JPS6141047A - Hydraulic servo mechanism of frictional engagement device - Google Patents

Abstract

PURPOSE:To facilitate assembling a snap ring which is installed on a case of an automatic speed change gear after a piston is assembled in an annular hydraulic servo by forming a piston of a hydraulic servo mechanism by a piston body and an adapter sleeve in a two-split structure. CONSTITUTION:A hydraulic servo 1 of a frictional engagement device in a transmission includes a hydraulic servo drum 2 having an outer cylinder 2a and an inner cylinder 2b, an intermediate cylinder 71 welded to the middle portion of a side wall 2c of the drum 2, and a piston 3 fitted in space between the outer cylinder 2a and the intermediate cylinder 71. The hydraulic servo drum 2 is fixed by fitting a snap ring to a ring groove of the case inner wall. In this case, the piston 3 comprises a piston body 3b fitted between the outer cylinder 2a and the intermediate cylinder 71 and an adapter sleeve 3c, wherein the sleeve 3c is formed in such a manner that one end 3a of the piston body 3b can be covered with a L-shaped wall portion.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic servo mechanism of a friction engagement device of an automatic transmission for a vehicle, and mainly relates to a friction engagement brake.

[Prior Art] Generally, a hydraulic servo mechanism for a frictional engagement device includes an annular hydraulic servo drum consisting of an outer cylinder, an inner cylinder, and a side wall, an annular piston installed between the outer cylinder and the inner cylinder, and This automatic transmission case includes a return spring that always biases the piston toward the side wall, and a snap ring that locks the end surface of the outer cylinder and fixes the annular hydraulic servo drum. When assembling the hydraulic servo mechanism of the frictional engagement device, the annular hydraulic servo drum, piston, and return spring are roughly set aside in advance and assembled into the case.

[Problems to be Solved by the Invention] Conventionally, however, when line pressure oil is supplied into the hydraulic servo, the piston biases the friction material of the friction engagement device, so that the piston is moved closer to the end surface of the hydraulic servo drum. If the end face of the piston is made to protrude in this way, and the snap ring is assembled after the piston is assembled to the hydraulic servo drum in the assembly process, There is a problem that the snap ring cannot be assembled.

By dividing the piston into two parts, the piston body and the adapter sleeve, the piston can be attached to the case of a vehicle automatic transmission after the piston is assembled to the annular hydraulic servo, and the axial direction can be fixed with a snap ring. The purpose of the present invention is to provide a hydraulic servo mechanism for an engagement device.

[Means for solving the problems] The hydraulic servo mechanism 1 of the frictional engagement device of the present invention has an outer cylinder 2a.
, an annular hydraulic servo drum 2 consisting of an inner cylinder 2b and a side wall 2C, a piston 3 installed between the outer cylinder 2a and the inner cylinder 2b, and a return spring that always biases the piston 3 against the side wall 2C. 4, and the tip surface 2d of the outer cylinder 2a.
and a cylindrical member such as the transmission case 130 of the case 110 of a vehicle automatic transmission to which a snap ring such as a Cheever ring 5 is attached which locks the hydraulic servo drum 2 and fixes the hydraulic servo drum 2. 3a
It consists of a piston body 3b formed to be substantially the same as the tip end surface of the outer cylinder 2a, and an adapter sleeve 3C that is assembled to the end surface 3a after attaching a snap ring such as the Cheever ring 5 during assembly. That is the composition.

[Operations and Effects of the Invention] With the above configuration, the hydraulic servo mechanism of the frictional engagement device of the present invention has the following operations and effects.

The piston has a piston body whose end surface is approximately the same as the tip surface of the outer cylinder of the annular hydraulic servo drum, and a snap ring is attached to the cylindrical member during assembly to fix the hydraulic servo drum in the axial direction. After that, it consists of an adapter sleeve that is attached to the end face of the piston body, and because of this two-part structure, it is easy to attach the snap ring after assembling the annular hydraulic servo drum, piston, and return spring, and attaching it to the cylindrical member. Can be done.

[Example code] Next, the present invention will be explained based on embodiments shown in the drawings.

Automatic transmission 1 ioo includes a fluid transmission device (torque converter in this embodiment) 200 and a transmission 300.
and a hydraulic control device 400.

The transmission 300 includes an overdrive planetary gear transmission @10 comprising a first planetary gear set 20, one multi-disc clutch C01 operated by a hydraulic servo, one multi-disc brake BO, and one one-way latch FO; 2 planetary gear set 50, 3rd planetary gear set 80, 2 multi-disc clutches C1, C2 operated by hydraulic servo, 1 belt brake B1
．． It is comprised of an underdrive planetary gear transmission 40 with three forward speeds and one reverse speed, which includes two multi-disc brakes B2 and B3 and two one-way latches F1 and F2.

Case 110 of automatic transmission 100 includes a torque converter housing 120 that accommodates torque converter 200;
It consists of a transmission case 130 that houses the overdrive planetary gear transmission 10 and the underdrive planetary gear transmission 40 in series, and an extension housing 140 that covers the rear side of the automatic transmission 1a 100. These torque converter housing 120 and the transmission The case 130 and the extension housing 140 are each fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 121 that is open at the front (engine side) of the torque converter housing 120, includes a front cover 111 connected to the output shaft of the engine, and a circular ring welded to the front cover 111 at the outer periphery. A plate-shaped rear cover 112, a pump impeller 205 disposed around the inner peripheral wall of the rear cover 112, a turbine runner 2O6 disposed opposite to the pump impeller 205, and a turbine shell holding the turbine launch 206. 207, one-way clutch 20
a stator 201 supported by a fixed shaft 203 via 2;
and the front cover 111 and the turbine shell 20
7 is provided with a direct coupling clutch (lock-up clutch) 113 that directly couples between the torque converter chamber 12 and the torque converter chamber 12.
1 and the cylindrical transmission chamber 132 of the transmission case 130, which is continuous to the rear thereof, is provided with a gear type oil pump 150 therein and an annular transmission chamber 150 having a cylindrical portion 152 protruding forward in the center thereof. The oil pump body 151 is fitted into the front end of the transmission case 130 with a spigot and is fastened, and the rear side of the oil pump body 151 has a coaxial center with the cylindrical part 152 and projects rearward. An oil pump cover 154 having a cylindrical front support 153 is fastened.

The oil pump body 151 and the oil pump cover 1
Reference numeral 54 forms an oil pump housing 155, serves as a partition wall between the torque converter chamber 121 and the transmission chamber 132, and also serves as a front support wall of the transmission 300. Further, the transmission case 130
The overdrive mechanism chamber 1 is located in the middle of the transmission chamber 132.
33 and the underdrive mechanism chamber 134, and an intermediate support wall 159 is separately cast and provided to the right of a cylindrical center support 158 that projects rearward.

At the rear of the transmission case 130, there is a rear support wall 1 having a cylindrical rear support 156 that projects forward.
57 is integrally cast with the transmission case 130. The space between the oil pump housing (front support wall or partition wall) 155 and the rear support wall 157 constitutes a transmission chamber 132 in which the transmission 300 is housed, and the rear support wall 157 and the extension housing 1
The space between 40 and 7 forms the output shaft chamber 141 of the transmission.
, the extension housing 140 includes an electronically controlled sensor rotor 143 and a speedometer drive gear 144.
A sleeve yoke (not shown), which is connected to a propeller shaft (not shown) coaxially with the front support 153, is inserted through the rear end portion.

The fixed shaft 20 is located inside the front support 153.
The input shaft 11 of the transmission, which is the output shaft of the torque converter 200, is rotatably supported inside the shaft 3. The input shaft 11 has a large diameter rear end portion 12 having a flange portion 12a projecting rearward from a front support 153, and a rearward center hole 13 is formed in the axis of the rear end portion 12. An input shaft 11 is located behind the input shaft 11.
An intermediate transmission shaft 14 having a coaxial center and arranged in series is rotatably provided.

The intermediate power transmission shaft 14 has its tip inserted into the center hole 13 and comes into rotatable sliding contact with the inner periphery of the center hole 13 via a metal bearing, and its rear end 15 has a large diameter. A rearwardly facing central hole 16 is formed in the axis. An output shaft 36 is rotatably provided behind the intermediate transmission shaft 14 and is coaxial with the intermediate transmission shaft 14 and arranged in series. The tip of the output shaft 36 is inserted into the center hole 16 of the intermediate transmission shaft 14 and is in sliding contact with the inner wall of the center hole 16 via a metal bearing. The output shaft 36 is connected to the ring gear R2 of the third planetary gear set 80 at the intermediate portion 37.
The sensor rotor 143 and the speedometer drive are spline-fitted to a flange plate 82 provided with a rearwardly protruding shaft support 81 that meshes with the sleeve yoke at the rear part 38. Gear 144 is fixed.

In the overdrive mechanism chamber 133, the input shaft 1
A first planetary gear set 20 is provided on the rear side of the
The ring gear RO has a flange plate 22 on the intermediate transmission shaft 14.
The planetary carrier PO is connected to the input shaft 1 through
The sun gear SO is connected to the flange portion 12a of the inner race shaft 23 and is formed on the inner race shaft 23. On the front side of the first planetary gear set 20, a first hydraulic servo drum 24 that opens rearward is fixed to an inner race shaft 23, and an annular piston 25 is fitted between the outer circumferential wall and the inner race shaft 23, and a clutch CO In addition to forming the hydraulic servo C-0, a return spring 26 is provided on the inner race shaft 23 side.
A clutch GO is installed inside the outer peripheral wall, and the clutch C
It is connected to the planetary carrier PO via O.

An inner race shaft 23 is attached to the inner circumference of the first hydraulic servo drum 24.
A one-way latch FO with an inner race is provided,
A clutch Co and a brake BO are provided on the outer periphery between the outer race 27 and the transmission case 130, and a piston 29 is provided on the front side of the intermediate support wall 159 on the rear side.
is fitted to form a hydraulic pressure valve B70 of the brake BO, and a return spring 32 provided on the inner circumference 31 of the tip of the intermediate support wall 159 is fitted.

Inside the underdrive mechanism chamber 134, at the front, a second hydraulic servo drum 41 that opens rearward is rotatably fitted onto the center support 159, and an annular piston 42 is fitted between its inner and outer circumferential walls to operate the clutch C2. In addition to forming a hydraulic servo C-2, a return spring 44 is attached to the inner circumferential wall, and a clutch C2 is attached to the inner side of the outer circumferential wall. On the rear side of the second hydraulic servo drum 41, a third hydraulic servo drum 46 which is open to the rear and has an annular projection 35 at the front is fixed to the rear end 15 of the intermediate transmission shaft 14, and is connected to the rear end 15. An annular piston 4 between the outer peripheral wall
7 is fitted to form the hydraulic servo C-1 of the clutch C1, and a return spring 49 is attached to the inner circumferential side, and a clutch C2 is attached to the outer circumference of the annular projection 35, and the second hydraulic servo drum 41 and Third
A hydraulic servo drum 46 is connected.

A second planetary gear set 50 is provided on the rear side of the third hydraulic servo drum 46, the ring gear R1 of which is connected to the third hydraulic servo drum 46 via an annular projection 48 and a clutch C1, and a planetary carrier P1. is spline-fitted to the tip of the output shaft 36, and the sun gear S1
is formed integrally with the sun gear shaft 45. Also, the second
Hydraulic servo drum and third hydraulic servo drum 41.4
6 and the second planetary gear set 50 in a minimum space, the connecting drum 60 is fixed at its tip to the outer periphery of the second hydraulic servo drum 41, and its rear end is fixed to the outer circumference of the second hydraulic servo drum 41.
The ring gear shaft 45 is located on the rear side of the second planetary gear set 50.
A belt brake B1 is provided on the outer peripheral side.

Transmission case 1 on the rear side of the brake B2
30, the brake disc b2 of the brake B2, the outer spline 725 of the fourth hydraulic servo drum 72, and the brake disc b3 of the brake B3 are spline-fitted from the front to the spline 75 formed inside the rear support wall 157 on the rear side. A piston 77 is fitted into an annular hole between the outer peripheral side of the rear support 156 and the transmission case 130 to form a hydraulic servo B-3 of the brake B3, and seven return springs of the hydraulic servo B-3 are connected to the rear support 156. It is supported by a retainer attached to the tip.

A one-way latch F1 having the sun gear shaft 45 as an inner race is provided inside the brake B2, an outer race 39 is connected to the brake B2, and a return biasing means 90 and a return biasing means 90 are provided on the rear side of the one-way clutch "1". A one-sided clutch F2 is installed in which an inner race 83 is spline-fitted to the fourth hydraulic servo drum 70 at its outer inner diameter.

The third planetary gear set 80 includes a sun gear S2 integrally formed with the sun gear shaft 45, and a planetary carrier P.
2 is connected to the 7-wheel race 86 of the one-way latch F2 on the front side, and is also connected to the brake B3, and a ring gear R2 having a parking gear 85 around its outer periphery is connected to the intermediate portion 37 of the output shaft 36. .

The parking gear 85 is activated when the shift lever of the automatic transmission is selected to the parking (P) position.
4 meshes with the parking gear 85 to fix the output shaft 36.

As shown in FIG. 3, the hydraulic zarpo 1 of the frictional engagement device of the present invention is provided with a one-way latch F1 having the sun gear shaft 45 as an inner race inside the brake B2, and three outer races are connected to the brake B2. A one-way clutch F2 is connected to the one-way clutch F1 and is spline-fitted between a fourth extraction sarpodrum having an inner race 83 on the rear side of the one-way clutch F1 and an outer spline 83c formed on the outer circumferential side 83b of the small diameter portion 83a. , an extra space 61 on the rear side of the connecting drum 60 outside the second planetary gear set 50
, an annular fourth hydraulic servo drum 72 provided with a front opening and protruding from a predetermined position within the fourth hydraulic servo drum 72 , and a welded portion 7 between the fourth hydraulic servo drum 72 and the fourth hydraulic servo drum 72 .
1A, an intermediate cylinder 71 that prevents oil pressure leakage of the hydraulic servo is press-molded, and an annular piston 73 fitted between the outer cylinder 721 of the fourth hydraulic servo drum 72 and the intermediate cylinder 71, The return spring 74, the fourth hydraulic servo drum 72, the piston 73, and the return spring 74 form the hydraulic servo B-2 of the brake B2 between the inner circumferential wall of the fourth hydraulic servo drum 72 and the intermediate cylinder 71, and the inner circumferential wall Brake B2 is installed on the .

The intermediate cylinder 71 has a diameter that is optimal for the area of the piston 73.

As shown in FIG. 3.4, the fourth hydraulic servo drum 72 includes an outer cylinder 721, an inner cylinder 722, and a side wall 723 connecting the two.
an inner spline 724, which is formed into a U-shaped cross section by pressing, and is spline-fitted to the outer spline 83c on the outer circumferential side 83b of the small diameter portion 83a of the inner race 83 of the one-way clutch F2 on the inner circumference by processing;
An outer spline 725 that is spline-fitted with the spline 75 of the transmission case 130 is formed on the outer periphery, and is fixed to the transmission case 130 in the rotational direction by the outer spline 725, so that the reaction of the inner race 83 of the one-way clutch F2 is transferred to the transmission case 130. The backing is fixed in the axial direction from the tapered drawlough 33, which is a snap ring, and the step 726 formed in the transmission case 130, and receives a pressing force when the brake B3 is engaged on the rear side of the hydraulic servo B-2. The tapered roller t33 also serves as a plate and supports this axial pressing force. Furthermore, a ring groove 728 is formed in one end 727 of the inner cylinder 722 to fix a return spring to be described later. Also, the intermediate cylinder 11 is connected to the welded part 71A of the intermediate part 729 of the side wall 723 of the fourth hydraulic V-bod drum 72, and overlooks the seven-ring part 71B press-molded to prevent oil pressure leakage from the hydraulic servo B-2. It is set up.

In this embodiment, the piston 73 includes an outer cylinder 721 and an intermediate cylinder 71.
As shown in FIG.
A hole 73 (
The piston body 73A has one end surface 73e having a diameter of 9.10.
As shown in FIG. 11, it consists of an adapter sleeve 73B that is covered by a rear side (right side in the figure) 73g of a single-shaped wall portion 73[ and has a hole 731 opened on the front side (left side in the figure) 73h.

As shown in FIGS. 12 to 17, the return spring 4 has one end 91a fixed to one end surface 73b of the inner peripheral side 73a of the piston 73, and the other end 91b connected to the inner peripheral side 711 of the intermediate cylinder 71. The other end 921 is fixed to the snap ring 95 fixed to the ring groove 728 of the one end 727 of the inner cylinder 722, and the ring 94 fixed to the snap ring 95 is connected to the coupling tool 91 that is passed around the other end. Outer circumference 941
retainer 92 with one end 922 wrapped around to engage with
It is installed between.

The piston 73 and return spring 4 are connected to a retainer 92 and a snap ring 95 within the fourth hydraulic servo drum 72.
The fourth hydraulic servo drum member becomes an integral fourth hydraulic servo drum member, and can be easily assembled into the transmission case 130.

Although the distance between the friction material of the friction engagement device and the end surface of the piston body differs depending on the friction engagement device, it is only necessary to change the adapter sleeve, and the annular hydraulic servo drum, piston body, and return spring can be connected to each friction engagement device. Can be shared.

The transmission 300 controls a hydraulic control device 400 in a lubricant body 403, which is built into an oil pan 401 connected to the lower part of the transmission case 130 by a pole 402, depending on vehicle running conditions such as vehicle speed and throttle opening. The hydraulic pressure selectively output to the hydraulic servo of each friction engagement device engages or releases each clutch and brake, resulting in four forward gear shifts or one reverse shift.
It is designed to change gears. The operation of each clutch, brake, and one-way clutch and the gear position achieved (RAN
Examples of GE) are shown in Table 1.

Table 1 In Table 1, E indicates that the corresponding clutch, brake, or one-way clutch is engaged.

(L) indicates that the corresponding one-way clutch is engaged only in the engine drive state and is not engaged in the engine brake state. Furthermore, although the corresponding one-way clutch of L is engaged in the engine drive state, its engagement is not necessarily required because power transmission is guaranteed by a clutch or brake built in parallel with it. (lock). Roughly f indicates that the corresponding one-way clutch is free. A rough X indicates that the corresponding clutch and brake are released.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of a hydraulic servo of a frictional engagement device for an automatic transmission according to the present invention, and FIG. 2 is a cross-sectional view of a vehicle automatic transmission to which the frictional engagement device for an automatic transmission according to the present invention is applied. Figure 3 is the second
4 is a front view of the hydraulic servo drum connected to the hydraulic servo of the frictional engagement device of the automatic transmission of the present invention. FIG. 5 is a sectional view taken along line AA in FIG. Figure 6 is a front view of one side of the piston connected to the hydraulic servo of the frictional engagement device of the automatic transmission of the present invention, Figure 7 is a sectional view taken along line BB in Figure 6, and Figure 8 is the automatic transmission of the present invention. FIG. 9 is a cross-sectional view of the other piston connected to the hydraulic servo of the frictional engagement device of the automatic transmission of the present invention, and FIG. 10 is a cross-sectional view of the adapter sleeve. figure,
11 is a front view of FIG. 10, FIG. 12 is an enlarged sectional view of FIG. FIG. 14 is a sectional view of FIG. 13, FIG. 15 is a front view of a coupling device and return spring connected to the hydraulic servo of the frictional engagement device of the automatic transmission of the present invention, and FIG. 16 is a sectional view of FIG. 15. FIG. 17 is a front view of a retainer connected to a hydraulic servo of a frictional engagement device for an automatic transmission according to the present invention, and FIG. 18 is a sectional view taken along line CC in FIG. 17. .

Claims (1)

[Scope of Claims] 1) An annular hydraulic servo drum consisting of an outer cylinder, an inner cylinder, and a side wall, and a piston installed between the outer cylinder and the inner cylinder,
A hydraulic servo friction engagement device comprising a return spring that always urges the piston toward the side wall, and a cylindrical member fitted with a snap ring that locks the tip end face of the outer cylinder and fixes the hydraulic servo drum. A hydraulic servo mechanism for a frictional engagement device, comprising: the piston body; and an adapter sleeve that is assembled to the piston after the snap ring is attached during assembly.