JPS6138227A - Hydraulic servo drum of friction clutch - Google Patents

Abstract

PURPOSE:To make a hydraulic servo drum of friction clutch compact by making the piston area of a friction clutch be optimum design size and by making the friction material of a clutch be optimum size independently of piston size. CONSTITUTION:A hydraulic servo drum 3 is composed of a ring shaped member 3c having a barrel shaped section 3b on an outer circumference 3a, a coupling section 3d, and an outer circumference barrel shaped member 3h having a bulkhead guide plate section 3f which is extended from the one end 3e of the coupling section 3d in an axis direction and is opened in radial to guide the bulkhead plates 2a and 2b of a friction material 2 and being extended in the same direction as that of the bulkhead guide plate 3f at the side of an outer circumference with another end 3g of the coupling section 3d bent. For this reason, the piston area of a friction clutch can be made to be optimum design size causing the friction clutch to be compact.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic servo for a friction engagement clutch of an automatic transmission for a vehicle.

[Conventional technology] Conventionally, the hydraulic servo of the friction engagement clutch of an automatic transmission is
A rotatably arranged annular drum consisting of an outer cylindrical part, an inner cylindrical part, and an annular part connecting the two, and an annular drum provided between the outer cylindrical part and the inner cylindrical part of the drum. A friction engagement clutch is engaged by supplying line pressure oil between the drum and the piston. The friction engagement clutch was released by draining the line pressure oil.

[Problems to be Solved by the Invention] However, in a vehicle automatic transmission, when shifting up from second gear to third gear, for example, the transmission shaft and the friction engagement clutch C
2 to the sun gear of the planetary gear set. However, the hydraulic servo C-2 that engages or releases the clutch C2 is composed of an annular hydraulic drum and a piston having a return spring, and there is a large space between the outer circumferential cylindrical part and the inner circumferential cylindrical part of the hydraulic drum. Therefore, the installation area of the piston becomes large, and since the piston is large, the second
When shifting up from 3rd gear to 3rd gear, an engagement shock occurred. Therefore, it is better to have a smaller mounting area for the piston, so if you try to reduce the space between the outer circumferential cylindrical part and the inner circumferential cylindrical part, the hydraulic drum must be changed. Furthermore, the number of friction materials in the clutch varies depending on the vehicle model, and the larger the friction material, the better. For this reason, a problem arises in that the usability of the hydraulic drum is reduced.

In order to reduce shift shock when the friction engagement clutch is engaged, the piston area of the friction engagement device is set to an optimal design size, and the friction material of the clutch is set to an optimal design size regardless of the size of the piston. The purpose of the present invention is to provide a hydraulic servo for a friction engagement clutch for an automatic transmission, which allows the creation of a compact hydraulic servo for a friction engagement element.

[Means for Solving the Problems] As shown in FIG. 1, the hydraulic servo 1 of the friction engagement clutch of the present invention has the friction material 2 of the friction engagement clutch C2 assembled so as to be slidable in the axial direction. In the hydraulic servo 1 of the friction engagement clutch, which includes a hydraulic servo, a body drum 3, and a piston 4 built into the hydraulic servo drum 3, the hydraulic servo drum 3 has an annular shape having a cylindrical portion 3b on an outer periphery 3a. Part 3
C and a joint 3 welded along the outer periphery of the cylindrical portion 3b.
d, which extends in the axial direction from one end 3e of the joint portion 3d and guides the partition plates 2a and 2b of the friction material 2;
It has a partition wall plate guide portion 3f that is open in the radial direction, and the other end 3g of the joint portion 3d is bent to form the partition wall plate guide portion 3f.
and an outer circumferential cylindrical member 3h extending along the outer circumference in the same direction as the outer circumference.

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

An annular member having a cylindrical portion on the outer periphery, a joint welded to the outer periphery of the cylindrical portion, and extending in the axial direction from one end of the joint to guide the partition plate of the friction material. 2, which has a partition wall plate guide part opened in the radial direction, and an outer peripheral cylindrical member extending outward in the same direction as the partition plate guide part by bending the other end of the joint part. Since a separate hydraulic servo drum is provided, the piston area of the friction engagement device can be optimized to reduce shift shock when the friction engagement clutch is engaged, and clutch friction can be reduced regardless of the size of the piston. The material becomes the optimal design size, making it possible to create a hydraulic servo with a compact frictional engagement element.

[Example] The hydraulic servo of the frictional engagement device of the automatic transmission of the present invention is
An explanation will be given based on an embodiment shown in FIG. 3 and FIG.

FIG. 2 shows a cross section of an automatic transmission for a vehicle.

The automatic transmission 100 includes a fluid transmission device (torque converter in this embodiment) 200, a transmission 300, and a hydraulic control device 400.

The transmission 300 includes a first planetary gear set 20, an overdrive planetary gear transmission 10 comprising one multi-disc clutch C01 operated by a hydraulic servo, one multi-disc brake BO1 and one one-way latch FO; 2 planetary gear set 50, 3rd planetary gear set 80, 2 gears operated by hydraulic servo.
1 multi-plate clutch C1, C2, 1 belt brake B
1. Consists of an underdrive planetary gear transmission N40 with three forward speeds and one reverse speed, which includes two multi-disc brakes B2, B3 and two one-way latches F1, F2.

Case 110 of automatic transmission 100 includes a torque converter housing 120 that accommodates torque converter 200;
It consists of a transmission case 1301 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 100.
These torque converter housing 120, transmission case 130, and extension housing 140 are each fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter chamber 121 that is open at the front (engine side) of the torque converter housing 120, and 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 206 disposed opposite 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 is directly coupled to the terminal 7. 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, which serves as a partition wall between the torque converter chamber 121 and the transmission chamber 132, and also serves as a front supporting wall of the transmission 300. Further, the transmission case 13
A cylindrical center support 15 that partitions an overdrive mechanism chamber 133 and an underdrive Il compartment 134 and protrudes rearward is located between the transmission chamber 132 and the underdrive mechanism chamber 134.
An intermediate support wall 159 having a diameter of 8 is separately cast and provided.

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
400 forms the output shaft chamber 141 of the transmission,
The extension housing 140 is provided with an electronically controlled sensor rotor 143 and a speedometer drive gear 144, and a sleeve yoke (not shown) is connected to the propeller shaft (not shown) coaxially with the front support 153 at the rear end. It is inserted.

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 the 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 transmission shaft 14 has its tip inserted into the center hole 13 and comes into rotatable sliding contact with the inner circumferential wall 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 heart. 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.
It is spline-fitted to a seven-lunge plate 82 having a rearwardly protruding shaft support 81 that meshes with the sleeve yoke, and is spline-fitted to the sleeve yoke at the rear part 38. The drive 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 7 flange plates 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 A return spring 26 is provided on the inner race shaft 23 side.
A clutch CO 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 servo B-0 of the brake BO, and a return spring 32 provided on the inner peripheral portion 31 of the tip of the intermediate support wall 159 is fitted.

As shown in FIG. 3, the hydraulic servo 1 of the friction engagement clutch of the present invention is provided at the front in an underdrive mechanism chamber 134, and a second hydraulic servo drum 3 opening at the rear is rotatably mounted on a center support 159. The annular piston built into the second hydraulic servo drum 3 is fitted to form the hydraulic servo C-2 of the clutch C2, and the return spring 5 is attached to the inner circumferential wall and the clutch C is attached to the inner circumferential wall.
2 is installed.

The second hydraulic servo drum 3 has the piston 4 on its outer periphery 3a.
The outer periphery of the piston 4 is a sliding part, and the cylindrical part 3b prevents leakage of line pressure oil, and the inner periphery of the piston 4 is a sliding part,
A snap ring 3m that has a line pressure supply hole 31 formed in the radial direction, a lubricating oil supply hole 2j formed in the return spring 5 of the piston 4, etc., and that locks the retainer ring 31 that locks the return spring 5 at the end 3k. ring groove 3
The center support 1 is made up of an inner circumferential cylindrical part 3ρ forming a shape of n, and a side wall 3q connecting the cylindrical part 3b and the inner circumferential cylindrical part 3p.
59, a joint 3d welded to the outer periphery 3S of the cylindrical portion 3b, a joint 3d extending in the axial direction from one end 3e of the joint 3d, and a clutch. The friction material 2 of C2 is assembled so as to be slidable in the axial direction, and further guides the partition plates 2a and 2b of the friction material 2, and has a partition plate guide portion 3f that is open in the radial direction. The other end of the joint portion 3d is bent 180 degrees to form the partition wall plate guide portion 3.
It consists of an outer cylindrical member 3h extending along the outer periphery 3t in the same direction as f, provided with a belt brake B1 on the outer periphery, and having a distal end 3u spline-fitted to the connecting drum 60.

The piston 4 is slidably operated within the annular plate-shaped portion @3C, and the distal end surface 4b of the outer circumferential portion 4a serves as a pressing surface for the partition wall plate 2a, and the distal end surface 4d of the inner circumferential portion 4C. A return spring 5 is installed between the retainer rings 31, and an oil chamber 4f is formed between the annular plate-shaped member 3C and the side wall 4e. Further, the piston 4 is provided with an O-ring 4h between the annular plate member 3C and the piston 4.゛For this reason, the hydraulic servo 1 of the friction engagement clutch has a large mounting area for the piston 4 of the clutch C2 that is connected to the intermediate transmission shaft 14 and the sun gear S1 of the planetary gear set 50 when shifting up from second speed to third speed. smaller, second
The engagement shock when shifting up from 3rd gear to 3rd gear is reduced. Also, regardless of the size of the piston 4, the clutch C
The friction material 2 of No. 2 has an optimally designed size, and the hydraulic servo 1 of the friction engagement clutch becomes compact.

On the rear side of the second hydraulic servo drum 41, a third hydraulic servo drum 46 is fixed to the rear end portion 15 of the intermediate transmission shaft 14, and is open to the rear and has an annular projection 35 at the front.
An annular piston 47 is fitted between the rear end portion 15 and the outer circumferential wall to form a hydraulic servo C-1 of the clutch C1, 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. A second hydraulic servo drum 41 and a third hydraulic servo drum 46 are connected via a clutch C2. 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 integrally formed with the sun gear shaft 45. In addition, a connecting drum 60, which is formed to cover the second and third hydraulic servo drums 41, 46 and the second planetary gear set 50 in a minimum space, is attached to the outer periphery of the second hydraulic servo drum 41 at its tip. The rear end is connected to the sun gear shaft 45 on the rear side of the second planetary gear set 50, and 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 15 formed on the inside of the brake support wall 157 on the rear side. The piston 17 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 the return spring 79 of the hydraulic servo B-3 is connected to the rear support 156. It is supported by a seven-lunge plate 82 attached to the tip.

The third planetary gear set 80 includes a sun gear S2 integrally formed with the sun gear shaft 45, and a planetary carrier P2.
is connected to the outer race 86 of the front one-way clutch F2 and 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 a shift lever of an automatic transmission.
When the parking (P) position is selected, the parking claw 84 engages with the parking gear 85 to fix the output shaft 36.

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 spline-fitted with an inner race 83 on the rear side of the one-way clutch F1. A one-way clutch F2 is installed in the surplus space 61 on the rear side of the connecting drum 60 outside the second planetary gear set 50.
An annular fourth hydraulic servo drum 12 provided with an opening at the front, and a welded portion 71A that protrudes from a predetermined position within the fourth hydraulic servo drum 72.
The fourth hydraulic servo drum 72 is connected to the fourth hydraulic servo drum 72 by press-molding an intermediate cylinder 71 that prevents oil pressure leakage from the hydraulic servo.
An annular piston 73 fitted between the outer circumferential wall 721 of the fourth hydraulic servo drum 72 and the intermediate cylinder 71, a return spring 74 between the inner circumferential wall of the fourth hydraulic servo drum 72 and the intermediate cylinder 71, and a return spring 74 between the fourth hydraulic servo drum 72 and the piston 73. A hydraulic servo B-2 of the brake B2 is formed from the return spring 14, and the brake B2 is mounted inside the outer peripheral wall. The intermediate cylinder 71 has a diameter that is optimal for the area of the piston 73.

The transmission 300 changes the transmission case 1 according to vehicle driving conditions such as vehicle speed and throttle opening.
The engagement of each clutch and brake is controlled by hydraulic pressure selectively output to the hydraulic servo of each friction engagement device from a hydraulic control device 400 in a valve body 403 built in an oil pan 401 fastened to the lower part of the valve 30 by a bolt 402. The gears are engaged or released, resulting in four forward speeds or one reverse speed change. The operation of each clutch, brake, and one-way clutch and the gear position (RANGE) achieved
- Examples are shown in Table 1.

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

([) indicates that the corresponding one-way clutch engages only in the engine drive state and does not engage in the engine brake state. Furthermore, although the corresponding one-way clutch 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. (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 drawings]

FIG. 1 is a cross-sectional view of a hydraulic servo of a friction engagement clutch of the present invention, FIG. 2 is a cross-sectional view of a vehicle automatic transmission to which the hydraulic servo of a friction engagement clutch of the present invention is applied, and FIG. It is a sectional view of the main part of the figure. In the figure 1...Hydraulic servo drum of friction engagement clutch
2...Friction material 3...Second hydraulic servo drum 3b
... Cylindrical portion 3C... Annular plate member 3d... Joint portion 3f... Partition plate guide portion 3h... Outer circumferential cylindrical member 4... Piston 5... Return spring
100... Automatic transmission 200... Torque converter 300... Transmission 400... Hydraulic control device 721... Outer peripheral wall 722... Inner cylinder

Claims (1)

[Claims] 1) Hydraulic pressure of a friction engagement clutch that includes a hydraulic servo drum to which a friction material of the friction engagement clutch is slidably assembled in the axial direction, and a piston built into the hydraulic servo drum. In the servo, the hydraulic servo drum includes an annular member having a cylindrical portion on the outer periphery, a joint welded to the outer periphery of the cylindrical portion, and an axially extending portion extending from one end of the joint, to reduce the friction. It is for guiding a partition wall plate made of wood, and has a partition wall plate guide part that is open in the radial direction, and the other end of the joint part is bent to extend toward the outer circumferential side in the same direction as the partition wall plate guide part. A hydraulic servo for a friction engagement clutch consisting of an outer circumferential cylindrical member.