JPH0456172B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Field of Application] The present invention relates to a hydraulic servo for a vehicle automatic transmission, and more particularly to a fixing member used to axially fix an annular member of the hydraulic servo to an automatic transmission case. [Prior Art] Conventionally, automatic transmissions for vehicles are provided with frictional engagement devices such as brakes and clutches for controlling gear shifts, and hydraulic servos for operating these frictional engagement devices. For example, a hydraulic servo for a friction engagement brake is an annular member that consists of an outer cylinder, an inner cylinder, and a side wall that connects the outer cylinder and the inner cylinder, and is fixed in the axial direction with a snap spring inside the automatic transmission case. It consists of a certain annular hydraulic drum, a piston provided between an outer cylinder and an inner cylinder of the annular hydraulic drum, and a return spring provided outside the outer cylinder or in the inner cylinder, and the hydraulic servo drum and the piston. The friction engagement brake is engaged by supplying line pressure oil between the lines, and the friction engagement brake is released by discharging the line pressure oil. [Problems to be Solved by the Invention] In the conventional hydraulic servo, as described above, the annular member of the hydraulic servo is simply fixed by a general snap spring. However, with this kind of Snappring,
Not only is it easy for the annular member of the hydraulic servo to rattle, but the large axial load from the line pressure oil is repeatedly applied to the snap spring, which can cause the snap spring to slip out of the groove in which it fits. There is. The present invention was made in view of these problems, and its purpose is to ensure that the fixing ring of the annular member of the hydraulic servo does not come off even when the fixing ring receives an axial load. The object of the present invention is to provide a hydraulic servo for an automatic transmission that can prevent the above problems. [Means for Solving the Problems] In order to achieve the above-mentioned objects, the present invention provides an automatic transmission case in which an inner spline is formed on the inner periphery, and a spline fitting between the inner spline of the automatic transmission case and the spline. and an annular member formed on the outer periphery of the outer spline, and the automatic transmission case includes a trapezoidal ring groove in the inner spline portion to which a tapered ring is attached, and one end of the outer periphery of the annular member. and locking means for locking in the axial direction, the annular member has one end of its outer circumferential portion locked to the locking means of the automatic transmission case, and the other end of the annular member having a tapered ring mounted in the ring groove. In a hydraulic servo for an automatic transmission that is fixed in the axial direction by a ring, the tapered ring has a contact surface with the annular member and a curved part that contacts an inclined part of the trapezoidal ring groove. The load point, which is a contact point of the contact surface with the outer peripheral portion of the annular member, is provided on the inner peripheral side of the fulcrum, which is the contact point with the slope of the trapezoidal ring groove of the curved surface portion. It is characterized by being [Operation and Effects of the Invention] According to the hydraulic servo for an automatic transmission according to the present invention configured as described above, the load point, which is the contact point of the contact surface with the outer peripheral portion of the annular member, is located on the curved surface. Since it is provided on the inner circumferential side of the fulcrum which is the point of contact with the sloped part of the trapezoidal ring groove of the shaped part,
Even if the tapered ring receives an axial force, it is prevented from coming off. In particular, by setting the radial distance between the load point and the fulcrum of the tapered ring to 1 mm or less, even if an axial force is applied to the tapered ring, the moment acting on the tapered ring becomes small.
As a result, the tapered ring is prevented from coming off. Furthermore, by forming the corners between the outer and inner circumferential parts of the tapered ring and both end faces into a curved shape, it is possible to prevent the tapered ring from getting caught when assembling it, making it easier to assemble the tapered ring. This prevents reaction concentration and improves durability. [Example] The present invention will be explained based on an example shown in the drawings. 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, a first gear set 20 operated by a hydraulic servo.
1 multi-disc clutch C0, 1 multi-disc brake B
0, and one one-way clutch F0, a second planetary gear set 50, a third planetary gear set 80, two multi-disc clutches C1, C2, operated by hydraulic servos. One belt brake B1, two multi-disc brakes B2, B3, and 2
3 forward speeds and 1 reverse speed underdrive planetary gear transmission 40 with two one-way clutches F1 and F2
It consists of A case 110 of the automatic transmission 100 includes a torque converter housing 120 that houses a torque converter 200, an overdrive planetary gear transmission 10, and an underdrive planetary gear transmission 40.
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 is fastened with multiple 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;
An annular plate-shaped rear cover 112 welded to the front cover 111 at the outer periphery, and a pump impeller 20 disposed around the inner wall of the rear cover 112.
5. a turbine runner 206 disposed opposite the pump impeller 205; a turbine runner 20;
6, a stator 201 supported on a fixed shaft 203 via a one-way clutch 202, and the front cover 1.
11 and the turbine shell 207 is provided. The torque converter chamber 121 and the transmission case 1 connected to the rear thereof
Between the transmission case 130 and the cylindrical transmission chamber 132, there is an annular oil pump body 151 which is provided with a gear type oil pump 150 therein and has a cylindrical portion 152 protruding forward in the center thereof. A cylindrical front support 153 is provided on the rear side of the oil pump body 151 and has a coaxial center with the cylindrical portion 152 and projects rearward. oil pump cover 154 with
is fastened. The oil pump body 151 and the oil pump cover 154 are an oil pump housing 155.
It forms 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. Also,
An overdrive mechanism chamber 133 is located in the middle of the transmission chamber 132 of the Noran transmission case 130.
An intermediate support wall 159 is separately cast and provided, which separates the underdrive mechanism chamber 134 from the underdrive mechanism chamber 134 and has a cylindrical center support 158 that projects rearward. At the rear of the transmission case 130,
A rear support wall 157 having a cylindrical rear support 156 projecting forward is integrally cast with the transmission case 130. The oil pump housing (front support wall or bulkhead) 1
55 and the rear support wall 157 forms a transmission chamber 132 that houses the transmission 300,
Rear support wall 157 and extension housing 1
40 forms an output shaft chamber 141 of the transmission, and the extension housing 140 is provided with an electronically controlled sensor rotor 143 and a speedometer drive gear 144, and the rear end is provided with an output shaft chamber 141 coaxial with the front support 153. is connected to a propeller shaft (not shown), and a sleeve yoke (not shown) is inserted therethrough. 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 fixed shaft 203. 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 arranged in series with a coaxial center;
is rotatably provided. The intermediate transmission shaft 14 has its tip aligned with the center hole 1.
3, it rotatably slides into contact with the inner circumferential wall of the center hole 13 via a metal bearing, the rear end 15 has a large diameter, and a rearward-facing center 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. Output shaft 3
6 is a third planetary gear set 8 at the intermediate portion 37.
The sensor rotor is spline-fitted with a flange plate 82 provided with a rearwardly protruding shaft support 81 that meshes with the ring gear R2 of No. 0, and is spline-fitted with the sleeve yoke at the rear part 38. 143 and speedometer drive gear 144 are fixed. In the overdrive mechanism chamber 133, a first planetary gear set 2 is provided on the rear side of the input shaft 11.
0 is provided, the ring gear R0 is connected to the intermediate transmission shaft 14 via a flange plate 22, and the platenary carrier P0 is connected to the flange portion 12a of the input shaft 11.
The sun gear S0 is connected to the inner race shaft 23.
is formed. 1st planetary gear set 2
On the front side of clutch C0, 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 peripheral wall of the first hydraulic servo drum 24 and the inner race shaft 23.
-0, a return spring 26 is attached to the inner race shaft 23 side, and a clutch C0 is attached to the inner side of the outer peripheral wall, and is connected to a planetary carrier P0 via the clutch C0. A one-way clutch F0 having the inner race shaft 23 as an inner race is provided on the inner periphery of the first hydraulic servo drum 24, and a clutch C0 and a brake B0 are provided on the outer periphery between the outer race 27 and the transmission case 130. Rear intermediate support wall 15
The piston 29 is fitted into the front side of the brake B
0 hydraulic servo B-0 is formed, and the intermediate support wall 159
A return spring 32 provided on the inner peripheral portion 31 of the tip 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 the inner and outer circumferential walls of the second hydraulic servo drum 41 to rotate the clutch C2. A hydraulic servo C-2 is formed and a return spring 4 is installed on the inner peripheral wall side.
4. A clutch C2 is installed inside the outer peripheral wall. On the rear side of the second hydraulic servo drum 41,
A third hydraulic servo drum 46 that is open at the rear and has an annular protrusion 35 at the front is fixed to the rear end 15 of the intermediate transmission shaft 14, and an annular piston 47 is fitted between the rear end 15 and the outer peripheral wall. A hydraulic servo C-1 of the clutch C1 is formed, and a return spring 49 and an annular projection 35 are provided on the inner circumferential side.
A clutch C2 is attached to the outer periphery of the clutch C2.
via the second hydraulic servo drum 41, and the third
A hydraulic servo drum 46 is connected. On the rear side of the third hydraulic servo drum 46, a second
A planetary gear set 50 is provided, a ring gear R1 of which is connected to the third hydraulic servo drum 46 via an annular projection 48 and a clutch C1, a planetary carrier P1 is spline-fitted to the tip of the output shaft 36, and a sun gear S1 is integrally formed with the sun gear shaft 45. In addition, the second hydraulic servo drum and the third hydraulic servo drum 41, 4
6 and the second planetary gear set 50 in a minimum space.
is fixed at its tip to the outer periphery of the second hydraulic servo drum 41, and its 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 periphery side. An inner line 7 formed inside the transmission case 130 on the rear side of the brake B2.
5 shows, from the front, the brake disc b2 of the brake B2, the outer spline 1a of the fourth hydraulic servo drum 1, and the brake disc b3 of the brake B3.
is spline-fitted, and the rear support wall 15 on the rear side
A piston 77 is fitted into an annular hole between the outer peripheral side of the rear support 156 of No. 7 and the transmission case 130 to form a hydraulic servo B3 of the brake B3, and a return spring 79 of the hydraulic servo B-3 is connected to the rear support 156. It is supported by a retainer attached to the tip. The third planetary gear set 80 is a sun gear S
2 is formed integrally with the sun gear shaft 45, and the planetary carrier P2 is connected to the outer race 86 of the front one-way clutch F2, and the brake B3
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. When the shift lever of the automatic transmission is set to the parking position P, the parking claw 84 engages with the parking gear 85 to fix the output shaft 36. In the surplus space 61 on the rear side of the connecting drum 60 on the outside of the second planetary gear set 50, a fourth hydraulic servo drum, which is an annular member 1A fixed to a fixed member or a rotating member in the automatic transmission case according to the present invention, is provided. 1 is provided. The fourth hydraulic servo drum 1 is disposed with an open front as shown in FIG. and inner cylinder 1
d and is formed by a press into a U-shaped cross section. Further, by machining, an inner spline 1f is formed on the inner periphery of the inner cylinder 1d, and an outer spline 1a is formed on the outer periphery of the outer cylinder 1b to be spline-fitted with the spline of the transmission case 130. Transmission case 13
0 and the fourth hydraulic servo drum 4, the fourth hydraulic servo drum 1 is fixed to the transmission case 130 in the rotational direction. Further, as shown in FIG. 1, the fourth hydraulic servo drum 1 is fixed in the axial direction by a tapered ring 3 and a step portion 2c, which is a locking means, formed on the transmission case 130. and,
The fourth hydraulic servo drum 1 is supported by the tapered ring 3 when a pressing force is applied in the axial direction when the brake B3 is engaged on the rear side of the hydraulic servo B-2. A press-molded intermediate cylinder 1h is connected to the fourth hydraulic servo drum 1 at a welded portion 1g, and this intermediate cylinder 1h allows the hydraulic servo B-2
Hydraulic leakage is prevented. As shown in FIGS. 6, 7, 8, and 9, a connecting tool to be described later is attached to one end surface 4f of the inner circumferential side 4e, and the outer circumferential side 4h
A piston body 4a consisting of one end 4b having a hole 4g open on the front side, and an adapter in which the one end 4b of the piston body 4a is covered by an L-shaped wall rear side 4c as shown in FIGS. 10, 11 and 12. A piston 4 consisting of a sleeve 4d and having improved ease of assembly of the tapered ring 3 that fixes the fourth hydraulic servo drum 1 to the transmission case 130 is attached to the fourth hydraulic servo drum 1 at a predetermined position within the drum 1. It is fitted between the intermediate cylinder 1h protruding from the position to form a hydraulic servo B-2 of the brake B2, and the intermediate cylinder 1h has an optimum diameter for the area of the piston 4. As described later, the outer periphery of the inner cylinder 1d and the intermediate cylinder 1h
A piston return spring 93 is disposed in a space between the piston and the inner periphery of the piston, and one end of this return spring 93 is connected to the piston via a connector, and the other end is connected to the piston via a retainer. 4 is connected to the hydraulic servo drum 1. Therefore, the fourth hydraulic servo drum 1 also functions as a reaction plate for the return spring 93. As shown in FIG. 1, the tapered ring 3 is arranged such that a part of its outer circumferential side is fitted into a ring groove 2b formed in the automatic transmission case 130. Further, as shown in FIGS. 13, 14 and 15, one end surface 3a of the tapered ring 3 also has an outer peripheral end 3a.
k is an inclined surface 31. Furthermore, the outer circumferential end 3c of one end surface 3a and both ends 3d, 3e of the other end surface 3b are curved parts 3f, 3g, 3h (radius r: 0.2 to 0.9 mm).
This prevents stress concentration. Furthermore, the boundary point between the inner peripheral end 3j of the one end surface 3a, the inclined surface 3l of the one end surface 3a, and the other surface 3m of the one end surface 3a,
Curved portions 3i and 3n each having a larger radius than the curved portions 3f, 3g, and 3h (radius r: 0.2 to 0.9 mm)
It is said that Slanted surface 31 of one end surface 3a and one end surface 3
By making the boundary point between a and the other surface 3m the curved portion 3n, the tapered ring 3 is prevented from getting caught. A curved portion 3n of one end surface 3a (front surface) is in contact with the inclined surface of the ring groove 2b, and the other end surface (rear surface) 3b is in contact with the tip end surface 1c of the outer cylinder 1b of the fourth hydraulic servo drum 1. ing. Then, as described above, the pressing force when the brake B3 is engaged is applied in the axial direction to the other end surface 3b via the fourth hydraulic servo drum 1. In that case, the point of contact of the other end surface 3b with the tip end surface 1c of the outer cylinder 1b, that is, the load point A, is 0.5 mm radially inward from the point of contact between the curved portion 3n and the inclined surface of the ring groove 2b, that is, the fulcrum B. is set to .
Conventionally, the load point A is set to 2.0 mm, so in the case of this embodiment, the load point A is set extremely close to the fulcrum B. By doing this, the moment due to the load applied to the tapered ring 3 is reduced. This prevents the tapered lung 3 from slipping out of the groove 2b. Further, by setting the distance C between the other end surface 3b and the inner spline 2a to be close to 0 mm, the inclination angle of the tapered ring 3 can be made small. Note that in the figure, 3p and 3q are holes formed at both ends r and s, and when removing the tapered ring 3, a wedge-shaped removal fitting such as a screwdriver is inserted into the holes 3p and 3q. The locking means may be a tapered ring other than a step provided on the transmission case,
Also, other materials may be used. The return biasing means 90 has one end 91a fixed to one end surface 4f of the inner peripheral side 4e of the piston 4, and the other end 91b rotated around from the inner peripheral side 1i of the intermediate cylinder 1h to the other end 1j of the intermediate cylinder 1h. Inserted connector 9
1, the other end 921 is fixed to one end 1k of the inner cylinder 1d, and the outer periphery 94 of a ring 94 is fixed to a snap ring 95 fixed to one end 1k of the inner cylinder 1d.
1, and a return spring 93 disposed between the connector 91 and the retainer 92. The transmission 300 operates according to vehicle running conditions such as vehicle speed and throttle opening from a hydraulic control device 400 in a valve body 403 built in an oil pan 401 fastened to the lower part of the transmission case 130 with bolts 402. The hydraulic pressure selectively output to the hydraulic servo of the frictional engagement device engages or releases each clutch and brake, resulting in four forward speeds or one reverse speed change. Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the gear ranges achieved.

[Table] 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 engine drive conditions and not in engine brake conditions. Furthermore, although L is engaged in the corresponding one-way clutch engine drive state, this engagement is not necessarily required since power transmission is guaranteed by a clutch or brake built in parallel. Indicates that (lock). Furthermore, f indicates that the corresponding one-way clutch is free. Additionally, an x indicates that the corresponding clutch and brake are released.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of a fixed member or annular plate-shaped member fixed to a rotating member in an automatic transmission case of the present invention, and FIG. 2 is a sectional view of a fixed member or rotating member in an automatic transmission case of the present invention. 3 is a sectional view of the main part of FIG. 2, and FIG. 4 is a sectional view of a fixed member in the automatic transmission case of the present invention or A front view of a hydraulic servo drum attached to an annular plate member fixed to a rotating member, FIG. 5 is a sectional view taken along line AA in FIG. 4, and FIG. FIG. 7 is a front view of one side of the piston attached to the annular plate member fixed to the rotating member, FIG. 7 is a sectional view taken along line BB in FIG. 6, and FIG. FIG. 9 is a sectional view of the other side of the piston attached to the annular member fixed to the rotating member, and FIG. 9 is a cross-sectional view of the piston attached to the annular plate member fixed to the fixed member or rotating member in the automatic transmission case of the present invention. Fig. 10 is a sectional view of the adapter sleeve, Fig. 11 is a front view of Fig. 10, Fig. 12 is a sectional view of the adapter sleeve, Fig. 13 is a front view of the tapered ring, and Fig. 14 is Fig. 13. side view, No. 15
The figure is a sectional view of FIG. 14. In the figure 1... An annular plate-shaped member fixed to a fixed member or rotating member in the automatic transmission case, 2b...
...Ring groove, 2d...Slope portion, 3...Tapered ring, 3a...One end surface, 3n...Curved surface portion, 10
0... Automatic transmission, 200... Torque converter, 300... Transmission, 400...
Hydraulic control device.

Claims (1)

[Claims] 1. An automatic transmission case having an inner spline formed on its inner periphery, and an annular member having an outer spline formed on its outer periphery to be spline-fitted with the inner spline of the automatic transmission case, The automatic transmission case has a trapezoidal ring groove in the inner spline portion to which a tapered ring is attached, and a locking means for locking one end of the outer peripheral portion of the annular member in the axial direction, In a hydraulic servo for an automatic transmission, the member has one end of its outer peripheral portion locked by a locking means of the automatic transmission case, and the other end fixed in the axial direction by a tapered ring installed in the ring groove, The tapered ring has a contact surface with the annular member and a curved portion that contacts the slope of the trapezoidal ring groove, and the contact point of the contact surface with the outer peripheral portion of the annular member A hydraulic servo for an automatic transmission, characterized in that a load point is provided on the inner circumferential side of a fulcrum that is a contact point of the curved surface portion with the sloped portion of the trapezoidal ring groove. 2. The hydraulic servo for an automatic transmission according to claim 1, wherein the radial distance between the load point and the fulcrum of the tapered ring is 1 mm or less. 3. The hydraulic servo for an automatic transmission according to claim 2, wherein the corners between the outer and inner circumferences of the tapered ring and both end surfaces are curved.