JPH0794855B2 - Clutch device for automatic transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to an automatic transmission, and more particularly to an automatic transmission for a vehicle used with a torque converter, and more particularly to a structure of a clutch device in the automatic transmission.

(B) Conventional technology Generally, an automatic transmission is provided with two single planetary gear units, the sun gears of both planetary units are common, and the carrier of the first planetary gear unit and the ring gear of the second planetary gear unit are integrally connected. It is configured by the so-called Simpson method,
By selectively inputting to the ring gear and / or sun gear of the first planetary gear unit with a clutch, and locking a predetermined rotating element of the planetary gear unit with a brake or a one-way clutch, and further integrally connecting to a carrier of the first planetary gear unit. Output from the ring gear of the second planetary gear unit that is in operation to obtain the third forward speed.

The speed change mechanism has a first (Forward) clutch that connects the input member to the ring gear of the first planetary gear unit and a second (direct) clutch that connects to the sun gear. These clutches are arranged in the axial direction. They are installed and controlled by individual hydraulic actuators and return springs.

Further, conventionally, the 4-speed automatic transmission is based on the 3-speed automatic transmission mechanism including the two planetary gear units described above.
An overdrive (O / D) mechanism or an underdrive (U / D) mechanism consisting of one planetary gear unit is attached to the third speed automatic transmission mechanism to obtain a forward four speed shift stage.

(C) Problems to be Solved by the Invention By the way, there is a recent demand for further downsizing of an automatic transmission due to, for example, the use of vehicles such as F / F (front engine / front drive). In the configuration of the clutch device which is arranged in the axial direction and has individual operating means,
Since it becomes long in the axial direction, it cannot cope with the further miniaturization.

On the other hand, Japanese Patent Laid-Open No. 59-183147 proposes an automatic transmission mechanism in which two clutches are added to a conventional so-called Simpson type planetary gear unit to obtain a fourth speed. That is, in the automatic transmission mechanism, the third clutch is interposed between the sun gear of the first planetary gear unit and the sun gear of the second planetary gear unit, which are integrally connected in the conventional Simpson system, and the sun gear of the first gear unit is interposed. And the carrier of the second gear unit to the fourth
And the third clutch is disengaged to disconnect the first gear unit and the second gear unit, and the third clutch is connected to apply an input to the carrier of the second gear unit. By fixing the sun gear of the second gear unit and outputting the overdrive from the ring gear, the fourth speed is obtained in addition to the conventional third speed.

By the way, the improved four-speed automatic transmission mechanism described above also has the clutches arranged in the axial direction and has individual operating means, similarly to the Simpson type three-speed automatic transmission mechanism, and is for further separating the two gear units. Along with the fact that many clutches are required, the structure is long in the axial direction, and it is not possible to cope with the further miniaturization.

Also, a plurality of clutches that transmit from the input member to different rotating elements of the planetary gear unit respectively need to secure a clutch capacity corresponding to the torque capacity of the rotating elements that transmit, but these multiple clutches are arranged together. When trying to reduce the axial dimension by
In order to secure the torque capacity of each clutch, the size becomes large in the radial direction. Especially, in the case of an engine horizontal type vehicle, because the vehicle frame is arranged in the bonnet, it is on the opposite side of the torque converter. That is, the rear end portion of the automatic transmission mechanism interferes with the vehicle frame and impairs vehicle mounting performance.

Therefore, according to the present invention, the first and second clutches can be arranged compactly together at the rear end of the automatic transmission, and the vehicle mounting performance of the automatic transmission can be ensured. However, it is an object of the present invention to provide a clutch device for an automatic transmission having appropriate clutch capacities corresponding to torque capacities of different rotating elements engaged with each other.

(D) Means for Solving the Problems The present invention has been made in view of the above circumstances, and includes an input member (5) connected to an output portion of a torque converter (16) and a planetary gear unit (2, 3). ), A first clutch (C ₁ ) connecting the input member (5) and the first rotating element (R ₁ ) of the planetary gear unit,
A second clutch (C ₂ ) connecting the input member (5) and the second rotating element (S) of the planetary gear unit;
An output member (9) connected to the third rotating element (CR) of the planetary gear unit and a locking means (B, R,) for appropriately locking the predetermined rotating element (S, R ₂ ) of the planetary gear unit.
F) and an automatic transmission having an automatic transmission mechanism (10 ₁ ), which has an inner diameter side boss (at the rear end portion of the planetary gear unit opposite to the torque converter). 5b) is connected to the input member (5), and the rear end side is a small diameter side step (54c) and the planetary gear unit side is a large diameter side step (54d). ) Is arranged, the first clutch (C ₁ ) is arranged on the inner peripheral surface of the large diameter side step portion (54d) of the flange portion, and the inner peripheral side of the small diameter side step portion (54c) of the flange portion. A cylinder of the first clutch, which is formed so as to prevent relative rotation in the cylinder of the first clutch, and whose inner diameter side is supported by the boss portion (5b) of the flange portion so as to be movable in the axial direction. A one-clutch piston (62), A first oil chamber (65) constituted by a cylinder of the first clutch, a piston of the first clutch, and a boss portion of the flange portion, and hydraulic oil is supplied to the first oil chamber. Based on the movement of the piston (62) of the first clutch, the large-diameter side step (54d) of the flange and the first rotary element (R ₁ ) of the planetary gear unit are connected, and the second clutch (C ₂ ) is a cylinder of a second clutch which is disposed on the inner peripheral surface of the piston (62) of the first clutch and is formed on the inner peripheral side of the piston (62) of the first clutch, and the second clutch cylinder. A piston (63) of the second clutch, which is disposed in the cylinder of the clutch and whose inner diameter side is supported by the boss portion (5b) of the flange portion so as to be movable in the axial direction;
A second oil chamber (67) including a cylinder of the second clutch, a piston of the second clutch, and a boss portion of the flange portion, and hydraulic oil is supplied to the second oil chamber. A clutch device in an automatic transmission characterized in that the flange portion and the second rotating element (S) of the planetary gear unit are connected by the movement of the piston (63) of the second clutch based on .

Further, preferably, a return spring (70) for urging both the piston (62) of the first clutch and the piston (63) of the second clutch toward the release side is provided.

Further, the planetary gear unit has a single planetary gear (2) and a dual planetary gear (3), and carriers (CR) and sun gears (S) of both planetary gears are integrally connected to each other, and the input member (5) The first rotating element connected to the first planetary gear unit via the first clutch (C ₁ ) is the ring gear (R ₁ ) of the single planetary gear unit, and the second rotating element connected via the second clutch (C ₂ ). The second rotating element is the sun gear (S), the third rotating element connected to the output member (9) is the carrier (CR), and the locking means (B, F) is used. It is preferable that the predetermined rotating elements that are appropriately locked are the sun gear (S) and the ring gear (R ₂ ) of the dual planetary gear.

(E) Action Based on the above configuration, the rear end side becomes the small diameter side step (54c) and the planetary gear unit side becomes the large diameter side step (54c).
The flange portion (54) to be d) is arranged at the rear end of the automatic transmission mechanism (10 ₁ ), and the first and second clutches (C ₁ , C ₂ ) are provided in the flange portion (54). Hydraulic actuator (66,6
9) is arranged together to reduce the radial dimension of the rear end portion of the automatic transmission mechanism and shorten the axial direction.

Further, since the first clutch (C ₁ ) is arranged on the large diameter side step portion (54d) of the flange portion (54), the small diameter side step portion (54
Although the hydraulic actuator (66) is arranged using c) as a cylinder, a clutch capacity corresponding to the torque capacity of the _first rotating element (R ₁ ) can be secured.

Further, the second clutch (C ₂ ) has its inner diameter side fitted to the boss portion (5b) of the flange portion to form a hydraulic actuator using the piston (62) of the first clutch as a cylinder. The piston (63) of the second clutch can be arranged without significantly reducing the pressure receiving area of the second oil chamber (67), and the clutch capacity corresponding to the torque capacity of the second rotating element (S) can be secured. it can.

The reference numerals in the parentheses are for the purpose of contrasting with the drawings, but do not limit the configuration of the present invention in any way.

Next, the automatic transmission mechanism will be specifically described below. Three
Speed automatic transmission mechanism 10 ₁ operates as a working table shown in Figure 3. That is, in the 1st speed state in the D range, the first (forward) clutch C ₁ is connected. Then, the rotation of the input member (shaft) 5 is transmitted to the ring gear R ₁ of the single unit 2 via the clutch C ₁ , and in this state, the ring gear R ₂ of the dual unit 3 is rotated by the second one-way clutch F _2. Since the sun gear S is idled in the reverse direction, the common carrier CR is significantly decelerated and rotated in the forward direction, and the rotation is extracted from the output member (gear) 9. Further, in the second speed state, the second (second) brake B ₂ is operated in addition to the connection of the first clutch C ₁ . Then,
The rotation of the sun gear S is stopped by the operation of the first one-way clutch F ₁ based on the brake B ₂ , so that the rotation of the ring R ₁ from the input member 5 causes the ring gear R ₂ of the dual unit 3 to idle while rotating in the positive direction. The CR is decelerated and rotated in the positive direction, and the rotation is taken out to the output member 9 as the second speed. In the third speed state, the first (forward) clutch
In addition to the C ₁ connection, the second (direct) clutch C ₂ is connected. Then, the rotation of the input member 5 is transmitted to the sun gear S together with the ring gear R ₁ , the planetary gear unit 2 rotates integrally, and the carrier CR also rotates integrally, and the output member 9 rotates at the same speed as the input member 5. It Note in this case, the second brake B ₂ before connection of the direct clutch C ₂ is dissociated, since reverts back to the first speed state or the second brake B ₂ dissociates after clutch C ₂ is connected, or engage Leave it alone. Further, in the reverse (R) range, the second clutch C ₂ and the third (1st reverse) brake B ₃ are activated. Then, the rotation of the input member 5 is transmitted to the sun gear S via the clutch C ₂ , and in this state, the ring gear R ₂ of the dual unit 3 is fixed by the operation of the third brake B ₃ , so that the single unit 2 The carrier CR is also reversely rotated while the ring gear R ₁ is reversely rotated, and the reverse rotation of the carrier is taken out to the output member 9. In addition, in the 1st range, in addition to the 1st speed state in the D range, the third brake B ₃
Works. Therefore, engine braking (input / output reverse rotation)
At this time, in the D range, the transmission is disengaged by the one-way clutch F ₂ and the idling state occurs, but in the 1 range, the ring gear R ₂ is fixed by the brake B ₃ and is kept in the 1st speed state. Further, the first speed in the second range is the same as the first speed in the D range, and in the second speed, the first (2nd coast) brake B ₁ operates in addition to the second speed state in the D range. Then, when the engine is braked, the one-way clutch F ₁ causes the idling state in the D range, but in the 2 range, the sun gear S is fixed by the brake B ₁ and is maintained in the second speed state.

Then, when the first clutch C _{1 is} maintained, that is, when the vehicle is traveling forward, pressure oil is supplied to the oil chamber 65 of the hydraulic actuator 66 via the oil passage. Then, the piston 62 of the hydraulic actuator 66 is
in contact with the first clutch C ₁ after the movable member 62 constituting the a is moved slight distance d _1, to connect the clutch C _1. In this state, the rotation of the flange portion 54 integrated with the input member 5 is transmitted from the connecting spline portion 54d to the ring gear R ₁ via the first clutch C ₁ . Further, at the time of the 3rd speed shift, the second clutch C ₂ is connected in addition to the first clutch C ₁ , but at this time, the oil pressure is also supplied to the oil chamber 67 of the hydraulic actuator 69 via the oil passage. Then, the movable member 62 as the cylinder 62b,
After the piston member 63 has moved a predetermined distance, the second clutch C ₂
Contact with the connecting the clutch C _2. In this state, the rotation of the flange portion 54 integrated with the input member 5 is connected to the movable member 62 via the connecting spline portion 54d, and further transmitted from the connecting spline portion 62d of the movable member 62 to the second clutch C _2. , And is transmitted to the sun gear S of the hollow shaft 53 via the connecting member 53b. When the vehicle is moving backward, only the second clutch C ₂ is engaged, but in this case, the oil chamber of the hydraulic actuator 69 is closed.
Only 67 is supplied with hydraulic pressure. Then, the piston member 63 moves by the distance d ₂ and then contacts the second clutch C ₂ to connect only the clutch C ₂ .

(F) Examples Hereinafter, examples in which the present invention is embodied will be described.

The automatic transmission 1 ₂ equipped with the 3-speed automatic transmission mechanism 10 ₁
As shown, the torque converter 31,3 speed automatic transmission mechanism 10 _1, additional shifting portion 20 ₂ and the differential portion 35
And these parts are housed in a transaxle housing 36, a transaxle case 37, and a transaxle cover 39 that are integrally joined to each other. Then, the converter unit 31 is the torque converter 16
And a lockup clutch 17 (see FIG. 2),
From the shaft 15 connected to the engine crankshaft, the oil flow in the torque converter 16 or the lockup clutch 17
Is transmitted to the input shaft 5 in the automatic transmission mechanism 10 _i through the connection. Incidentally, the oil pump 47 is provided between the portion of the valve body 46 is disposed, also the automatic transmission mechanism 10 ₁ and the torque converter 31 to the upper portion of the transaxle case 37.

3-speed automatic transmission mechanism 10 ₁ includes a brake portion 49 toward the rear end in the axial direction from the engine output unit, the output unit 50, planetary and Li gear unit portion 51 and the clutch unit 6 are arranged in order, more input shaft 5 A hollow shaft 53 is rotatably supported by being fitted in the. Then, the planetary gear unit section 51
Is composed of a single gear unit 2 and a dual gear unit 3, and the single unit 2 is composed of a sun gear S ₁ formed on a hollow shaft 53, a ring gear R ₁ , and a carrier CR ₁ supporting a pinion P ₁ meshing with these gears, the dual unit 3 sun gear S ₂ formed on the hollow shaft 53, the ring gear R _2, and the first pinion P ₂ meshing with the sun gear S ₂
And a carrier CR ₂ that supports the pinion P ₂ that meshes with the ring gear R _{2 so as} to mesh with each other. The two units 2 and 3 are both sun gears S ₁ and S ₂ which are gears of the same number of teeth formed on the hollow shaft 53 (hereinafter simply referred to as S), and the carriers CR ₁ and CR ₂ are three. It is constructed integrally with the side plate (hereinafter simply referred to as CR). In addition, this embodiment is a pinion
Although P ₁ and P ₂ are configured separately, as shown in FIG. 2, they may be configured as an integral long pinion P, and both sun gears S ₁ and S ₂ may be configured in common. . Also, the brake part 49
Includes a first one-way clutch F ₁ , a second brake B ₂ and a first brake B ₁ arranged in this order from the inner diameter side to the outer diameter direction. Further, an oil pump 47 is provided at a position adjacent to each brake. Hydraulic actuators 55,5 formed on the case
6 are arranged side by side in the radial direction. The first brake B ₁ is interposed between the flange 53a at the end of the hollow shaft 53 and the pump case 37a integrated with the axle case 37, and the second brake B ₂ is the outer race of the first one-way clutch F ₁ . interposed between the pump casing 37a, and the first one-way clutch F ₁ is interposed between the hollow shaft 53 and the second brake B ₂ and. The output unit 50 includes an output member 9 which is located substantially center portion of the transmission mechanism 10 _1. The output member 9 is rotatably and axially immovably supported by a partition wall 37b integrally formed with the axle case 37 via a bearing 57, and the bearing 57 is a partition wall. Two inner races with an outer race splined to 37b and a spacer ring
It consists of a double tapered roller bearing with 57.
Further, the outer race has a step portion and extends in the axial direction, and the extended portion is also used as the inner race of the second one-way clutch F ₂ . Further, a connecting member 59 which is spline-connected to the ring gear R ₂ of the dual unit 3 and extends in the axial direction to serve as an outer race of the one-way clutch is arranged, and the second one-way clutch F ₂ is interposed between these races. ing. Therefore, the one-way clutch
F ₂ is axially arranged between the planetary gear unit 3 and the case partition wall 37b, and the ring gear R _{2 of the} unit 3 is arranged.
It is placed almost inward. Further, the ring gear R and the third brake B ₃ interposed between the _second outer peripheral and axle case 37, and the partition wall 37b one side wall surface portion and the second one-way clutch F
_The hydraulic actuator 60 is arranged so as to be sandwiched between the _two . Further, the hydraulic actuator 60 has an arm comprising a cylindrical comb shape, the arms extend axially through the outer diameter side of the second one-way clutch F _2, the third brake B ₃ A return spring is provided in the comb tooth portion for controlling.

The clutch unit 6 is the first (forward) clutch C ₁
And the second (direct) comprises a clutch C _2, and is housed automatic transmission mechanism 10 ₁ rear end, i.e. on the opposite side transaxle cover 39 portion located on the edge portion of the torque converter 16. Further, as shown in detail in FIG.
A flange portion 54 is integrally connected to a rear end portion of the input shaft 5 via a connecting boss portion 5b, and a movable member 62 that constitutes a piston of the first clutch is fitted to the flange portion 54, Further, the movable member 62 is fitted with a piston member 63 which constitutes the piston of the second clutch. Further, the flange portion 54 has a stepped flange portion, and the inner peripheral surface of the small diameter side step portion 54c constitutes the cylinder 54a of the hydraulic actuator 66 for operating the first clutch C ₁ and the large diameter side thereof. A spline for coupling the clutch C ₁ is formed on the inner peripheral surface of the step portion 54d. The movable portion 62 also has a stepped collar portion 62c and a rising portion 62e at its tip, the inner peripheral surface of the inner diameter portion of which constitutes the cylinder 62b of the second clutch C ₂ operating hydraulic actuator 69, and the outer portion thereof. A clutch C ₂ connecting spline 62d is formed on the circumferential surface of the radial side, and constitutes a piston 62a of the hydraulic actuator 66 together with a rising portion 62e. Further, the movable member 62 has a flange portion at its inner diameter portion.
An oil chamber 65 is formed between the rising portion 62e and the oil chamber 65.
Is connected to the spline 54d of the flange portion 54 so as to prevent only relative rotation, and is in contact with the first clutch C ₁ with a small gap d ₁ . On the other hand, the piston member 63 forms an oil chamber 67 with the movable member 62, and has a second surface on the opposite side.
It is in contact with the _second clutch C ₂ at a distance d ₂ from the clutch C ₂ and is provided with a check valve 68 at its tip. The hydraulic actuator 69 has a structure in which the pressure oil in the oil chamber 67 is less likely to be removed by centrifugal force when the pressure oil is discharged, but the check valve 68 is configured to discharge the pressure oil at a predetermined pressure. The pressure oil inside is quickly discharged. Also, the hydraulic actuator 66 for the first clutch C ₁
Also, although not shown, a check valve is similarly provided. Further, a spring 70 is contracted between the piston member 63 and the ring fixed to the flange connecting boss portion 5b, and the spring 70 is a hydraulic actuator for both hydraulic actuators.
A return spring common to the piston members 62 and 63 of 66 and 69 is configured. Further, the first clutch C ₁ is interposed between the inner circumference of the flange portion 54 on the outer diameter side and the outer circumference of the ring gear R ₁ of the single unit 2, and the second clutch C ₂ includes the movable member 62.
It is interposed between the inner circumference of and the flange portion 53b connected to the tip of the hollow shaft 53. Further, the return spring 70 is provided on the inner diameter side of the second clutch C ₂ with the piston member 63 and the flange portion 53.
It is located between b and. The transaxle cover 39 is formed with a support annular collar portion 39a.
9a supports the input shaft 5 and forms an oil passage,
Hydraulic actuator 6 through the hole formed in boss 5b
Oil may be supplied to the oil chambers 65 and 67 of 6,69.

On the other hand, the additional shifting portion 20 ₂ has a counter shaft 71 which is rotatably supported by the axle case 37, a single planetary gear unit 26 for underdrive the tip portion of the shaft 71 (U / D) The sub-transmission unit 22 is attached. Further, a differential drive pinion 23 is connected to and supported by the shaft 71, and a counter driven gear that meshes with a counter drive gear 9 is provided on a hollow boss portion 23a of the pinion 23.
21 is rotatably supported by bearings. The planetary gear unit 26 includes a sun gear S ₃ , a carrier CR ₃ that supports the pinion P ₃ and is connected to the differential drive pinion 23, and a ring gear R ₃ that is integrally connected to the counter driven gear 21. Further, a boss member 76 on which the sun gear S ₃ is formed is rotatably supported on the shaft 71, and a flange portion 76a is coupled to the boss member 76. And the boss member 7
6 Connecting member 37c connected to the tip and axle case 37
The 4 (U / D) the one-way clutch F ₃ is interposed, also the 4 (U / D) brake B ₄ consisting of band brake on the outer periphery of the flange portion 76a is disposed between the . Further, the inner circumference of the flange portion 76a and the carrier C of the gear unit 26 are
A fourth (U / D direct) clutch C ₃ is interposed between R ₃ and R ₃ , and the clutch C ₃ is controlled by a hydraulic actuator 77 formed in the flange portion 76a. A spring 80 for returning the actuator 77 is arranged inside the flanged side plate 79 that constitutes the carrier CR ₃ .

Further, the differential portion 35 is rotatably supported by the axle case 37, and the left and right front axles 81, 81.
r, differential gear unit 82 and ring gear mount case, and left and right front axle 81
It is connected to 81r.

Next, the operation of the above embodiment will be described with reference to the schematic diagram shown in FIG. 5 and the operation table shown in FIG.

Engine torque is transmitted to the third speed input shaft 5 of the automatic transmission mechanism 10 ₁ through the torque converter 31. Then, in the speed-change mechanism section 10 _1, the third clutches C ₁ by the operation table shown in FIG, C _2, each brake B _1, B _2, B ₃ and the one-way clutch F _1, F ₂ described above operates Based on the above, the forward third speed and the reverse first speed are obtained, and the changed rotation is transmitted from the counter drive gear 9 to the counter driven gear 21 of the additional transmission unit 20 ₂ . Furthermore, in the additional transmission unit 20 _2, the clutch C ₃ by the operation table shown in FIG. 6, are 2 shift to the direct and U / D on the basis of the operation of the brake B ₄ and the one-way clutch F _3. Then, the automatic transmission mechanism unit 10 ₁ and the additional transmission unit 20 ₂
4 gears are combined, and a total of 4 forward speeds (maximum combination of 6 speeds possible) is obtained. That is, the first speed of the automatic transmission mechanism 10 ₁ is in the first speed and second speed and additional transmission portion 20 ₂ throughout In the U / D state, to obtain a second speed, then the automatic transmission mechanism 10 ₁ 2
In the state of high speed, the additional transmission unit 20 ₂ is switched to direct connection and
Then, the automatic transmission mechanism 10 ₁ is switched to the third speed from this state to obtain the fourth speed as a whole. Then, the fourth forward rotation is transmitted from the differential drive pinion 23 to the ring gear 85 of the differential portion 35, and further transmitted to the left and right float axles 81, 81r by the differential gear unit 85 to drive the front wheels.

Next, the automatic transmission 1 ₄ (1 ₅ ) including the 4-speed automatic transmission mechanism unit 10 ₂ will be described with reference to FIG. 7. Since the automatic transmission is different from the above-described embodiment only in the clutch portion of the automatic transmission mechanism portion, portions other than the clutch portion are denoted by the same reference numerals, and description thereof will be omitted.

Automatic transmission 1 ₄ (1 ₅₎ has a 4-speed automatic transmission mechanism 10 _2, and the speed-change mechanism section 10 ₂ clutch at a portion which is covered at its front end portion or the transaxle cover 39 ' 6 '. The clutch portion 6'is the first clutch
The third clutch C ₀ is arranged side by side with C ₁ in the axial direction,
Further, the third one-way clutch F ₀ is arranged between the return spring 70 and the flange portion 53b. Therefore, since the third clutch C ₀ and the one-way clutch F ₀ are located at different positions in the radial direction, the third clutch C ₀ is configured to be axially longer than the third speed automatic transmission mechanism 10 ₁ by the width of the clutch C ₀ . Further, the first clutch C ₁ and the second clutch C ₂ , and their hydraulic actuators 66 and 69 are the three-speed automatic transmission mechanism unit 10 _{1 described above.}
Substantially the same as the above, except that the ring gear R ₁ engaged with the first clutch C ₁ is engaged via the connecting member 92, and the flange portion engaged with the second clutch C _2. The difference is that the flange portion of 53b is axially long, and the flange portion 54 connected to the tip of the input shaft 5 is axially long. A cylindrical movable member 93 is fitted on the outer periphery of the flange portion 54, and the movable member 93 has a reaction force member whose one end inner peripheral surface is fitted to the flange portion 54.
The third clutch C ₀ fitted in 95 in an oil-tight manner and having an oil chamber 96
Constitutes an actuator for. Further, the movable member
A tongue member 99 capable of contacting the third clutch C ₀ is hung and fixed in the inner diameter direction at the tip of 93, and between the other end of the movable member 93 and the ring fixed to the flange portion 5a. The return spring 100 is retracted.

Next, the operation of the above-described embodiment will be described with reference to the schematic diagram shown in FIG. 8 and the operation table shown in FIGS. 9 and 10.

Input shaft 5 to which power is transmitted via the torque converter 31
Rotation, at four-speed automatic transmission mechanism 10 _2, the clutches C ₁ by the operation table, C _2, C _0, the brake B _1, B _2, B ₃ and the one-way clutch F _1, F _2, F of Based on the operation of _0, the fourth forward speed and the first reverse speed are obtained. Incidentally, R-range, the first speed in the 2nd range and D-range, 2 Hayatoki is omitted because it is the same as the 3-speed automatic transmission mechanism 10 ₁ described above. That is, in the third speed state in the D range, the third clutch C ₀ is connected in addition to the connection of the first clutch C ₁ . Then, the rotation of the input shaft 5 is transmitted via the clutch C ₁ to the ring gear of the single unit 2.
At the same time as being transmitted to R ₁ , it is transmitted to the ring gear R ₂ of the dual unit 3 via the clutch C ₀ . Therefore, the respective elements of both planetary gear units 2 and 3 rotate integrally, and the carrier CR transfers the counter drive gear 9 to the input shaft 5
And the same speed rotation is transmitted. At this time, the second brake B ₂
Keeps the locked state until the clutch C ₀ is engaged and prevents the gear from returning from the 2nd speed to the 1st speed once, and the engagement of the clutch C ₀ is completed and the planetary units 12 and 13 rotate integrally. In this state, the third one-way clutch F ₀ rotates synchronously. Then, in the fourth speed state, the first clutch C ₁ is disengaged and the first brake B ₁ is operated. Then, the rotation of the input shaft 5 is transmitted to the ring gear R ₂ of the dual unit 13 via the clutch C _0, and since the sun gear S in this state is stopped, while accelerating idle single unit ring gear R ₁ carrier The CR rotates at high speed, and the high speed rotation is taken out to the counter drive gear 9 as overdrive (O / D). Furthermore, shifting rotation of the counter drive gear, at the additional transmission unit 20 _2, the clutch C ₃ by the operation table is shifted to the direct and U / D on the basis of the operation of the brake B ₄ and the one-way clutch F _3. Then, the respective shifts of the automatic transmission mechanism 10 ₂ and the additional transmission unit 20 ₂ are combined, and the entire transmission has 5 forward speeds (1 ₄ ) or 6 forward speeds (1 ₅ ) (a maximum combination of 8 speeds is possible. ) Is obtained. To be more specific, the combination of the first speed of the 4-speed automatic transmission mechanism unit 10 ₁ and the U / D of the additional transmission unit 20 ₂ obtains the first speed as a whole, and then the additional transmission is performed with the mechanical unit 10 ₂ kept at the first speed. The section 20 ₂ is directly connected to obtain the second speed, the mechanism section 10 ₂ is further changed to the second speed, and the additional speed change section 20 _{2 is changed} to U / D to obtain the third speed. total to obtain a fourth speed by switching the ₂ only directly, and in the directly coupled state, the automatic transmission mechanism 10 ₂ third speed, fifth speed throughout switched to the fourth speed, so as to obtain a 6-speed, Susumusoku A 6-speed automatic transmission ₁₅ is obtained. Further, from the automatic transmission 1 _5, the automatic transmission mechanism 10 ₂ is added shifting portion 20 ₂ at the first speed is to remove the second gear comprising a U / D,
Automatic transmission 1 ₄ of the fifth forward speed is obtained.

(G) Effect of the Invention As described above, the axial direction of the automatic transmission mechanism is shortened, and the radial dimension of the rear end portion is made compact, so that interference with the vehicle frame in the bonnet is prevented. As a result, it is possible to secure the vehicle-mounted performance.

In addition, the above-mentioned axial dimension and radial dimension can be made compact to ensure vehicle mounting performance,
The first and second clutches arranged at the rear end of the automatic speed change mechanism can ensure appropriate clutch capacities corresponding to the torque capacities of different rotating elements, and can always reliably and reliably transmit power regardless of the gear stage. it can.

Further, since the first and second clutches are collectively arranged at the rear end of the automatic speed change mechanism, the number of speed change stages can be increased by adding a third clutch, for example, and the manufacturing equipment and parts can be commonly used. It is also possible to adapt to other types of vehicles by changing the type.

[Brief description of drawings]

FIG. 1 is an enlarged cross-sectional view showing an essential part of the present invention, FIG. 2 is a schematic view showing a three-speed automatic transmission mechanism to which the present invention can be applied, and FIG. 3 is a view showing operating states of respective elements thereof. . Further, FIG. 4 is an overall sectional view showing an embodiment according to the present invention, FIG. 5 is a schematic view thereof, and FIG. 6 is a view showing operating states of respective elements thereof. Further, FIG. 7 is an overall sectional view showing another embodiment according to the present invention, FIG. 8 is a schematic view thereof, and FIGS. 9 and 10 are views showing operating states of respective elements in different modes. 1 ₂ , 1 ₄ , 1 ₅ ...... Automatic transmission, 2 ...... Single planetary gear unit, 3 ...... Dual planetary gear unit, 6,6 '...... Clutch section, 5 ...... Input member, 9 ...... Output member, 10 ₁ ...... (3rd speed) automatic transmission (part), 10 ₂ ……
(4th speed) automatic transmission mechanism (part), 20 ₁ , 20 ₂ ... additional transmission part, 37 ... (transaxle) case, 39 ... (transaxle) cover, 54 ... flange part, 54a ... cylinder , 54c …… Small diameter side step, 54d …… Large diameter side step, 62…
... Piston (movable member) of the first clutch, 62b ... Cylinder, 62c ... Step collar, 62d ... Connection (spline)
Part, 63 ... Piston of second clutch (piston member),
65 ...... first oil chamber, 66 ...... hydraulic actuator, 67 ...... second oil chamber, 69 ...... hydraulic actuator, 70 ...... return spring, C ₁ ...... first clutch, C ₂ ...... second clutch, C ₃ ...
… Third clutch, B ₁ …… First brake, B ₂ …… Second brake, B ₃ …… Third brake, F ₁ …… First one-way clutch, F ₂ …… Second one-way Clutch, F ₀ ...
… Third one-way clutch, R ₁ , R ₂ , R ₃ …… Ring gear, S, S ₁ , S ₂ , S ₃ …… Sun gear, R ₁ …… First rotating element, S …… Second rotation Element, P, P ₁ , P ₂ …… Garyapinion, CR, CR ₁ , CR ₂ …… Third rotating element (carrier).

Claims (3)

[Claims] 1. An input member connected to an output portion of a torque converter, a planetary gear unit, a first clutch connecting between the input member and a first rotating element of the planetary gear unit, the input member and the A second clutch that connects the second rotating element of the planetary gear unit, an output member that connects to the third rotating element of the planetary gear unit, and locking means that appropriately locks a predetermined rotating element of the planetary gear unit. In an automatic transmission including an automatic transmission mechanism having the above, the rear end portion of the automatic transmission mechanism, which is the opposite side of the planetary gear unit to the torque converter, is connected to the input member via a boss portion on the inner diameter side. With
A flange portion is arranged in which the rear end side is a small diameter side step portion and the planetary gear unit side is a large diameter side step portion, and the first clutch is arranged on an inner peripheral surface of the large diameter side step portion of the flange portion. And a cylinder of the first clutch formed on the inner peripheral side of the small-diameter side step portion of the flange portion and a cylinder of the first clutch arranged so that relative rotation is prevented, and the inner diameter side is a boss of the flange portion. A piston of a first clutch that is supported by an axially movable portion, a cylinder of the first clutch, a piston of the first clutch, and a first oil chamber configured by a boss portion of the flange portion. , The large-diameter side step portion of the flange portion and the first rotating element of the planetary gear unit are moved by the movement of the piston of the first clutch based on the supply of hydraulic oil to the first oil chamber. The second clutch is connected to the second clutch, and the second clutch is disposed on the inner peripheral surface of the piston of the first clutch and is formed on the inner peripheral side of the piston of the first clutch, and the second clutch. Of the second clutch, the inner diameter side of which is supported by the boss of the flange so as to be axially movable, the cylinder of the second clutch, the piston of the second clutch, and the boss of the flange. A second oil chamber constituted by a second portion of the planetary gear unit and a flange of the planetary gear unit by the movement of the piston of the second clutch based on the supply of hydraulic oil to the second oil chamber. A clutch device in an automatic transmission, characterized in that the rotating elements of are connected. 2. The automatic transmission according to claim 1, further comprising a return spring for urging both the piston of the first clutch and the piston of the second clutch to a release side. Clutch device. 3. The planetary gear unit has a single planetary gear and a dual planetary gear, and carriers of both planetary gears and sun gears are integrally connected to each other, and the planetary gear unit is connected to the input member via the first clutch. One rotating element is the ring gear of the single planetary gear unit, the second rotating element connected via the second clutch is the sun gear, and the third rotating element is further connected to the output member.
The rotary element of is the carrier, and the predetermined rotary element that is appropriately locked by the locking means is the ring gear of the sun gear and the dual planetary gear. A clutch device in the automatic transmission according to item 2.