R2...Ring gear (first rotating member),
F,... Outer race (second rotating member). 5B

Claims (1)

[Claims] a first rotating member rotatably supported; a second rotating member spline-fitted on the radially outer side near the end face of the first rotating member; a third rotating member that is rotatably disposed; and a third rotating member that is disposed in contact with the second rotating member on the outer periphery of the first rotating member, and restricts movement of the second rotating member in the axial direction. It has a snap ring and a washer disposed between both end faces of the first rotating member and the second rotating member,
The automatic transmission is characterized in that the washer has a locking piece extending horizontally from the outer periphery of the snap ring close to the outer periphery of the snap ring, and the locking piece is locked to the second rotating member. Machine.