JPH0656192B2 - Servo drum rotation support device for automatic transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to a servo drum rotation support device for an automatic transmission.

[Conventional technology]

A hydraulic servo that engages and disengages multiple disc clutches, multiple disc brakes, etc. is provided in the shift case of the automatic transmission, and the servo drum that constitutes the cylinder of the hydraulic servo is supported by the transmission case via a support. Has been done.

Since hydraulic oil is supplied to the inside of the servo cylinder by communication between the oil groove formed on the support and the port formed on the servo drum, conventionally, the sliding support surface has conventionally been operated in the axial direction of the hydraulic oil. A seal ring for preventing leakage was interposed, and the seal ring was directly fitted in the seal ring groove of the support.

[Problems to be solved by the invention]

By the way, recently from the demand for weight reduction of automatic converters,
Although the support is made of aluminum, improvements have been made,
The seal ring made of synthetic resin such as polytetrafluoroethylene, which is normally used because of its good sealing property, is not compatible with this type of material, and the support made of aluminum supports the seal ring made of synthetic resin directly. Can not be used.

On the other hand, the oil passage sealed by the seal ring is an oil passage that guides hydraulic pressure for engaging and disengaging the multi-disc clutch, the multi-disc brake, etc. of the transmission. It directly affects the ring.

INDUSTRIAL APPLICABILITY The present invention makes it possible to use a synthetic resin material for the seal ring that prevents the leakage of servo oil in the servo drum support mechanism portion, improves the leakproofness, and improves the shift shock feeling in the automatic transmission. The purpose is to

[Means for solving problems]

To achieve the above object, the present invention rotatably supports a servo drum of an automatic transmission in a transmission case via a support, and supplies hydraulic oil from the support to the servo drum via a rotation support portion. In the servo drum rotation support device having an oil passage formed therein, a cast iron sleeve is fitted to the outer periphery of the rotation support portion of the support that supports the inner circumference of the servo drum, and leakage of hydraulic oil from the rotation support portion is prevented. A seal ring made of a synthetic resin for blocking both sides of the sleeve in the axial direction is fitted to both sides of the sleeve in the axial direction.

[Operation and effect of the invention]

According to the servo drum support device of the present invention having the above structure, by fitting a sleeve made of cast iron to the outer periphery of the rotation support portion regardless of the material of the support, such as polytetrafluoroethylene having a high sealing property A synthetic resin seal ring can be used. Therefore, it is possible to obtain an effect that the shift shock feeling of the automatic transmission can be improved by reliably preventing the leakage of the servo oil from the rotation support portion.

In addition, by separating the sleeve, it is possible to improve the workability of the seal ring groove, and when the thrust bearing is arranged on the end surface of the support, project the sleeve bearing side from the support portion in the axial direction. With the dimensions set, the inner peripheral surface of the sleeve can also be used as a thrust guide.

〔Example〕

 Next, an embodiment of the present invention will be described with reference to the drawings.

FIG. 2 is an overall sectional view of an automatic transmission for a vehicle to which the servo drum rotation supporting device of the present invention is applied.
Is composed of a fluid torque converter 200, a transmission 300, and a hydraulic control device 400.

The transmission 300 includes an overdrive transmission 300A including a first planetary gear unit U0, a multi-disc clutch C0 operated by a hydraulic servo, a multi-disc brake B0, and a one-way clutch F0, a second planetary gear unit U1, and a third planetary gear unit. Gear unit U2, two multi-plate clutches C1, C2 operated by hydraulic servos, belt booth B1, two multi-plate brakes B2, B3 and two one-way clutches F1, F2.
And an underdrive transmission 300B having three forward gears and one reverse gear.

The transmission case 110 of the automatic transmission 100 is a torque converter.
Torque converter housing 120 accommodating 200, overdrive transmission 300A and underdrive transmission 30
It includes a transmission case 130 integrally formed with each chamber for housing 0B and an extension housing 140 that covers the rear side of the automatic transmission 100, and these are fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 120 whose front side (engine side) is open, and is rotated by the drive of an engine (not shown).
1, an annular plate-shaped rear cover 202 welded to the inner periphery thereof, a pump impeller 203 provided on the inner peripheral wall of the rear cover 202,
A turbine shell 205 holding a turbine runner 204 arranged to face the pump impeller 203 is supported by a fixed shaft 207 connected to the transmission case 110 via a one-way clutch to provide torque capacity when the input speed is low. A stator 208 to be increased, a direct coupling clutch (lock-up clutch) 209 arranged between the front cover 201 and the turbine shell 205 and directly coupling them are provided.

The external gear 150a and the internal gear 1 are internally provided between the tubular transmission case 130 and the torque converter housing 120, which are continuous to the rear of the torque converter housing 120.
An internal gear oil pump 150 including 50b is accommodated, and an oil pump poddy 152 having a cylindrical portion 151 protruding forward on the inner periphery is fastened to the front portion of the transmission case 130, and an inner peripheral end portion of the rear cover 202. Connected extension member 210
Is spline-fitted to the inner circumference of the external gear 150a through the inner circumference of the tubular portion 151. Also, the oil pump body 152
On the rear side, an oil pump cover 1 having a tubular front support 153 coaxial with the tubular portion 151 and projecting rearward
The oil pump housing 152 and the oil pump cover 154 form a partition between the torque converter housing 120 and the transmission case 130 when the oil pump housing 152 and the oil pump cover 154 are tightened.

Further, in the middle of the transmission case 130, a center support 132 for separating the overdrive mechanism chamber 130A in which the overdrive transmission 300A is arranged and the underdrive mechanism chamber 130B in which the underdrive transmission 300B is arranged. It is provided. A rear support wall 134 having a cylindrical rear support 133 protruding forward is provided at a rear portion (right side in the drawing) of the transmission case 130.

Inside the front support 153, the torque converter 2
Fixed shaft of one-way clutch 206 supporting stator 208 of 00
An input shaft 10 of the transmission 300, which is the output shaft of the torque converter 200, is fitted inside the fixed shaft 207.
Is rotatably supported. The input shaft 10 has a flange portion 101 at the rear end, and a rearward facing hole 102 at the center of the rear end.
Are formed. An intermediate transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted behind the input shaft 10. The intermediate transmission shaft 11 has its tip inserted into the hole 102 of the input shaft 10, has a flange-shaped rotating body 8 at the rear end thereof, and has an output shaft for transmitting power to the drive wheel side at the center.
A rearward facing hole 112 into which the tip of 12 is inserted is formed. The output shaft 12 has a sensor rotor 121 for detecting the number of rotations and a speedometer drive gear 122 in the extension housing 140, and a sleeve yoke for transmitting power to the drive wheel side is fitted on the outer periphery at the rear end. Spline groove 123
And is rotatably supported by the extension housing 140 via the sleeve yoke, and the front end is rotatably supported in the hole 112 of the intermediate shaft 11.

The overdrive transmission 300A includes a first planetary gear unit U0 behind the input shaft 10 and has a ring gear R0.
Is coupled to the intermediate transmission shaft 11 via a flange plate 113,
The planetary carrier P0 is a flange portion 101 of the input shaft 10.
The sun gear S0 is formed by the inner race shaft 13 of the one-way clutch F0. On the front side of the first planetary gear unit U0, a first hydraulic servo drum 14 that opens rearward is fixedly provided on the inner race shaft 13, and between the outer peripheral wall 14A and the inner peripheral wall 14B of the first hydraulic servo drum 14. An annular piston 15 is fitted into the hydraulic piston to form a hydraulic servo C-0 of a clutch C0 that engages and disengages the carrier P0 with the first hydraulic servo drum 14, and the annular piston 15 is provided on the inner race shaft 13 side. A return spring 16 for pressing the clutch to the servo C-0 side, a clutch C0 is mounted inside the outer peripheral wall 14A, and the first hydraulic servo drum 14, the inner race shaft 13 and the carrier P0 are connected via the clutch C0. It is connected. A one-way clutch F0 having an inner race shaft 13 as an inner race is provided on the inner circumference of the first hydraulic servo drum 14, and a clutch C0 and a brake B0 are provided between the outer race 17 and the transmission case 130 on the outer circumference of the first race. The piston 18 for pressing the brake B0 is fitted in front of the center support 132 behind the B0, and the piston 18 and the center support 132
Between them, a hydraulic servo B-0 of the brake B0 is formed, and a return spring 19 that presses the piston 18 toward the hydraulic servo B-0 side is fitted in the front end inner peripheral portion 135 of the center support 132.

In the underdrive transmission 300B, first, a second hydraulic servo drum 20 having an opening at the rear is disposed in the outer periphery of the rotation support portion 3 of the center support 132 rotatably in the front thereof. An annular piston 21 that presses the clutch C2 is fitted into the servo drum 20, and a return spring 24 that presses the annular piston 21 toward the second hydraulic servo C-2 side is provided.
The hydraulic servo C of the clutch C2 is provided between the hydraulic servo drums 20.
-2 is formed, and the clutch C2 is mounted inside the outer peripheral wall 20A of the second hydraulic servo drum 20. Behind the second hydraulic servo drum 20, a third hydraulic servo drum 24, which is open rearward and has an annular projection 23 in the front, is fixed to the outer periphery of the flange-shaped rotating body 8 at the rear portion of the intermediate transmission shaft 11. The annular piston 25 that presses the clutch C1 is fitted between the rear end of the intermediate transmission shaft 11 and the outer peripheral wall 24A of the third hydraulic servo drum 24.
A hydraulic servo C-1 of the clutch C1 is formed between the second hydraulic servo drum 24 and the third hydraulic servo drum 24, and a return spring 26 for pressing the annular piston 25 to the hydraulic servo C-1 side is provided on the inner peripheral side of the clutch C1. Further, a clutch C2 is mounted on the outer periphery of the annular projection 23, and the second and third hydraulic servo drums 20 and 24 are connected via the clutch C2.
A second planetary gear unit U1 is provided behind the third hydraulic servo drum 24, and its ring gear R1 is a ring gear R1.
A rotation support member that rotatably supports 1 on the outer circumference of the output shaft 12.
27 is connected to the third hydraulic servo drum 24 via an annular protrusion 28 provided to project in front of 27 and a clutch C1, and the carrier P1 is spline-fitted to the front end portion of the output shaft 12 to form a sun gear. S1 is formed integrally with the tip of a sun gear shaft 29 that is rotatably fitted around the outer periphery of the output shaft 12. In addition, the second and third hydraulic servo drums 20 and 24 and the second
A connecting drum 30 molded so that the minimum space covers the planetary gear unit U1 is fixed to the outer periphery of the second hydraulic servo drum 20 at its front end, and its rear end is at the rear side of the second planetary gear unit U1 at the sun gear. This connecting drum is connected to the shaft 29.
Belt brake B for fixing and releasing the outer periphery of 30
1 is provided.

FIG. 3 is a front view of the center support 132. Inside the center support 132, a C-1 hydraulic oil supply oil passage 3A communicating with the hydraulic servo C-1 and supplying / discharging hydraulic oil of the clutch C1 is shown. And a C-2 hydraulic oil supply oil passage 3B that communicates with the hydraulic servo C-2 of the clutch C2 and supplies and discharges hydraulic oil.
A lubricating oil supply oil passage 3C for supplying lubricating oil from the outer circumference of the intermediate transmission shaft 11 to the inner circumference and a hydraulic servo B-0 of the brake B0, which communicates with the hydraulic servo B-0 to supply and discharge the hydraulic oil B-0 hydraulic oil supply oil passage 3D and are provided.

FIG. 1 is a side view showing a second hydraulic servo drum rotation support device, which shows a cylindrical portion 1 on the inner circumference of the second hydraulic servo drum 20 fitted on the outer circumference of the rotation support portion 3 of the center support 132. Is provided with a port 1A communicating with a C-2 hydraulic oil supply oil passage 3B provided in the center support 132. A sleeve 5 according to the present invention is interposed between the tubular portion 1 and the rotation support portion 3. The sleeve 5 is made of stainless steel, iron, or the like, and is press-fitted to the outer circumference of the rotation support portion 3. And on the outer periphery of the sleeve 5,
An oil groove 5A corresponding to the port 1A is formed, and a seal ring groove 4 on the front side and a seal ring groove 4A on the rear side are formed on both sides of the oil groove 5A. The rear portion of the sleeve 5 is reduced in diameter through the step 5B and is continuous with the journal portion 5C, and the rear end projects rearward of the rotation support portion 3. The protruding portion forms a thrust trace guide 9 that supports the thrust trace 6 of the bearing 7 arranged between the rotation support portion 3 and the rotating body 8 from the outer periphery. The oil groove 5A communicates with the C-2 hydraulic oil supply oil passage 3B via an oil passage (not shown), and the seal ring grooves 4 and 4A of the sleeve 5 are connected to the port 1A via the oil groove 5A. A front seal ring 2 and a rear seal ring 2A made of polytetrafluoroethylene are provided so as not to leak the supplied operating oil. The journal portion 5C is induction hardened, and a bush 1C to be described later is provided.
Prevents abrasion due to sliding contact. Center support 132
A ring-shaped metal bearing 20A is arranged between the rear surface and the second hydraulic servo drum 20, and the second hydraulic servo drum 20, the center support 132, and the metal bearing 20A.
A gap A is formed between the seal ring 2 and the seal ring 2, and the gap A and the lubricating oil supply oil passage 3C are communicated with each other by the seal ring lubrication hole 3E. Also, the tubular portion 1 and the journal portion 5
An oil groove 1 that communicates with the front and rear on the inner circumferential side between C and C
A tubular member (bush) 1C having B and smoothing the rotation of the tubular portion 1 is provided, and the inner circumference of the tubular portion 1 and the rotation support portion 3 are provided.
A space B is formed between the outer peripheral surface of the sleeve 5 and the rear surface of the step 5B and the front surface of the sleeve 5. The space B communicates with the lubricating oil supply oil passage 3C through a hole 5D provided in the sleeve 5 and a hole 3F provided in the rotation support portion 3.
In the lubricating oil supply oil passage 3C, since the lubricating oil constantly flows during the rotation of the input shaft, the lubricating oil is supplied to the clearance A through the seal ring lubrication hole 3E, and the working oil in the clearance A is fed to the front seal ring 2 To forcibly lubricate the seal ring 2.
In the space B, holes 3F and 5D are provided from the lubricating oil supply oil passage 3C.
Lubricating oil is supplied to the bush 1C via the rear seal ring 2A, the bush 1C, and the oil groove 1B on the inner circumference of the bush 1C.

Returning to FIG. 2, the spline 136 formed inside the transmission case 130 is spline-fitted with the brake plate b2 of the brake B2 on the front side and the brake plate b3 of the brake B3 on the rear side. Has a ring-shaped projection 31 that opens forward and
The fourth servo drum 32 having the above is spline-fitted. An annular piston 33 that presses the brake B2 is fitted between the outer peripheral wall 32A of the fourth servo drum 32 and the annular projection 31, and the hydraulic servo B of the brake B2 is inserted between the annular piston 33 and the fourth hydraulic servo drum 32. -2 is formed,
A return spring 34 for pressing the annular piston 33 toward the hydraulic servo B-2 side is provided on the inner peripheral wall 32B side. A one-way clutch F1 having a sun gear shaft 29 as an inner race shaft is provided inside the brake B2, and the brake B2 is attached to the outer periphery of the outer race 35. A plurality of pistons 37 that press the brake B3 are provided in an annular hole 36 formed between the rear support 133 outer peripheral side of the rear support wall 134 behind the brake B2 and the transmission case 130.
1,373 and the reaction sleeve 372 are fitted to form a hydraulic servo B-3 of the brake B3, and a return spring 38 for pressing the pistons 371,373 toward the hydraulic servo B-3 side is attached to the tip of the rear support 133. It is supported by a return spring fitting 38A.
The inner race 39 of the one-way clutch F2 arranged on the inner circumference of the brake B3 is connected to the fourth servo drum 32 on the outer circumference of the sun gear shaft 29, and the brake B3 is attached to the outer circumference of the outer race 40 of the one-way clutch F2. Has been done.

In the third planetary gear device U2, the sun gear S2 is integrally formed with the sun gear shaft 29, the carrier P2 is coupled to the outer race 40 of the front one-way clutch F2, and
A ring gear R2, which is connected to the brake B3 and has a parking gear 41 engraved on the outer circumference, is connected to the output shaft 12 via a connecting member 42 that is spline-fitted to the output shaft 12 on the inner circumference. When the shift lever of the automatic transmission is selected to the parking (P) position, the parking gear 41 has the parking claw 43.
Are provided so as to mesh with each other and fix the output shaft 12.

Transmission 300 of this embodiment configured as described above, by the hydraulic pressure selectively output to the hydraulic servo of each friction engagement device from the hydraulic control device 400 according to the vehicle traveling conditions such as vehicle speed and throttle opening, By engaging or disengaging the respective clutches and brakes, four forward gear shifts and one reverse gear shift are performed. The hydraulic control device 400
Is provided in a valve body 403 incorporated in an oil pan 402 that is fastened to the lower portion of the transmission case 130 by a bolt 401. Actuation of each clutch, brake, and one-way clutch, and the achieved shift speed (RANGE)
An example is shown in Table 1.

In Table 1, E indicates that the corresponding clutch and brake are engaged, and X indicates that they are released. L has a corresponding one-way clutch engaged in the engine drive state, but the engagement is not always required because the transmission of power is ensured by a clutch or a brake installed in parallel with the one-way clutch ( Lock). (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. Further, f indicates that the corresponding one-way clutch is free.

Although the present invention has been described in detail based on one embodiment, the present invention is not limited to the above-described embodiment, and various specific configurations of details can be obtained within the scope of the matters described in the claims. Needless to say, it can be implemented by changing it. For example, although the bush 1C is used as the tubular member in the above-described embodiment, a needle bearing, a metal bearing, or the like may be used instead. Further, in the above embodiment, the journal portion 5C of the sleeve is induction hardened to prevent the bush 1C from being seized and worn. However, the entire sleeve may be carburized and quenched.

[Brief description of drawings]

FIG. 1 is a side sectional view showing a servo drum rotation support device according to an embodiment of the present invention, FIG. 2 is an overall side sectional view of a vehicle automatic transmission to which it is applied, and FIG. 3 is a support thereof. FIG. 1 ... Cylindrical part, 2, 2A ... Seal ring, 3 ... Rotation support part, 4, 4A ... Seal ring groove, 5 ... Sleeve, 6 ... Thrust trace, 7 ... Bearing, 8 ...
Rotor, 9 …… Thrust trace guide, 20 …… Second hydraulic servo drum, 110 …… Transmission case, 132 …… Center support

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takehito Kano 10 Takane, Fujii-cho, Anjo-shi, Aichi Aisin Warner Co., Ltd. In-house (72) Inventor Kazuaki Watanabe 1 Toyota-cho, Toyota-shi, Aichi Toyota Automobile Co., Ltd. (56) Reference JP-A-57-43041 (JP, A)

Claims (1)

[Claims] 1. A servo drum of an automatic transmission is rotatably supported by a transmission case via a support, and an oil passage for supplying hydraulic oil from the support through a rotation support portion is formed in the servo drum. In the servo drum rotation support device, a cast iron sleeve is fitted on the outer periphery of a rotation support portion that supports the inner circumference of the servo drum of the support, and leakage of hydraulic oil from the rotation support portion occurs on both sides in the axial direction of the sleeve. A servo drum rotation supporting device for an automatic transmission, characterized in that sealing rings made of synthetic resin for blocking are fitted to both sides of the sleeve in the axial direction.