JPH02129442A - Clutch support structure of automatic transmission - Google Patents

Abstract

PURPOSE:To reduce the total length of a transmission by forming a bent stepped portion narrower than the width of a bearing member on a clutch drum and inserting a fixed member in the bent stepped portion. CONSTITUTION:In a reverse range, the second clutch C2 and the second brake B2 are engaged so that the rotation of an input shaft 8 is transmitted to sun gears S1, S2 through the second clutch C2. At this time, as a ring gear R2 is fixed by braking of the second brake B2, a carrier CR1 is reversed while a ring gear R1 is reversed and reversion of the carrier CR1 is taken out from an output gear 9. Thus, a fixed member 26 is fitted to a bent stepped portion 21 of a clutch drum 17, and the axial length drum 17 can be reduce correspondingly so as to shorten the total length of a transmission.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a clutch support structure for an automatic transmission that can be made compact.

[Conventional technology]

Generally, automatic transmissions are based on a 3-speed automatic transmission mechanism consisting of two single planetary gear units called the so-called Simpson system, and an overdrive mechanism or underdrive mechanism consisting of one planetary gear unit in the 3-speed automatic transmission mechanism. is attached to provide four forward speeds.

Incidentally, in recent years, as vehicles have become more F-F and higher horsepower, there has been a demand for automatic transmissions to be further downsized and to have an increased transmission torque capacity. However, the automatic transmission consists of a power transmission path that inputs input from one end of the transmission mechanism and outputs linearly to the other end, and because both gear units are separated, the structure is long in the axial direction. Therefore, there is a limit to the ability to respond to the above-mentioned miniaturization. In addition, since the output member is located at the tip of the transmission path, the clutches cannot be placed all together at the tip of the mechanism, which is easy to replace and change.
The automatic transmission mechanism and the automatic transmission mechanism must be manufactured separately. For this reason, it is difficult to standardize parts and assembly lines, and high-mix, low-volume production results in a significant increase in costs.

In order to solve the above problem, the present applicant has already constructed a single planetary gear unit and a dual J-replane planetary gear unit, the carrier and the sun gear of which are integrally configured, and the output member is placed approximately at the center of the automatic transmission mechanism. (Japanese Patent Laid-Open No. 145846/1983) has proposed an automatic transmission that can be arranged in a central area, have a reciprocating transmission path, and be compact in the axial direction.

This will be explained with reference to FIG.

A planetary gear unit 2.3, an input shaft 5 connected to appropriate rotating elements of the gear unit via clutches, respectively.
, an automatic transmission mechanism having an output member 9 connected to a predetermined rotating element CR, and a locking means for locking the rotating elements R1, S as appropriate.

The output member 9 is disposed approximately in the center of the automatic transmission mechanism so as to cover the input shaft 5.

Furthermore, when the automatic transmission mechanism is the 3-speed automatic transmission mechanism 101, a first
(Forward) clutch C6 is arranged (see the underlined half of the !-! line in the figure), and if the automatic transmission mechanism is a 4-speed automatic transmission horizontal 108, the first clutch C3 is located further axially outward. , a third clutch C0 that operates during overdrive is arranged (see the upper half of line 2-2 in the figure).

As shown in FIG. 6, the 3-speed automatic transmission mechanism 10t includes a single planetary gear unit 2 and a dual planetary gear unit 3, and the sun gears 31 and carrier CR of both units 2. is connected to. Further, the acid sun gear S1 is appropriately locked by the first brake B1, and the ring gear R8 of the dual planetary gear unit 3 is appropriately locked by the second brake Bz and one-way clutch FI. Further, the input shaft 5 is connected to the ring gear R of the single planetary gear unit 2 via the first clutch C1, and to the sun gear S via the second clutch C2.
1, and the carrier CR, is connected to the output member 9.

On the other hand, as shown in FIG. 7, the 4-speed automatic transmission mechanism 10g includes, in addition to the 3-speed automatic transmission mechanism IQ+, a third clutch C0 disposed further axially outside the first clutch C9. Therefore, the clutch C0 can appropriately connect and separate the input shaft 5 and the ring gear R2 of the dual planetary gear unit 3.

The above configuration also has a 3-speed automatic transmission.

As shown in the operation table shown in FIG.
The 4-speed automatic transmission mechanism 10g is operated by clutches C11Ct, Co and locking means B+, Bz, F, as shown in the operation table shown in FIG.
The gears are shifted to four forward speeds and one reverse speed by appropriate operation of the output member 9 and the additional transmission section 20 . Or transmitted at 20°.

[Problem to be solved by the invention]

FIG. 9 shows the detailed structure of the automatic transmission mechanism.

The second clutch C2 is interposed between a sun gear input flange 53a fitted to the hollow shaft 53 and a flange portion 5a rising from the human power shaft 5, and also provides a sun gear input to the clutch Ct. A clutch drum 53b is disposed on the axially opposite side of the flange 53a.

Further, a piston 54 is fitted into the clutch drum 53b, and a spring 55 is interposed between the back surface of the piston 54 and a stop ring, and these constitute a hydraulic actuator for the second clutch C2. are doing. Further, a brake drum 53c is fixed to the outer periphery of the clutch drum 53b, and a first brake B consisting of a band brake can be moved into and out of contact with the drum 53c.

In the hydraulic actuator for the second clutch C2, the clutch drum 53b is rotatably supported by a boss portion 47a of a fixed wall via a bearing 80, and an oil passage 81 formed in the boss portion 47a of the fixed wall and 82, oil is supplied and discharged between the clutch drum 53b and the piston 540. For this purpose, the clutch drum 5
Seal rings 83 are provided on both sides of the oil passage 82 to seal between the oil passage 3b and the boss portion 47a of the fixed wall.

However, in the above conventional structure, the clutch drum 5
Since the bearing 80 and the two seal rings 83 are disposed coaxially on the bearing portion of the clutch drum 53b, the axial length of the clutch drum 53b becomes longer, resulting in a problem that the overall length of the transmission becomes longer. Furthermore, if the length of the bearing is shortened in order to shorten the length of the clutch drum 53b in the axial direction, there is a problem that the centering of the clutch becomes poor, wear of the bearing occurs, and the durability decreases.

The present invention is intended to solve the above problem, and aims to shorten the axial length of the clutch while ensuring a predetermined length of the bearing portion, thereby shortening the overall length of the transmission.

[Means for solving problems]

For this purpose, the automatic transmission clutch support structure of the present invention has the following features:
An input shaft (8) that connects a plurality of rotating elements of a planetary gear unit (10) via clutches (C, , C, , Co), and an output member that connects to at least one rotating element (CRI) of the gear unit. (9) and locking means (B) for locking a predetermined rotating element of the gear unit;
, , Bz, F+), one of the clutches (C3) is connected to the fixed member (23, 25, 26
) has a clutch drum (17) rotatably supported via a bearing member (22), and the clutch drum (17
) through an oil passage (29) formed in a fixed member (23, 25, 26), and oil is supplied and discharged through an oil passage (29) formed in a fixed member (23, 25, 26), and between the fixed member and the clutch drum, oil is supplied to and discharged from both sides of the oil passage (29). a seal ring (27) is formed on the clutch drum (17), a bent step (21) narrower than the width of the bearing member (22) is formed, and the fixing member is inserted into the bent step. Note that the numbers added to the above configurations are for comparison with the drawings, and the configurations are not limited thereby.

[Action and effect of the invention]

The clutch according to the present invention achieves a reverse state, for example, and in the reverse range, the second clutch C2 and the second brake B are engaged, and the input shaft 8 is rotated through the second clutch C2. Sun gear S, , S,
At this time, since ring gear R8 is fixed by braking of second brake B2, ring gear R,
While the carrier CR+ is being reversed, the carrier CR+ is also reversed, and the reverse rotation of the carrier CR1 is taken out from the output gear 9.

Therefore, according to the present invention, since the fixing member 26 is fitted into the bent step portion 21 of the clutch drum 17, the axial length of the clutch drum 17 is shortened by that amount, and the overall length of the transmission can be shortened. Can be done. Moreover, the length of the bearing portion of the clutch drum 170 can also be ensured.

[Example] Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 2, the automatic transmission to which the present invention is applied includes a torque converter section A, a four-speed automatic transmission mechanism section B, an output gear mechanism section C, and a differential gear mechanism section. Each of these mechanical parts is housed in a transmission case 2.3.4 which is integrally constructed by joining each other, and the pulp body 1 is disposed in the upper part of the case 3. The torque converter section A consists of a torque converter 5 and a centrifugal lock-up clutch 6, and the rotation of the engine is controlled by the rotation of the engine within the automatic transmission mechanism section B through an oil flow within the torque converter 5 or a mechanical connection by the lock-up clutch 6. The signal is transmitted to the input shaft 8. Further, an oil pump 7 is installed between the torque converter section A and the automatic transmission mechanism section B.

A hollow shaft 11 rotatably supported by the input shaft 8 is fitted into the 4-speed automatic transmission mechanism section B.
The second clutch Ct is arranged on the outer periphery of the engine in order from the engine output side.
A first brake B1, an output gear 9, a one-way clutch FI, a planetary gear unit 10, a second brake Bu, a first clutch C1, and an overdrive clutch C0 are arranged.

Further, the output gear mechanism section C has a counter shaft 83 rotatably supported by a bearing 8182 between the transmission cases 3 and 4.
On top of 3 is a counter driven gear 85 that meshes with the output gear 9.
and a differential drive gear 86 are fixed. In addition, the differential gear mechanism part includes a differential gear unit 87 and a ring gear mount case 8.
9, the mount case 89 has a ring gear 90 that meshes with the differential drive gear 86,
Differential pinion 9 of differential gear unit 87
1 and constitutes a differential carrier. The differential gear unit 87 has left and right side gears 92.93 that mesh with the differential pinion 91, and power is transmitted from these side gears 92.93 to the left and right wheels.

Next, details of the 4-speed automatic transmission mechanism B will be explained with reference to FIGS. 1 and 3.

The planetary gear unit 10 includes a single planetary gear unit 12 and a dual planetary gear unit 13.
The single planetary gear unit 1-12 consists of
Sun gear S1% ring gear R formed on hollow shaft 11
1 and a first pinion P that meshes with these gears.The dual planetary gear unit 13 also has a second pinion P2 and a third pinion P, and the second pinion P8 is sun gear S3
and a third pinion P, the third pinion P
consists of a carrier CR that meshes with the second pinion P and the ring gear R2, and supports these gears so that they mesh with each other. And these two gear units 12
．． 13, the sun gears S1 and S2 are integrally formed with the hollow shaft 11, and the carrier CR is also integrally formed.

Next, the clutch support structure, which is a feature of the present invention, will be explained.

The second clutch C□ is interposed between a sun gear input flange 15 spline-coupled to the hollow shaft 11 and a flange portion 16 rising from the input shaft 8. Input flange 1
A clutch drum 17 is disposed on the opposite side of the clutch drum 5 in the axial direction. Furthermore, the clutch drum 17 includes a piston 19.
is inserted therein, and a spring 20 is interposed between the back surface of the piston 19 and the retaining ring, and these constitute a hydraulic actuator for the second clutch C8.

A bent step portion 2 is provided on the manpower shaft 8 side of the clutch drum 17.
1 is formed, and the bent step portion 21 is rotatably disposed on a fixed shaft 23 via a bearing or bush 22 that is a bearing member.

The width of the bent step portion 21 is narrower than the width of the bearing member. Also, the fixed wall 2 coupled to the fixed shaft 23
A fixing ring 26 is fixed to the clutch drum 5, and the fixing ring 26 fits into and supports the bent step 21 of the clutch drum 17.

Further, seal rings 27 for sealing between the clutch drum 17 and the fixed ring 26 are provided on both sides of the oil passage 29. Oil is supplied and discharged between the clutch drum 17 and the piston 19 from an oil passage (not shown) formed in the fixed wall 25 via an oil passage 29.

Therefore, in the clutch support structure described above, since the fixing member 26 is fitted into the bent step portion 21 of the clutch drum 17, the axial length of the clutch drum 17 is shortened by that amount, and the overall length of the transmission is shortened. be able to. Further, the length of the bearing portion of the clutch drum 17 can also be ensured.

Furthermore, the structure of each part will be explained.

A brake drum 30 is fixed to the outer periphery of the clutch drum 17, and a first brake B consisting of a band brake can be moved into and out of contact with the drum 30.

Further, an output gear 9 is disposed approximately in the center of the automatic transmission mechanism section B, and the output gear 9 is provided with a boss section 9a. The inner periphery of the boss portion 9a is spline-coupled to the carrier CR, and the outer periphery of the boss portion 9a is rotatably and axially movable via a bearing 31 on a partition wall 3a integrally formed with the transmission case 3. It is supported irrevocably. The bearing 31 is a double tapered roller bearing having an outer race 32 spline-coupled to the partition wall 3a and two inner races 35 with a spacer 33 interposed therebetween.

Furthermore, the outer race 32 extends in the axial direction, and the inner race 36 of the first one-way clutch F is fixed to the extended portion, and movement in the axial direction is prevented by a locking ring 37. Further, an outer race 39 of a one-way clutch F is disposed so as to be connected to the ring gear R2 of the dual planetary gear unit 13 and extend in the axial direction, and a first one-way clutch F1 is interposed between these two races. Therefore, the one-way clutch F1 is arranged in the axial direction between the dual planetary gear unit 13 and the partition wall 3a, and is arranged substantially inside the ring gear R of the unit 13. Further, a support member 41 is engaged with a gear on the inner circumference of the ring gear R8, and two thrust bearings 42 are arranged on both sides of the tip of the support member 41. It receives the generated thrust force.

Furthermore, a seal ring 43 is provided between the support member 41 and the outer race 39 of the one-way clutch F.

Further, a second disc brake B8 is interposed between the outer periphery of the ring gear R2 and the case 3, and a cylinder is formed on one side wall surface of the partition wall 3a, and the cylinder includes a piston 44. A hydraulic actuator is arranged to be sandwiched between the one-way clutch F1 and the one-way clutch F1. Further, the piston 44 has a cylindrical comb-shaped arm, which extends in the axial direction passing through the outer circumferential side of the one-way clutch F1, and controls the second brake B2. (A return spring 45 is disposed in the toothed portion.

Furthermore, the first (forward) clutch C1 is interposed between a clutch drum 46 spline-coupled to the input shaft 8 and the outer periphery of the ring gear R of the single planetary gear unit 12, and a piston is disposed in the drum 46. 47 and a spring 49 are provided to constitute a hydraulic actuator for the clutch C1.

Further, a third clutch C0 is arranged in line with the first clutch C1 on the outside in the radial direction, and a clutch drum 50 is rotatably supported on a boss portion 2b formed in the housing 2. , a third clutch C0 is interposed between the drum 50 and the clutch drum 46 spline-coupled to the input shaft 8. A piston 51 and a spring 52 are disposed inside the clutch drum 50 to constitute a hydraulic actuator for the third clutch C0, and the tip of the drum 50 and the ring gear R of the dual planetary gear unit 13 are connected to each other. , are connected by a connecting member 53.

Next, the operation of the four-speed automatic transmission mechanism section B having the above structure will be explained with reference to the gear train shown in FIG. 3 and the operation table shown in FIG. 4.

Engine torque is transmitted to an input shaft 8 via a torque converter 5 and a lock-up clutch 6. and,
In the 4-speed automatic transmission mechanism section B, each clutch C1, C! according to the operation table shown in FIG. , C0, brakes B+, Bz, and one-way clutch F1, four forward speeds and one reverse speed are obtained, and the changed rotations are output from the output gear 9 to the output gear mechanism section C.

In the l-speed state, the first clutch C1 is engaged.

Then, the rotation of the input shaft 8 is transmitted to the ring gear R of the single planetary gear unit 12 via the first clutch C1.
At this time, since the ring gear R of the dual planetary gear unit 13 is prevented from rotating by the one-way clutch F, the common carrier CR is significantly decelerated in the forward direction while rotating the sun gears Sl and Sz in the opposite direction. The rotation is extracted from the output gear 9.

In the second speed state, in addition to the engagement of the first clutch C5, the first brake B1 is operated, and the sun gears S1 and S2 are
The rotation is stopped by the brake B of the input shaft 8.
The rotation of ring gear R1 from 7 decelerates and rotates carrier CR in the positive direction while rotating ring gear R2 in the positive direction, and this rotation is taken out from output gear 9 as second speed.

In the third speed state, in addition to the engagement of the first clutch C1, the third
clutch C0 is engaged, and the rotation of the human power shaft 8 is transmitted to the ring gear R1 of the single planetary gear unit 12 via the clutch CI.
7, each element of the planetary gear unit 10 rotates as one, and therefore, the carrier CR also rotates as one, so that rotation at the same speed as the input shaft 8 is extracted from the output gear 9.

Furthermore, in the 4th speed state, when the first clutch C1 is released and the first brake B is activated, the rotation of the input shaft l is transmitted to the ring gear R8 of the dual planetary gear unit 13 via the clutch C0. At this time, since sun gears S+ and Sz are stopped, carrier CR rotates at high speed while rotating ring gear R1 of single planetary gear unit 12 at an increased speed, and the high speed rotation is taken out from output gear 9 as overdrive.

In the reverse range, the second clutch Ct and the second brake lower are engaged, and the rotation of the input shaft 8 is transmitted to the sun gears S, St, through the second clutch C8, and at this time, the ring gear R1 is in the second Since the carrier CR is fixed by the braking of the brake B2, the carrier CR is rotated while the ring gear R3 is reversed.

The reverse rotation of the carrier CR, is also taken out from the output gear 9.

Furthermore, in the first speed state during coasting, the one-way clutch F is in a free state, but the first clutch CI
In addition to this, the second brake B□ is engaged, and the brake Bt fixes the ring gear R2, maintaining the first speed state and effectively operating the engine brake.

In the above embodiment, a 4-speed automatic transmission has been described as an example, but it goes without saying that the invention may also be applied to a 3-speed automatic transmission. Further, in the above embodiment, the second clutch C2 is explained as an example, but any clutch may be used as long as the clutch has a clutch drum rotatably supported by a fixed member via a bearing member.

[Brief explanation of drawings]

FIG. 1 is a partial sectional view of FIG. 2 showing one embodiment of the automatic transmission of the present invention, FIG. 2 is an overall sectional view of one embodiment of the automatic transmission of the present invention, and FIG. 1 is a schematic diagram of the automatic transmission mechanism section, FIG. 4 is a diagram for explaining the operation of the automatic transmission, FIG. 5 is an overall sectional view of a conventional automatic transmission, and FIGS. 6 and 7 are 5 is a schematic diagram of the automatic transmission mechanism section, FIG. 8 is a diagram for explaining the operation of the automatic transmission mechanism shown in FIG. 6, and FIG. 9 is a partial sectional view of FIG. 5. C+, Ct, Co...clutch, B+, B□, F
l...Locking member, RI, Rt...Ring gear, Sl
, S A... Sun gear, CR,... Carrier, P,
, P□, P3...pinion, 8...input shaft, 9...
・Output gear, 10... Planetary gear unit, 17
...Clutch drum, 21...Bending step, 22...
・Bearing member, 23.25.26...Fixing member, 27.
... Seal ring, 29... Oil passage. Applicant: Aisin AW Co., Ltd. Representative Patent Attorney: Hiroki Shirai (5 others) Procedural Amendment Form Cap Button January 10, 1999 2. Title of Invention: Clutch Support Device for Automatic Transmission 3, Amendment Relationship with the case of a person who does Increased number of claims None 7, column of 0 title of invention in specification subject to amendment, column of claims and content of amendment 1, title of invention is amended to "clutch support device for automatic transmission" 2. The claims are amended as follows. (1) An input shaft that connects a plurality of rotational elements of a planetary gear unit via clutches, an output member that connects to at least one rotational element of the gear unit, and a predetermined rotational element of the gear unit are locked. In an automatic transmission equipped with a locking means, one of the clutches has a clutch drum rotatably supported by a fixed member via a bearing member, and an oil passage formed in the fixed member is provided in the clutch drum. supplying and discharging oil, seal rings are provided on both sides of the oil passage between the fixed member and the clutch drum, and the clutch drum has a bent stepped portion narrower than the width of the bearing member. Clutch support for an automatic transmission in which the fixing member is inserted into the bent stepped portion.3. Correct "structure" to -town. 1゜Procedural amendment (formality) Case description Patent Application No. 283381 of 1986 3゜Relationship with the case of the person making the amendment Patent applicant Address 110 Fujiimachi Taka, Anjo City, Aichi Prefecture Name Aisin AW Co., Ltd. Representative: Shuzo Moroto 4, Agent address: 1-18-11 Ueno, Taito-ku, Tokyo (Shipping date: March 7, 1999) As per the details of the 8° amendment

Claims (1)

[Claims] (1) An input shaft that connects a plurality of rotational elements of a planetary gear unit via a clutch, an output member that connects to at least one rotational element of the gear unit, and a locking means that locks a predetermined rotational element of the gear unit. In the automatic transmission, one of the clutches has a clutch drum rotatably supported by a fixed member via a bearing member, and oil is supplied into the clutch drum through an oil path formed in the fixed member. , and has seal rings on both sides of the oil passage between the fixed member and the clutch drum, and the clutch drum has a bent step narrower than the width of the bearing member, and the clutch drum has a bent step narrower than the width of the bearing member. A clutch support structure for an automatic transmission, in which the fixing member is inserted into a bent step.