JP2002266956A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission capable of obtaining a gear ratio of ahead 8 stage appropriately spaced. SOLUTION: A second ring gear of a speed reduction planetary gear device having a carrier supporting a long pinion engaged with a sun gear and a pinion engaged with the long pinion; a second ring gear engaged with the long pinion; and a first ring gear engaged with the pinion is connected to an input shaft by a fourth clutch and the sun gear and the first ring gear are connected to first and second brakes and are connected to each other by a first clutch. A ring gear of a first planetary gear mechanism and a carrier of a second planetary gear mechanism are connected to each other, are connected to an input shaft by a second clutch and are connected to a third brake. The ring gear of the second planetary gear mechanism is connected to the carrier of the speed reduction planetary gear device and the sun gears of the first and second planetary gear mechanisms are connected to each other by a third clutch. The sun gear of the first planetary gear mechanism is connected to a fourth brake and the carrier is connected to an output shaft.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compound planetary gear device for speed reduction connected to an input shaft and a control clutch and a control brake connected to respective elements of a compound planetary gear device for speed change, which are disengaged from the input shaft. The present invention relates to an automatic transmission that transmits rotation to an output shaft by shifting the rotation to a plurality of stages.

[0002]

2. Description of the Related Art A sun gear, a carrier for supporting a long pinion meshing with the sun gear and an intermediate pinion meshing with the long pinion, a second ring gear meshing with the long pinion, and a first ring gear meshing with the intermediate pinion are provided. A second planetary gear set for reduction; a second ring gear of the double planetary gear set for reduction connected to an input shaft; a sun gear and a first ring gear connected to first and second control brakes; The first and second planetary gear mechanisms constitute a double planetary gear device for speed change, and the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism are connected and input. The shaft is removably connected to the shaft by a second control clutch and is connected to a third control brake to reduce the ring gear of the second planetary gear mechanism. And the sun gears of the first and second planetary gear mechanisms are removably connected by a third control clutch, and the sun gear of the first planetary gear mechanism is connected to a fourth control brake. An automatic transmission that connects a carrier of a first planetary gear mechanism to an output shaft to achieve a gear ratio of seven forward speeds and three reverse speeds is disclosed in 2000-266.
No. 138 publication.

[0003]

The above-mentioned conventional automatic transmission can change the gear ratio between seven forward speeds and three reverse speeds. However, in recent years, in order to improve fuel economy and power transmission performance, or to obtain a gear ratio that matches the driver's preference, an automatic transmission that can establish an eight-stage forward gear ratio that is appropriately separated has been demanded. Have been.

SUMMARY OF THE INVENTION The present invention has been made in order to meet such a demand, and it is an object of the present invention to provide an automatic transmission which can obtain a gear ratio of eight forward gears which are appropriately separated.

[0005]

Means for Solving the Problems In order to solve the above-mentioned problems, the structural features of the invention according to claim 1 include a sun gear, a long pinion meshed with the sun gear, and an intermediate pinion meshed with the long pinion. Carrier that supports
A speed reducing double planetary gear device having a second ring gear meshing with the long pinion and a first ring gear meshing with the intermediate pinion is provided, and the second ring gear of the speed reducing double planetary gear device is connected to an input shaft by a fourth control clutch. The sun gear and the first ring gear are connected to first and second control brakes, respectively, and are connected to each other by a first control clutch so as to be disengageable. A double planetary gear device for shifting is constituted, wherein the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism are connected to each other so as to be detachably connected to the input shaft by the second control clutch, and to the third control brake. The ring gear of the second planetary gear mechanism is connected to the carrier of the compound planetary gear device for reduction, and the sun gears of the first and second planetary gear mechanisms are controlled by the third control. While linked to disengage the latch, the sun gear of the first planetary gear mechanism is connected to the fourth control brake is that the concatenation of the carrier of the first planetary gear mechanism to the output shaft.

According to a second aspect of the present invention, a sun gear, a carrier for supporting a long pinion meshing with the sun gear and an intermediate pinion meshing with the long pinion, a second ring gear meshing with the long pinion, and A double reduction planetary gear set having a first ring gear meshing with the intermediate pinion is provided, a second ring gear of the double reduction gear planetary gear apparatus is connected to an input shaft, and the sun gear and the first ring gear are first and second gears. The first and second planetary gear mechanisms constitute a speed change double planetary gear device, and are connected to the second control brake and the first control clutch, respectively. 2 Connect the carrier of the planetary gear mechanism
The control clutch is releasably connected and connected to the third control brake. The ring gear of the second planetary gear mechanism is connected to the carrier of the double planetary gear device for reduction and connected to the fifth control brake. The sun gears of the two planetary gear mechanisms are releasably connected by the third control clutch, the sun gear of the first planetary gear mechanism is connected to the fourth control brake, and the carrier of the first planetary gear mechanism is connected to the output shaft. That is.

[0007]

According to the first aspect of the present invention, a carrier that supports a sun gear, a long pinion that meshes with the sun gear, and an intermediate pinion that meshes with the long pinion, meshes with the long pinion. The second ring gear of the compound planetary gear device for reduction having the second ring gear to be engaged and the first ring gear meshing with the intermediate pinion is selectively connected to the input shaft by a fourth control clutch, and the sun gear and the first ring gear are connected to the first and second ring gears. The second control brake selectively restricts the rotation and selectively connects the first control clutch to each other, and connects the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism of the double planetary gear device for shifting. Selectively connected to the input shaft by the second control clutch, and selectively restricts rotation by the third control brake. The gear is connected to the carrier of the compound planetary gear device for reduction, and the sun gears of the first and second planetary gear mechanisms are selectively connected by the third control clutch, and the rotation of the sun gear of the first planetary gear mechanism is controlled by the fourth control. Since the carrier is selectively controlled by the brake and the carrier of the first planetary gear mechanism is connected to the output shaft, the forward rotation of the conventional automatic transmission can be achieved by simply adding one control clutch to appropriately rotate the rotation of the input shaft. It is possible to provide an automatic transmission which can transmit a gear at a gear ratio of a gear and output the gear to an output shaft. Furthermore, since the gear ratio on the high speed side can be made denser, the engine performance can be optimally brought out in the high speed range of the vehicle speed, and the change in the gear ratio at the time of a gear change, and hence the change in the output torque. And a good feeling can be obtained.

[0008] In the invention according to claim 2, the carrier supports the sun gear, the long pinion meshed with the sun gear, and the intermediate pinion meshed with the long pinion, and the second ring gear meshes with the long pinion. And a second ring gear of the compound planetary gear device for reduction having a first ring gear meshing with the intermediate pinion is connected to the input shaft, and the sun gear and the first ring gear are selectively rotated by the first and second control brakes. The first control clutch is selectively connected to each other, and the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism of the double planetary gear device for shifting are selectively connected to the input shaft by the second control clutch. The rotation of the ring gear of the second planetary gear mechanism is controlled by the third control brake. Selectively rotation restricting the fifth control brake with coupling to the rear, selectively connects the sun gears of the first and second planetary gear mechanism in the third control clutch,
Since the rotation of the sun gear of the first planetary gear mechanism is selectively restricted by the fourth control brake, and the carrier of the first planetary gear mechanism is connected to the output shaft, only one control brake is applied to the conventional automatic transmission. Thus, it is possible to transmit the rotation of the input shaft to the output shaft by shifting the rotation at an appropriately separated eight forward gear ratio. Furthermore, since the gear ratio on the high speed side can be made denser, the engine performance can be optimally brought out in the high speed range of the vehicle speed, and the change in the gear ratio at the time of a gear change, and hence the change in the output torque. And a good feeling can be obtained.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of an automatic transmission according to the present invention will be described below with reference to the drawings. In FIG. 1, reference numeral 10 denotes an automatic transmission according to the present invention, for example, a fluid torque converter 1 rotationally driven by an automobile engine.
1 is used to transmit the output rotation to the drive wheels at a variable speed. The automatic transmission 10 includes an input shaft 15, a double reduction planetary gear unit 16, a double transmission planetary gear unit 17, and an output shaft 18, which are sequentially supported on a common axis 13 in a transmission case 12 mounted on a vehicle body. Have been. The compound planetary gear unit 16 for reduction includes the sun gears S1 and S2 and the carriers C1 and C2 of the double pinion type planetary gear mechanism 21 and the single pinion type planetary gear mechanism 22.
Are connected and shared. That is, the common axis 1
3, common sun gears S1, S rotatably supported on
2. Long pinion 2 meshing with sun gears S1 and S2
3. Common carriers C1, C rotatably supported on the common axis 13 and rotatably supporting the long pinion 23 and the intermediate pinion 24 meshing with the long pinion 23.
2. Ring gears R2 and R1 meshed with the long pinion 23 and the intermediate pinion 24, respectively, and rotatably supported on the common axis 13. The ring gear R2 is the fourth
The control clutch C-4 is detachably connected to the input shaft 15. Sun gears S1, S2 and first ring gear R
1 is connected to first and second control brakes B-1 and B-2 provided on the transmission case 12, respectively, and is connected to each other by a first control clutch C-1 so as to be disengageable. Carriers C1 and C2 are one-way clutches F-
1 is connected to the transmission case 12 to restrict reverse rotation.

The dual gear planetary gear set 17 includes a sun gear, a ring gear rotatably supported on a common axis 13,
It is composed of first and second planetary gear mechanisms 25 and 26 of a single pinion type composed of a carrier that supports a pinion that meshes with a sun gear and a ring gear. Ring gear R3 of first planetary gear mechanism 25 and second planetary gear mechanism 25
Are connected to the carrier C4 to form connection elements R3 and C4. The connection elements R3 and C4 are removably connected to the input shaft 15 by the second control clutch C-2 and are provided on the transmission case 12. Third control brake B-3
It is connected to. The ring gear R4 of the second planetary gear mechanism 26 is connected to the carriers C1, C of the compound planetary gear unit 16 for reduction.
2 are connected. First and second planetary gear mechanisms 25,
Each of the twenty-six sun gears S3 and S4 has a third control clutch C-
3 are connected to each other in a detachable manner. The sun gear S3 of the first planetary gear mechanism 25 is connected to a fourth control brake B-4 provided on the transmission case 12.
The carrier C3 of the first planetary gear mechanism 21 is connected to the output shaft 18.

The pump impeller 30 of the fluid torque converter 11 is driven to rotate by an engine (not shown) to send out oil, and the stator 31 receives a reaction force of the oil and generates torque to the turbine 32. The input shaft 15 is connected to a turbine 32. 33
Is a lock-up clutch that directly connects the pump impeller 30 and the turbine 32.

The automatic transmission 10 constructed as described above
Selectively engages and disengages the first to fourth control clutches C-1 to C-4 and selectively operates the first to fourth control brakes B-1 to B-4 to reduce and shift the speed. Planetary gear 1
By regulating the rotation of the elements 6 and 17,
A gear ratio of three-stage and reverse can be established. In FIG. 2, a black circle in the column of each control clutch and control brake corresponding to each shift speed indicates that the control clutch is in the connected state and the control brake is in the rotation restricting state. Further, FIG. 2 shows the gear ratio (the number of revolutions of the input shaft 15 / the number of revolutions of the output shaft 18) at each speed stage and the increase ratio of the gear ratio when the speed stage is increased by one stage (the gear ratio at this speed stage). / Gear ratio of the previous gear).

In the double pinion type planetary gear mechanism 21 of the compound planetary gear unit 16 for reduction, the sun gear rotation speed Ns, the carrier rotation speed Nc, and the ring gear rotation speed Nr
The relationship between the gear ratio and the gear ratio λ of the planetary gear mechanism is expressed by Expression (1), and the single pinion type planetary gear mechanism 22 and the single pinion type first and second planetary gear mechanisms 22 of the double planetary gear device 16 for reduction.
In the planetary gear mechanisms 25 and 26, the rotation speed Ns of the sun gear, the rotation speed Nc of the carrier, and the rotation speed Nr of the ring gear
The relationship between the gear ratio and the gear ratio λ of the planetary gear mechanism is expressed by Expression (2), and the gear ratio at each shift speed is calculated based on Expressions (1) and (2). The number of teeth of the sun gears S1, S2, S3, S4 is Zs1, Zs2, Zs3, Zs4, and the ring gear R
1, R2, R3, and R4 are Zr1, Zr2, and Zr.
3, Zr4, the planetary gear mechanisms 21, 22, of the compound planetary gear device 16 for reduction and the compound planetary gear device 17 for speed change.
The gear ratio of 25, 26 is λ1 = Zs1 / Zr1, λ2 = Z
s2 / Zr2, λ3 = Zs3 / Zr3, λ4 = Zs4 /
Zr4. Nr = (1−λ) Nc + λNs (1) Nr = (1 + λ) Nc−λNs (2)

First to fourth control brakes B-1 to B-4
Are selectively operated, and the first to fourth control clutches C- 1 to C- 1 are operated.
When C-4 is selectively connected, the speed ratio of each element of the compound planetary gear device 16 for reduction and the compound planetary gear device 17 for speed change is as shown in the speed diagram shown in FIG. The velocity diagram is
In the planetary gear device, each element including a sun gear, a carrier, and a ring gear is arranged at an interval corresponding to a gear ratio in a horizontal axis direction, and a speed ratio is taken in a vertical axis direction corresponding to each element. FIG. 3 shows speed diagrams of the compound planetary gear units 16 and 17 for speed reduction and speed change, arranged side by side. In the compound planetary gear device 16 for reduction, the sun gear S1,
Since S2 and carriers C1 and C2 are common,
S1, S2 and common sun gears S1, S2 and common carrier C on one vertical line respectively marked with C1, C2.
1 and C2, and the speed ratio of the ring gears R1 and R2 on one vertical line with R1 and R2 respectively. Regarding the double pinion type planetary gear mechanism 21,
Set the distance between the vertical line of the carrier C1 and the vertical line of the sun gear S1 to 1
Therefore, the vertical line of the ring gear R1 is disposed on the same side as the vertical line of the sun gear S1 from the vertical line of the carrier C1 and separated by an interval λ1. Regarding the single pinion type planetary gear mechanism 22, the distance between the vertical line of the carrier C2 and the vertical line of the sun gear S2 is regarded as 1, and the vertical line of the ring gear R2 is defined as the carrier C.
2 is arranged on the opposite side of the vertical line of the sun gear S2 from the vertical line of FIG.

In the double compound planetary gear set 17 for shifting, first,
Since the ring gear R3 of the second planetary gear mechanisms 25 and 26 and the carrier C4 are connected and the sun gears S3 and S4 are connected, the ring gears R3, C4 and S3 and S4 are connected on one vertical line respectively. Ring gear R3 and carrier C
4, the speed ratio between the sun gears S3 and S4,
4, a ring gear R4 on one vertical line with C3
Represents the speed ratio of carrier C3. Since the first planetary gear mechanism 25 is of a single pinion type, the distance between the vertical line of the ring gear R3 and the vertical line of the sun gear S3 is regarded as 1 + λ3, and the vertical line of the carrier C3 is shifted from the vertical line of the sun gear S3 to the vertical line of the ring gear R3. Are placed on the same side at a distance of one. Second
Since the planetary gear mechanism 26 is also of a single pinion type, the interval between the vertical line of the carrier C4 and the vertical line of the sun gear S4 is regarded as 1, and the vertical line of the ring gear R4 is opposite to the vertical line of the sun gear S4 from the vertical line of the carrier C4. On the side at a distance of λ4. In the velocity diagram, the first to fourth control brakes B-
1 to B-4, first to fourth control clutches C-1 to C-4
Are selectively activated at points B-1 to B-4 and C-1 to C-4.
-2 is entered.

In the speed diagram of the gearshift compound planetary gear set 17 thus created, the elements corresponding to the four vertical lines are represented by the first, second, third, and fourth elements in the order in which the vertical lines are arranged. And In the case of the first embodiment, the ring gear R4 as the first element is a common carrier C of the compound planetary gear unit 16 for reduction.
, C2, the ring gear R3 and the carrier C4, which are connected to each other as a second element, are connected to the second control clutch C
-2 and the third control brake B-3 are connected in parallel, the carrier C3 as a third element is connected to the output shaft 18,
The sun gears S3 and S4 as the fourth element are the third clutch C
-3, the sun gear S3 is connected to the fourth control brake B-4.

The operation of each shift speed will be described below.
In the case of the first forward speed, the second control brake B-2 is operated, the rotation of the ring gear R1 is regulated, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15.
And the compound planetary gear unit 16 for reduction is
A first decelerated rotation having a lower rotation speed than the rotation of the input shaft 15 is generated on the carriers C1 and C2. This first deceleration rotation is the first
The third control clutch C-3 is operated to connect the sun gears S3 and S4, and the fourth control brake B-4 is operated to regulate the rotation of the sun gears S3 and S4. The carrier C3, which is the third element, and the output shaft 18 are driven to rotate normally at the first gear ratio of 5.428.

In the case of the second forward speed, the first control brake B-1 is operated to regulate the rotation of the sun gears S1 and S2, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15. The speed reduction double planetary gear device 16 has a rotation speed smaller than that of the
The second deceleration rotation larger than the deceleration rotation is performed by the carriers C1 and C2.
To generate. The second reduced rotation is transmitted to the ring gear R4, which is the first element, the third control clutch C-3 is operated to connect the sun gears S3 and S4, and the fourth control brake B
-4 operates to regulate the rotation of the sun gears S3 and S4, so that the carrier C3, which is the third element, and the output shaft 18 are driven to rotate forward at the gear ratio of the second shift stage of 3.092.

In the case of the third forward speed, the fourth control clutch C-4 is connected, the second ring gear R2 is driven to rotate by the input shaft 15, the first control clutch C-1 is operated, and the sun gears S1 and S2 are operated. And the ring gear R1 are connected to each other, so that the compound planetary gear unit 16 for reduction is rotated integrally so that the input rotation of the same speed as the input shaft 15 is carried out by the carriers C1, C2.
To be generated. This input rotation is transmitted to the ring gear R4, which is the first element, the third control clutch C-3 is operated to connect the sun gears S3 and S4, and the fourth control brake B-4
Operates to regulate the rotation of the sun gears S3 and S4.
The carrier C3, which is the third element, and the output shaft 18 are driven to rotate normally at a gear ratio of 2.061 at the third speed.

In the fourth forward speed, the second control clutch C-2 is connected, the ring gear R3 is rotated at the same speed as the input shaft 15, the fourth control brake B-4 is operated, and the sun gear S3 is moved. Because the rotation is regulated, the carrier C3,
The output shaft 18 is normally driven at a gear ratio of 1.405 at the fourth speed. At this time, the fourth control clutch C-4 is connected, the second ring gear R2 is rotationally driven by the input shaft 15, the first control clutch C-1 is operated, and the sun gear S
1, S2 and the ring gear R1 are connected, so that the compound planetary gear unit 16 for reduction is integrally rotated by the input rotation.

In the fifth forward speed, the fourth control clutch C-4 is connected, the second ring gear R2 is driven to rotate by the input shaft 15, the first control clutch C-1 is operated, and the sun gears S1 and S2 are operated. And the ring gear R1 are connected to each other, so that the compound planetary gear unit 16 for reduction is rotated integrally so that the input rotation of the same speed as the input shaft 15 is carried out by the carriers C1, C2.
To be generated. This input rotation is transmitted to the ring gear R4 which is the first element, the second control clutch C-2 is connected, the coupling elements R3 and C4 are rotated at the same speed as the input shaft 15, and the third control clutch C-3 Is activated and the sun gear S3
Since S4 is connected, the dual gear planetary gear set 17 for rotation is rotated integrally, and the carrier C3 and the output shaft 18 are driven to rotate normally at the gear ratio of the fifth shift stage of 1.000.

In the case of the sixth forward speed, the first control brake B-1 is operated to regulate the rotation of the sun gears S1 and S2, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15. And the compound planetary gear unit 16 for reduction drives the second reduced rotation by the carriers C1 and C2.
To be generated. This second reduced rotation is transmitted to the ring gear R4 as the first element, and the connecting elements R3 and C4 are connected to the input shaft 15 by the second control clutch C-2, and the sun gear S
Since S3 and S4 are connected by the third control clutch C-3, the carrier C3 is driven to rotate forward at a gear ratio of 0.829 at the sixth speed according to the rotation difference between the input rotation and the second reduced rotation. .

In the case of the seventh forward speed, the second control brake B-2 is operated, the rotation of the first ring gear R1 is restricted, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15. And the compound planetary gear unit 16 for reduction drives the first reduced rotation by the carriers C1 and C2.
To be generated. This first reduced rotation is transmitted to the ring gear R4, which is the first element, and the coupling elements R3, C4 are connected to the input shaft 15 by the second control clutch C-2, and the sun gear S
Since S3 and S4 are connected by the third control clutch C-3, the carrier C3 is normally driven at a gear ratio of 0.723 at the seventh speed in accordance with the rotation difference between the input rotation and the first reduced rotation. .

In the case of the eighth forward speed, the connecting elements R3, C
4 is connected to the input shaft 15 by a second control clutch C-2 and is input-rotated, and the double reduction gear planetary gear unit 16 connected and integrated with the first control clutch C-1 is connected to the second control brake B-. 2, the rotation of the ring gear R4, which is the first element, is restricted, and the sun gears S3, S
4 is connected by the third control clutch C-3, so that the carrier C3 is driven to rotate forward at the gear ratio of 0.618 at the eighth speed.

The first control clutch C-1 is connected and the first control brake B-1 is actuated in order to restrict the rotation of the ring gear R4 by integrating the speed reducing double planetary gear unit 16 and restricting the rotation. Or the first and second
The control brakes B-1 and B-2 may be operated.

In the case of the reverse first speed, the second control brake B-2 is operated to regulate the rotation of the first ring gear R1, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15. And the compound planetary gear unit 16 for reduction drives the first reduced rotation by the carriers C1 and C2.
To be generated. This first decelerated rotation is transmitted to the ring gear R4, which is the first element, and the third control brake B-3 is operated to restrict the rotation of the coupling elements R3 and C4.
3 and S4 are connected by the third control clutch C-3,
The carrier C3 and the output shaft 18 are reversely driven at a reverse first gear ratio of 4.260.

In the case of the second reverse speed, the first control brake B-1 is operated to regulate the rotation of the sun gears S1 and S2, the fourth control clutch C-4 is connected, and the second ring gear R2 is connected to the input shaft 15. And the compound planetary gear unit 16 for reduction drives the second reduced rotation by the carriers C1 and C2.
To be generated. The second reduced rotation is transmitted to the ring gear R4, which is the first element, and the third control brake B-3 is operated to restrict the rotation of the coupling elements R3 and C4, and the sun gear S
3 and S4 are connected by the third control clutch C-3,
The carrier C3 and the output shaft 18 are driven to rotate in reverse at a reverse second gear ratio of 2.427.

In the case of the third reverse speed, the fourth control clutch C-4 is connected, the second ring gear R2 is driven to rotate by the input shaft 15, the first control clutch C-1 is operated, and the sun gears S1 and S2 are operated. And the ring gear R1 are connected to each other, so that the compound planetary gear unit 16 for reduction is rotated integrally so that the input rotation of the same speed as the input shaft 15 is carried out by the carriers C1, C2.
To be generated. This input rotation is transmitted to the ring gear R4, which is the first element, and the third control brake B-3 is operated to restrict the rotation of the connection elements R3, C4, and the sun gears S3, S4
4 is connected by the third control clutch C-3, so that the carrier C3 and the output shaft 18 are in a reverse third gear ratio of 1.61.
8 is driven in reverse.

Assuming that the number of revolutions of the input shaft 15 is 1, the sun gears S1 to S4 and the carriers C1 to C4 at each shift speed are provided.
3, and the rotation diagram of FIG. 3 showing the rotation ratios of the ring gears R1 to R4, the rotation ratio of the carrier C3, which is the third element in each shift speed, that is, the gear ratio is arranged at appropriate intervals. ADVANTAGE OF THE INVENTION According to the automatic transmission which concerns on this invention, the gear ratio of 8 steps | paragraphs of forwards and 3 steps | paragraphs of back which were appropriately separated can be obtained. Further, as shown in FIG. 2, the increase ratio of the gear ratio when the gear is increased by one gear is 1.756 between the first and second gears, and 1 between the second and third gears. .50
1.467 between the 0th, 3rd, and 4th gears, 1.405 between the 4th and 5th gears, 1.2 between the 5th and 6th gears
1.147, seventh and eighth gears between the sixth, sixth and seventh gears
The gear ratio is 1.170. The higher the gear ratio, the smaller the increase ratio is, the more optimally the engine performance can be obtained in a high vehicle speed range, and the change ratio of the gear ratio at the time of gear change, and thus the output. The rate of change of torque is reduced,
Good feeling can be obtained. Further, the spread obtained by dividing the gear ratio of the lowest shift speed by the gear ratio of the highest shift speed is sufficiently large at 8.78, so that the acceleration performance can be improved in the low shift speed and the fuel efficiency can be improved in the high shift speed. .

In the first embodiment, the second ring gear R2 of the compound planetary gear unit 16 for reduction is removably connected to the input shaft 15 by the fourth control clutch C-4, and the carriers C1 and C2 are combined with the compound gears for shifting. The planetary gear unit 17 is connected to the ring gear R4 which is the first element.
In the embodiment, as shown in FIG. 4, the second ring gear R2
Is directly connected to the input shaft 15, and the double planetary gear train 1 for shifting
Ring gear R4, which is the first element of carrier 7, is connected to carriers C1, C
2 and the fifth control brake B-5.

FIG. 5 shows the operation state of each control clutch and control brake at each shift speed in the second embodiment.
The gear ratio and the rate of increase at each gear are the same as in the first embodiment. The velocity diagram, as shown in FIG.
This is substantially the same as the case of the first embodiment. The operation of each speed stage is such that the second ring gear R2 of the compound planetary gear device 16 for reduction is rotationally driven by the input shaft 15 via the fourth control clutch C-4 or is directly rotated except in the eighth forward speed. Since the operation is the same except for the difference between the driving and the driving, the description is omitted.

In the case of the eighth forward speed, the connecting elements R3, C
4 is connected to the input shaft 15 by the second control clutch C-2 and is input and rotated. The operation of the fifth control brake B-5 restricts the rotation of the ring gear R4, which is the first element, and the sun gears S3 and S4 Since the third control clutch C-3 is engaged, the carrier C3 has a gear ratio of 0.6 at the eighth speed.
The motor 18 is driven to rotate forward.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram showing a first embodiment of an automatic transmission according to the present invention.

FIG. 2 is a diagram showing operating states of a control brake and a control clutch at each speed stage of the first embodiment.

FIG. 3 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each speed stage of the first embodiment.

FIG. 4 is a skeleton diagram showing a second embodiment.

FIG. 5 is a diagram showing operating states of a control brake and a control clutch at each speed stage of the second embodiment.

FIG. 6 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each speed stage of the second embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Automatic transmission, 11 ... Fluid torque converter, 12 ... Transmission case, 13 ...
Common axis, 15: Input shaft, 16: Double planetary gear unit for reduction, 17: Double planetary gear unit for speed change, 18
... output shaft, 25 ... first planetary gear mechanism, 26 ...
-Second planetary gear mechanism, S1, S2, S3, S4 ... sun gear, C1, C2, C3, C4 ... carrier, R
1, R2, R3, R4 ... ring gear, R3, C4
..Connection elements, C-1, C-2, C-3, C-4,.
First, second, third, fourth, control clutches, B-1, B-
2, B-3, B-4, B-5 ... first, second, third,
Fourth and fifth control brakes.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Satoru Kasuya 10 Takane, Fujiimachi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd.・ Within AW Co., Ltd. (72) Inventor Toshihiko Aoki 10th Takane, Fujiimachi, Anjo-shi, Aichi F-term in Aisin AW Co., Ltd. (reference) 3J028 EA30 EB09 EB15 EB37 EB54 EB62 FA06 FB03 FC26 FC59 FC62 GA02

Claims (2)

[Claims] A sun gear, a carrier for supporting a long pinion meshing with the sun gear and an intermediate pinion meshing with the long pinion, a second ring gear meshing with the long pinion, and a first ring gear meshing with the intermediate pinion. A second planetary gear unit for reduction; a second ring gear of the double planetary gear unit for reduction is detachably connected to an input shaft by a fourth control clutch, and the sun gear and the first ring gear are first and second control units; Each of the first and second planetary gear mechanisms constitutes a double planetary gear device for speed change, and the ring gear and the second planetary gear of the first planetary gear mechanism. A gear mechanism carrier is connected to the input shaft so as to be disengageable by a second control clutch and to a third control brake, The ring gear of the second planetary gear mechanism is connected to the carrier of the compound planetary gear device for reduction, the sun gears of the first and second planetary gear mechanisms are removably connected by the third control clutch, and the first planetary gear mechanism is provided. Wherein the sun gear is connected to a fourth control brake, and the carrier of the first planetary gear mechanism is connected to the output shaft. 2. A sun gear, a carrier for supporting a long pinion meshing with the sun gear and an intermediate pinion meshing with the long pinion, a second ring gear meshing with the long pinion, and a first ring gear meshing with the intermediate pinion. A double planetary gear unit for reduction is provided, a second ring gear of the double planetary gear unit for reduction is connected to an input shaft, and the sun gear and the first ring gear are connected to the first and second ring gears.
The first and second planetary gear mechanisms constitute a double planetary gear device for speed change. The first and second planetary gear mechanisms form a double planetary gear device for gear shifting. The carrier of the planetary gear mechanism is connected to the input shaft so as to be removably connected to the input shaft by the second control clutch and connected to the third control brake, and the ring gear of the second planetary gear mechanism is used as the carrier of the double planetary gear device for reduction. Connected to the fifth control brake, the sun gears of the first and second planetary gear mechanisms are removably connected by the third control clutch, and the sun gear of the first planetary gear mechanism is connected to the fourth control brake. An automatic transmission, wherein the carrier of the first planetary gear mechanism is connected to the output shaft.