JP2002168313A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten the set length of gear ratio steps between the second and first speed stages and between the second and third speed stages in the axial direction of a transmission. SOLUTION: The transmission comprises one double-pinion planetary gear G1, three single pinion planetary gears G2, G3 and G4, two friction clutch elements C1 and C2, and three friction brake elements B1, B2 and B3. The forward sixth speed stage and the reverse first speed stage are obtained by engaging/disengaging the friction clutches C1 and C2 and the friction brakes B1, B2 and B3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission, and more particularly to a transmission used for an automatic transmission of an automobile.

[0002]

2. Description of the Related Art Conventionally, in a forward six-speed transmission used for an automatic transmission of an automobile, a friction engagement element includes:
It is customary to have two clutches and three brakes, such arrangements being disclosed, for example, in US Pat.
5,792 and JP-A-6-323381.

[0003]

However, in the devices disclosed in the above two publications, the gear ratio of the second speed can be set only to around 2, and the gear ratio between the first speed and the second speed and the gear ratio of the second speed can be set.
There was a problem that the gear ratio step between the third speed and the third speed increased.

In order to solve such a problem, for example, a device disclosed in Japanese Patent Application Laid-Open No. Hei 4-290649 employs a double planetary gear unit in the first gear train to increase the degree of freedom of the gear ratio. However, on the other hand, the frictional engagement element is composed of three clutches and two brakes, and there is a problem that the axial length of the device is increased and the mountability on the vehicle is deteriorated.

[0005] Therefore, the present invention can reduce the axial length of the apparatus by appropriately controlling the planetary gear mechanism using two friction clutch elements and three friction brake elements. An object of the present invention is to provide a transmission capable of obtaining a second reverse speed.

[0006]

Means for Solving the Problems The first technical means taken to solve the above-mentioned technical problem is, as described in claim 1, "an input shaft 11, an output shaft 12, and the input shaft 11. A first row of double pinion planetary gears G1 having a sun gear S1 constantly connected to the shaft 11, a second row of single pinion planetary gears G2, a third row of single pinion planetary gears G3, and a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the first row of double pinion planetary gears G1, the ring gear R2 of the second row of single pinion planetary gears G2, and the sun gear S3 of the third row of single pinion planetary gears G3; , The fourth
Carrier P of single pinion planetary gear G4 in row
C4 is the second row single pinion planetary gear G
The second carrier PC2 is connected to the carrier PC3 of the third row of single pinion planetary gears G3.
A third shaft element J3 connecting the sun gear S4 of the fourth row of single pinion planetary gears G4 and the ring gear R3 of the third row of single pinion planetary gears G3 to the output shaft 12, and an input shaft. A fourth shaft element J4 connecting the second gear 11 to the sun gear S2 of the second row of single pinion planetary gears G2; a ring gear G of the second row of single pinion planetary gears G2;
2 and the third row of single pinion planetary gears G3
And a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2. , A first friction brake element B1 for selectively fixing the first shaft element J1, and a second friction brake for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4. Element B2
And a third friction brake element B3 for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1.

[0007] This is what constitutes.

[0008] A second technical means taken to solve the above-mentioned technical problem is as follows: "The input shaft 11, the output shaft 12, and the input shaft 11 are always connected. , A first row of double pinion planetary gears G1, a second row of single pinion planetary gears G2, a third row of single pinion planetary gears G3, and a fourth row of single pinion planetary gears G
4 and the first row of double pinion planetary gears G1
A first shaft element J1 for connecting a ring gear R2 of the second row of single pinion planetary gears G2 and a sun gear S3 of the third row of single pinion planetary gears G3 mutually connected to the ring gear R1;
Carrier P of single pinion planetary gear G4 in row
C4 is the second row single pinion planetary gear G
The second carrier PC2 is connected to the carrier PC3 of the third row of single pinion planetary gears G3.
A third shaft element J3 connecting the sun gear S4 of the fourth row of single pinion planetary gears G4 and the ring gear R3 of the third row of single pinion planetary gears G3 to the output shaft 12, and an input shaft. A fourth shaft element J4 connecting the second gear 11 to the sun gear S2 of the second row of single pinion planetary gears G2;
Carrier P of single pinion planetary gear G2 in row
C2 and the third row single pinion planetary gear G
And a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2. A first friction brake element B1 for selectively fixing the first shaft element J1; and a ring gear R of the fourth row of single pinion planetary gears G4.
Friction brake element B for selectively locking
2 and the first row of double pinion planetary gears G1
And a third friction brake element B3 for selectively fixing the carrier PC1. Is constituted.

The third technical means taken to solve the above technical problem is as follows: "The input shaft 11, the output shaft 12, and the input shaft 11 are always connected to each other. , A first row of double pinion planetary gears G1, a second row of single pinion planetary gears G2, a third row of single pinion planetary gears G3, and a fourth row of single pinion planetary gears G
4 and the first row of double pinion planetary gears G1
A first shaft element J1 connecting the ring gear R1 of the second row to the ring gear R2 of the second row of single pinion planetary gears G2 and the sun gear S3 of the third row of single pinion planetary gears G3; and the fourth row of single pinion planetary gears G4. Carrier PC4 of the second row of single pinion planetary gears G2.
2 and the third row of single pinion planetary gears G
A second shaft element J2 connecting the third carrier PC3 to the third carrier PC3;
A third shaft element J3 connecting the sun gear S4 of the fourth row single pinion planetary gear G4 and the ring gear R3 of the third row single pinion planetary gear G3 to the output shaft 12, an input shaft 11 and the second row. A fourth shaft element J4 connecting the sun gear S2 of the single pinion planetary gear G2, the ring gear R2 of the second row single pinion planetary gear G2, and the sun gear S3 of the third row single pinion planetary gear G3.
Friction clutch element C for selectively coupling
1, a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a first frictional clutch element C2 for selectively fixing the first shaft element J1. The second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4 and the sun gear S1 of the first row of double pinion planetary gears G1 are selected. And a third friction brake element B3 for temporarily fixing. Is constituted.

The fourth technical means taken to solve the above-mentioned technical problem is that the input shaft 11, the output shaft 12, and the input shaft 11 are always connected. A first row of double pinion planetary gears G1, a second row of single pinion planetary gears G2, a third row of single pinion planetary gears G3, a fourth row of single pinion planetary gears G4, and a fourth row of single pinion planetary gears G4. The ring gear R of the second row of single pinion planetary gears G2 interconnected with the ring gear R1 of the double pinion planetary gear G1
2 and the third row of single pinion planetary gears G
A first shaft element J1 connecting the third row of sun gears S3 to the third row of single pinion planetary gears G4; and a second row of single pinion planetary gears G2 to the carrier PC2 and the third row of single pinion planetary gears. A second shaft element J2 connecting the carrier PC3 of G3, a sun gear S4 of the fourth row single pinion planetary gear G4, and a ring gear R3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. A third shaft element J3, an input shaft 11, and the second row of single pinion planetary gears G;
A fourth shaft element J4 for connecting the second sun gear S2 to the carrier PC2 of the second row of single pinion planetary gears G2 and the third row of single pinion planetary gears G3 for selectively connecting the carrier PC3. A first friction clutch element C1, a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a selective connection of the first shaft element J1. A first friction brake element B1 for fixing, a second friction brake element B2 for selectively fixing the ring gear R4 of the single pinion planetary gear G4 in the fourth row, and a double pinion planetary gear in the first row. And a third friction brake element B3 for selectively fixing the sun gear S1 of G1. Is constituted.

A fifth technical means taken to solve the above technical problem is that the input shaft 11, the output shaft 12, and the input shaft 11 are always connected to each other. Ring gear R3 and carrier respectively connected to the first row of double pinion planetary gears G1, the second row of single pinion planetary gears G2, and the second row of single pinion planetary gears G2 having the carrier PC2 and the ring gear R2, respectively. PC3, a third row of single pinion planetary gears G3, a fourth row of single pinion planetary gears G4, a ring gear R1 of the first row of double pinion planetary gears G1, and a second row of single pinion planetary gears G
A first shaft element J1 connecting the second sun gear S2 to the carrier PC4 of the fourth row of single pinion planetary gears G4; a carrier PC2 of the second row of single pinion planetary gears G2; and the third row of single pinion planetary gears G3. A second shaft element J2 for connecting the ring gear R3 of the third row, the sun gear S4 of the fourth row of single pinion planetary gears G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the third row of single pinion planetary gears. A third shaft element J3 connecting the carrier PC3 of G3 to the output shaft 12, a fourth shaft element J4 connecting the sun gear S3 of the third row of single-pinion planetary gears G3,
A first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4, and a first friction clutch element C1 for selectively connecting the input shaft 11 and the second shaft element J2. The second friction clutch element C2, the first friction brake element B1 for selectively fixing the first shaft element J1, and the ring gear R4 of the fourth row of single pinion planetary gears G4. A transmission having a second friction brake element B2 for fixing and a third friction brake element B3 for selectively fixing the carrier PC1 of the double-pinion planetary gear G1 in the first row. It is.

According to a sixth aspect of the present invention, there is provided a control apparatus comprising: an input shaft, an output shaft, and an input shaft which is always connected to the input shaft; Ring gear R3 and carrier respectively connected to the first row of double pinion planetary gears G1, the second row of single pinion planetary gears G2, and the second row of single pinion planetary gears G2 having the carrier PC2 and the ring gear R2, respectively. PC3, a third row of single pinion planetary gears G3, a fourth row of single pinion planetary gears G4, a ring gear R1 of the first row of double pinion planetary gears G1, and a second row of single pinion planetary gears G
A first shaft element J1 connecting the second sun gear S2 to the carrier PC4 of the fourth row of single pinion planetary gears G4; a carrier PC2 of the second row of single pinion planetary gears G2; and the third row of single pinion planetary gears G3. A second shaft element J2 for connecting the ring gear R3 of the third row, the sun gear S4 of the fourth row of single pinion planetary gears G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the third row of single pinion planetary gears. A third shaft element J3 connecting the carrier PC3 of G3 to the output shaft 12, a fourth shaft element J4 connecting the input shaft 11 and the sun gear S3 of the third row single pinion planetary gear G3, Carry of two-row single pinion planetary gear G2 A first friction clutch element C1 for selectively connecting PC2 and the ring gear R3 of the third row single pinion planetary gear G3, and a selective connection between the input shaft 11 and the second shaft element J2. A second friction clutch element C2, a first friction brake element B1 for selectively fixing the first shaft element J1, and a ring gear R4 of the fourth row of single pinion planetary gears G4. The second to secure
And a third friction brake element B3 for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1. Is constituted.

According to a seventh aspect of the present invention, there is provided a motor control apparatus comprising: an input shaft 11, an output shaft 12, and a constant connection with the input shaft 11. A first row of double pinion planetary gears G1, a second row of single pinion planetary gears G2, and a ring gear R3 and a carrier respectively connected to the second row of single pinion planetary gears G2, the carrier PC2 and the ring gear R2. A third row single pinion planetary gear G3 including PC3,
A fourth row of single pinion planetary gears G4, a first shaft element J1 connecting the ring gear R1 of the first row of double pinion planetary gears G1 and the second row of single pinion planetary gears G2 sun gear S2, and the fourth row. A second shaft element J2 connecting the carrier PC4 of the single pinion planetary gear G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3; and the fourth row. A third shaft element J3 for connecting the sun gear S4 of the single pinion planetary gear G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the carrier PC3 of the third row of single pinion planetary gears G3 to the output shaft 12; The said The fourth shaft element connecting the sun gear S3 of the row single-pinion planetary gear G3 of J4
And a first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4, and selectively connecting the input shaft 11 and the second shaft element J2. A second friction clutch element C2, a first friction brake element B1 for selectively fixing the first shaft element J1, and a ring gear R4 of the fourth row of single pinion planetary gears G4. And a third friction brake element B3 for selectively fixing the sun gear S1 of the double pinion planetary gear G1 in the first row. Is constituted.

According to an eighth aspect of the present invention, an input shaft 11, an output shaft 12, and the input shaft 11 are always connected to each other. A first row of double pinion planetary gears G1, a second row of single pinion planetary gears G2, and a ring gear R3 and a carrier respectively connected to the second row of single pinion planetary gears G2, the carrier PC2 and the ring gear R2. A third row single pinion planetary gear G3 including PC3,
A fourth row of single pinion planetary gears G4, a first shaft element J1 connecting the ring gear R1 of the first row of double pinion planetary gears G1 and the second row of single pinion planetary gears G2 sun gear S2, and the fourth row. A second shaft element J2 connecting the carrier PC4 of the single pinion planetary gear G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3; and the fourth row. A third shaft element J3 for connecting the sun gear S4 of the single pinion planetary gear G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the carrier PC3 of the third row of single pinion planetary gears G3 to the output shaft 12; , Input shaft 1 and a fourth shaft element J4 connecting the sun gear S3 of the third row single pinion planetary gear G3, the carrier PC2 of the second row single pinion planetary gear G2, and the ring gear of the third row single pinion planetary gear G3. A first friction clutch element C1 for selectively connecting R3 and a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2; A first friction brake element B1 for selectively fixing the first shaft element J1, and a second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4. And a third friction brake element for selectively fixing the sun gear S1 of the first row of double pinion planetary gears G1. 3 and transmission device comprising a. Is constituted.

According to a ninth technical means taken to solve the above technical problem, as described in claim 9, the input shaft 11, the output shaft 12, and the input shaft 11 are always connected. Ring gear R3 and carrier respectively connected to the first row of double pinion planetary gears G1, the second row of single pinion planetary gears G2, and the second row of single pinion planetary gears G2 having the carrier PC2 and the ring gear R2, respectively. PC3, a third row of single pinion planetary gears G3, a fourth row of single pinion planetary gears G4, a ring gear R1 of the first row of double pinion planetary gears G1, and a second row of single pinion planetary gears G
A second shaft element J1 connecting the second sun gear S2 to a carrier PC2 of the second row single pinion planetary gear G2 and a ring gear R3 of the third row single pinion planetary gear G3.
2 and the second row of single pinion planetary gears G
2 ring gear R2, the carrier PC3 of the third row single pinion planetary gear G3, and the carrier PC4 of the fourth row single pinion planetary gear G4.
Is connected to the output shaft 12, a third shaft element J3, a sun gear S3 of the third row of single pinion planetary gears G3, and a fourth shaft element of a sun gear S4 of the fourth row of single pinion planetary gears G4. J4,
A first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4, and a first friction clutch element C1 for selectively connecting the input shaft 11 and the second shaft element J2. The second friction clutch element C2, the first friction brake element B1 for selectively fixing the first shaft element J1, and the ring gear R4 of the fourth row of single pinion planetary gears G4. A transmission device comprising: a second friction brake element B2 for fixing; and a third friction brake element B3 for selectively fixing the carrier PC1 of the double row planetary gear G1 in the first row. Is constituted.

A tenth technical measure taken to solve the above technical problem is as described in claim 10,
"A first row of double pinion planetary gears G1 including an input shaft 11, an output shaft 12, and a carrier PC1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, and a second row of single pinion planetary gears G2. Carrier PC2 and ring gear R of pinion planetary gear G2
2 and ring gear R3 and carrier PC3 respectively connected to
Third row single pinion planetary gear G3 comprising
And a fourth row single pinion planetary gear G4,
A first shaft element J1 connecting the ring gear R1 of the first row of double pinion planetary gears G1 and the second row of single pinion planetary gears G2 and sun gear S2;
And the second row of single pinion planetary gears G2
, A second shaft element J2 connecting the carrier PC2 of the third row and the ring gear R3 of the third row of single pinion planetary gears G3, the carrier PC4 of the fourth row of single pinion planetary gears G4, and the second row of single pinion planetary gears G2. Ring gear R2 and the third shaft element J3 for connecting the carrier PC3 of the third row of single pinion planetary gears G3 to the output shaft 12.
And the fourth row of single pinion planetary gears G4
A fourth frictional element C1 for selectively coupling the input shaft 11 and the fourth frictional element J4; a fourth shaft element J4 for coupling the sun gear S4 to the input shaft 11;
A second friction clutch element C2 for selectively connecting the first shaft element J1 to the second shaft element J2; and the first shaft element J1.
Friction brake element B1 for selectively fixing
And the fourth row of single pinion planetary gears G4
A second friction brake element B2 for selectively fixing the ring gear R4 of the first row, and a third friction brake element B3 for selectively fixing the sun gear S1 of the double pinion planetary gear G1 in the first row. Transmission ".

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the accompanying drawings. In this specific example, a case where the present invention is used for an automatic transmission for an automobile will be described.

FIG. 1 is a schematic view showing a gear train of an automatic transmission according to a first embodiment of the present invention.

The automatic transmission is disposed in the housing 1 and outputs an output from a torque converter 2 which outputs an output to a transmission via a shear force of a viscous medium by an engine (not shown) in response to switching of a friction engagement element. 6 forward speeds, 1 reverse
The speed is increased / decreased and output to an axle (not shown).

The transmission includes an input shaft 11, which is an output shaft of the torque converter 2, an output shaft 12, which is connected to an axle via a differential (not shown), and a sun gear S1, which is always connected to the input shaft 11. The first row of double pinion planetary gears G1, the second row of single pinion planetary gears G2, the third row of single pinion planetary gears G3, the fourth row of single pinion planetary gears G4, and the first row of double pinion planetary gears G1 A first shaft element J1 connecting the ring gear R1 of the second row to the ring gear R2 of the second row of single pinion planetary gears G2 and the sun gear S3 of the third row of single pinion planetary gears G3; and the fourth row of single pinion planetary gears G4. Carrier PC4 of the second row The second shaft element for connecting the carrier PC3 ON planetary carrier PC2 and the third column of Li gear G2 of the single pinion planetary gear G3 J2
And the fourth row of single pinion planetary gears G4
A third shaft element J3 for connecting the sun gear S4 of the third row and the ring gear R3 of the third row of single pinion planetary gears G3 to the output shaft 12, an input shaft 11 and a sun gear S2 of the second row of single pinion planetary gears G2. And a first friction clutch for selectively connecting a ring gear G2 of the second row of single-pinion planetary gears G2 and a sun gear S3 of the third row of single-pinion planetary gears G3. A second friction clutch element C2 for selectively connecting the element C1 to the input shaft 11 and the second shaft element J2.
A first friction brake element B1 for selectively fixing the first shaft element J1, and a second friction for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4. Brake element B2 and carrier P of double pinion planetary gear G1 in the first row
And a third friction brake element B3 for selectively fixing C1.

Thus, each of the friction engagement elements (C1, C2B
1, B2, B3) are engaged / disengaged (disengaged) according to the supplied hydraulic pressure. Also, the first
In the planetary gear G1, ρ1 = the number of teeth of the sun gear S1 / the number of teeth of the ring gear R1 = 0.556, in the second planetary gear G2, ρ2 = the number of teeth of the sun gear S2 / the number of teeth of the ring gear R2 = 0.44, and in the third planetary gear G3, ρ3. = Number of teeth of sun gear S3 / number of teeth of ring gear R3 = 0.46;
In the fourth planetary gear G4, ρ4 = the number of teeth of the sun gear S4 / the number of teeth of the ring gear R4 = 0.34.

The table of FIG. 2 shows the friction engagement elements (C1, C2, B1, B2, B3) and the gear ratios in the first specific example. In the table, ○ indicates an engaged state, and a blank indicates a released (disengaged) state. Then, by engaging / disengaging each of the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 2, a sixth forward speed and a first reverse speed can be formed.

[Specific Example 2] As shown in FIG.
The first transmission has a first row double pinion planetary gear G1 including an input shaft 11, an output shaft 12, a sun gear S1 constantly connected to the input shaft 11, a second row single pinion planetary gear G2, and a third row. A single-pinion planetary gear G3 in a row, a single-pinion planetary gear G4 in a fourth row, and a ring gear R2 in the second row of single-pinion planetary gears G2 interconnected with a ring gear R1 in the double-pinion planetary gear G1 in the first row; The first shaft element J1 connecting the sun gear S3 of the third row single pinion planetary gear G3 and the carrier PC4 of the fourth row single pinion planetary gear G4 are replaced with the carrier PC2 of the second row single pinion planetary gear G2 and the carrier PC2. 3rd row single pinio The carrier PC of the planetary gear G3
A third shaft element J2 connecting the third shaft 3 to the output shaft 12; a sun gear S4 of the fourth row single pinion planetary gear G4; and a ring gear R3 of the third row single pinion planetary gear G3. Shaft element J
3, a fourth shaft element J4 connecting the input shaft 11 and the sun gear S2 of the second row of single pinion planetary gears G2, a carrier PC2 of the second row of single pinion planetary gears G2 and the third row of single pinion planetary gears G2. A first friction clutch element C1 for selectively connecting the carrier PC3 of the pinion planetary gear G3, and a second friction clutch for selectively connecting the input shaft 11 and the second shaft element J2. An element C2, a first friction brake element B1 for selectively fixing the first shaft element J1, and a second frictional element for selectively fixing the ring gear R4 of the single-pinion planetary gear G4 in the fourth row. And the third friction for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1. Includes a brake element B3, the.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 2, a forward speed 6 and a reverse 1 speed can be formed.

[Specific Example 3] As shown in FIG.
The first transmission has a first row of double pinion planetary gears G1 including an input shaft 11, an output shaft 12, and a carrier C1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, and a third row of single pinion planetary gears G2. A single-pinion planetary gear G3 in the row, a single-pinion planetary gear G4 in the fourth row, a ring gear R1 of the double-pinion planetary gear G1 in the first row, a ring gear R2 of the single-pinion planetary gear G2 in the second row, and a single-pin gear in the third row. The first shaft element J1 connecting the sun gear S3 of the pinion planetary gear G3 and the carrier PC4 of the fourth row of single pinion planetary gears G4 are replaced with the carrier PC2 of the second row of single pinion planetary gears G2 and the third row of single carriers. Pinion planetary gear The third shaft element J2 connecting the third carrier PC3, the sun gear S4 of the fourth row single pinion planetary gear G4, and the ring gear R3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. Third axis element J3 and input shaft 11
A fourth shaft element J4 connecting the second row of single-pinion planetary gears G2 to the sun gear S2 of the second row of single-pinion planetary gears G2; a ring gear R2 of the second row of single-pinion planetary gears G2; and a sun gear S3 of the third row of single-pinion planetary gears G3. And a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2. A first friction brake element B1 for selectively fixing one shaft element J1, and a ring gear R of the fourth row of single pinion planetary gears G4.
Friction brake element B for selectively locking
2 and the first row of double pinion planetary gears G1
And a third friction brake element B3 for selectively fixing the sun gear S1.

By engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 2, a forward speed 6 and a reverse 1 speed can be formed.

[Specific Example 4] As shown in FIG.
The first transmission includes an input shaft 11, an output shaft 12, and a carrier PC11 which is always connected to the input shaft 11.
The row double-pinion planetary gear G1, the second row single-pinion planetary gear G2, the third row single-pinion planetary gear G3, the fourth row single-pinion planetary gear G4, and the ring gear R1 of the first row double-pinion planetary gear G1. Second row single pinion planetary gears G interconnected with
The first shaft element J1 connecting the second ring gear R2 and the sun gear S3 of the third row single pinion planetary gear G3, and the carrier PC4 of the fourth row single pinion planetary gear G4 are connected to the second row single pinion planetary gear. A second shaft element J2 connecting the carrier PC2 of G2 and the carrier PC3 of the third row of single pinion planetary gears G3; the sun gear S4 of the fourth row of single pinion planetary gears G4; and the third row of single pinion planetary gears. A third shaft element J3 connecting the ring gear R3 of G3 to the output shaft 12, a fourth shaft element J4 connecting the input shaft 11 and the sun gear S2 of the single-pinion planetary gear G2 in the second row, Carriage of the second row single pinion planetary gear G2 A first friction clutch element C1 for selectively connecting the gear PC2 and a carrier PC3 of the third row single pinion planetary gear G3, and selectively connecting the input shaft 11 and the second shaft element J2. A second friction clutch element C2 for connection, a first friction brake element B1 for selectively fixing the first shaft element J1, and a ring gear R4 of the fourth row of single pinion planetary gears G4. It comprises a second friction brake element B2 for selectively fixing, and a third friction brake element B3 for selectively fixing the sun gear S1 of the double pinion planetary gear G1 in the first row.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 2, a sixth forward speed and a first reverse speed can be formed.

Fifth Embodiment A transmission of a fifth embodiment shown in FIG. 6 has a first row of double pinion planetary gears including an input shaft 11, an output shaft 12, and a sun gear S1 constantly connected to the input shaft 11. G1, a second row of single pinion planetary gears G2, and a ring gear R3 and a carrier PC connected respectively to the carrier PC2 and ring gear R2 of the second row of single pinion planetary gears G2.
3rd row single pinion planetary gear G with gear 3
3 and the fourth row of single pinion planetary gears G4
And a first shaft element J connecting the ring gear R1 of the first row of double pinion planetary gears G1 and the second row of single pinion planetary gears G2 and the sun gear S2.
1 and the fourth row of single pinion planetary gears G
No. 4 carrier PC4, a second shaft element J2 connecting the carrier PC2 of the second row single pinion planetary gear G2 and the ring gear R3 of the third row single pinion planetary gear G3, and the fourth row of single pinion planetary gears. G4 sun gear S4, the second
A third shaft element J3 connecting the ring gear R2 of the single-row planetary gear G2 in the row and the carrier PC3 of the single-pinion planetary gear G3 in the third row to the output shaft 12, and a sun gear of the single-pinion planetary gear G3 in the third row. And a first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4.
A second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a first frictional clutch element C2 for selectively fixing the first shaft element J1. Selectively the friction brake element B1, the second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4, and the carrier PC1 of the first row double pinion planetary gear G1. And a third friction brake element B3 for fixing to the

Thus, each friction engagement element (C1, C2B
1, B2, B3) are engaged / disengaged (disengaged) according to the supplied hydraulic pressure. Also, the first
In the planetary gear G1, ρ1 = number of teeth of the sun gear S1 / number of teeth of the ring gear R1 = 0.444, in the second planetary gear G2, ρ2 = number of teeth of the sun gear S2 / number of teeth of the ring gear R2 = 0.46, and in the third planetary gear G3, ρ3. = Number of teeth of sun gear S3 / number of teeth of ring gear R3 = 0.26;
In the fourth planetary gear G4, ρ4 = the number of teeth of the sun gear S4 / the number of teeth of the ring gear R4 = 0.3076.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, a forward 6th speed and a reverse 1st speed can be formed.

[Embodiment 6] A transmission according to embodiment 6 shown in FIG. 8 includes an input shaft 11, an output shaft 12,
1, a first row of double pinion planetary gears G1 having a sun gear S1 constantly connected to the first row, a second row of single pinion planetary gears G2, and a carrier PC2 and a ring gear R2 of the second row of single pinion planetary gears G2, respectively. A third row single pinion planetary gear G3 including a ring gear R3 and a carrier PC3, and a fourth row single pinion planetary gear G
4 and the first row of double pinion planetary gears G1
The first shaft element J1 connecting the ring gear R1 of the second row and the second row of single pinion planetary gears G2 and the sun gear S2, and the carrier PC4 of the fourth row of single pinion planetary gears G4 are connected to the second row of single pinion planetary gears G2. The carrier PC2 and the ring gear R3 of the third row single pinion planetary gear G3
, A sun gear S4 of the fourth row of single pinion planetary gears G4, a ring gear R2 of the second row of single pinion planetary gears G2, and a carrier of the third row of single pinion planetary gears G3. A third shaft element J3 for connecting PC3 to the output shaft 12, a fourth shaft element J4 for connecting the input shaft 11 and the sun gear S3 of the single-pinion planetary gear G3 in the third row, The carrier PC2 of the single pinion planetary gear G2 and the ring gear R3 of the third row single pinion planetary gear G3
Friction clutch element C for selectively coupling
1, a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a first frictional clutch element C2 for selectively fixing the first shaft element J1. The first friction brake element B1, the second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4, and the carrier PC1 of the first row double pinion planetary gear G1 are selected. And a third friction brake element B3 for temporarily fixing.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, a sixth forward speed and a first reverse speed can be formed.

[Embodiment 7] A transmission according to embodiment 7 shown in FIG. 9 includes an input shaft 11, an output shaft 12,
1, a first row of double pinion planetary gears G1 having a carrier PC1 constantly connected thereto, a second row of single pinion planetary gears G2, and a carrier PC2 and a ring gear R2 of the second row of single pinion planetary gears G2, respectively. A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3, a fourth row of single pinion planetary gears G4, and the first row of double pinion planetary gears G
The first shaft element J1 connecting the first ring gear R1 to the second row of single pinion planetary gears G2 and the sun gear S2, and the carrier PC4 of the fourth row of single pinion planetary gears G4 to the second row of single pinion planetary gears G2. And the ring gear R of the third row of single pinion planetary gears G3
3, the second shaft element J2, the sun gear S4 of the fourth row of single pinion planetary gears G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the third row of single pinion planetary gears G3. A third shaft element J3 connecting the carrier PC3 to the output shaft 12, a fourth shaft element J4 connecting the sun gear S3 of the third row of single pinion planetary gears G3, the input shaft 11 and the fourth shaft element. Axis element J4
Friction clutch element C for selectively coupling
1, a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a first frictional clutch element C2 for selectively fixing the first shaft element J1. The second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4 and the sun gear S1 of the first row of double pinion planetary gears G1 are selected. And a third friction brake element B3 for temporarily fixing.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, it is possible to form the forward 6th speed and the 1st reverse speed. Example 8] As shown in FIG. 10, the transmission according to Example 8 includes an input shaft 11, an output shaft 12, and the input shaft 1
1, a first row of double pinion planetary gears G1 having a carrier PC1 constantly connected thereto, a second row of single pinion planetary gears G2, and a carrier PC2 and a ring gear R2 of the second row of single pinion planetary gears G2, respectively. A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3, a fourth row of single pinion planetary gears G4, and the first row of double pinion planetary gears G
The first shaft element J1 connecting the first ring gear R1 to the second row of single pinion planetary gears G2 and the sun gear S2, and the carrier PC4 of the fourth row of single pinion planetary gears G4 to the second row of single pinion planetary gears G2. And the ring gear R of the third row of single pinion planetary gears G3
3, the second shaft element J2, the sun gear S4 of the fourth row of single pinion planetary gears G4, the ring gear R2 of the second row of single pinion planetary gears G2, and the third row of single pinion planetary gears G3. A third shaft element J3 connecting the carrier PC3 to the output shaft 12, a fourth shaft element J4 connecting the input shaft 11 and the sun gear S3 of the single-pinion planetary gear G3 in the third row, and the second row. The carrier PC2 of the single pinion planetary gear G2 and the ring gear R of the third row single pinion planetary gear G3
A second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2;
A first friction brake element B1 for selectively fixing the first shaft element J1 and a second friction brake element for selectively fixing a ring gear R4 of the fourth row of single pinion planetary gears G4. B2 and a third friction brake element B3 for selectively fixing the sun gear S1 of the first row of double pinion planetary gears G1.

By engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, a forward 6th speed and a reverse 1st speed can be formed.

[Embodiment 9] As shown in FIG. 11, the transmission according to Embodiment 9 has an input shaft 11, an output shaft 12, and a first row including a sun gear S1 constantly connected to the input shaft 11. , A second row of single pinion planetary gears G2, and a carrier PC2 of the second row of single pinion planetary gears G2.
A third row single pinion planetary gear G3 including a ring gear R3 and a carrier PC3 respectively connected to the ring gear R2, a fourth row single pinion planetary gear G4, the ring gear R1 of the first row double pinion planetary gear G1, and the second row. A first shaft element J1 connecting two rows of single pinion planetary gears G2 and a sun gear S2 is connected to a carrier PC2 of the second row of single pinion planetary gears G2 and a ring gear R3 of the third row of single pinion planetary gears G3. A second shaft element J2; a ring gear R2 of the second row of single pinion planetary gears G2;
Carrier P of single pinion planetary gear G3 in row
C3 and a third connecting the carrier PC4 of the fourth row of single pinion planetary gears G4 to the output shaft 12.
, A fourth shaft element J4 coupled to the sun gear S3 of the third row single pinion planetary gear G3 and the sun gear S4 of the fourth row single pinion planetary gear G4, the input shaft 11 and the A first friction clutch element C1 for selectively connecting the fourth shaft element J4 and a second friction clutch element for selectively connecting the input shaft 11 and the second shaft element J2. C2
A first friction brake element B1 for selectively fixing the first shaft element J1, and a second friction for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4. Brake element B2 and carrier P of double pinion planetary gear G1 in the first row
A third friction brake element B3 for selectively fixing C1.

By engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, a forward speed of 6 and a reverse speed of 1 can be formed. FIG. 12 is a modification of the transmission according to the ninth embodiment.

[Tenth Embodiment] As shown in FIG. 13, a transmission according to a tenth embodiment includes an input shaft 11 and an output shaft 12.
A first row double pinion planetary gear G1 including a carrier PC1 constantly connected to the input shaft 11,
A third row of single pinion planetary gears G3, including a second row of single pinion planetary gears G2, a third row of single pinion planetary gears G3, and a third row of single pinion planetary gears G3 comprising a carrier PC2 and a ring gear R2 of the second row of single pinion planetary gears G2; A first pinion planetary gear G4, a first shaft element J1 connecting the ring gear R1 of the first row of double pinion planetary gears G1 and the second row of single pinion planetary gears G2 sun gear S2, and a second row of single pinions. The carrier PC2 of the planetary gear G2 and the third
A second shaft element J2 connecting the ring gear R3 of the single pinion planetary gear G3 in the row, and a carrier PC4 of the single pinion planetary gear G4 in the fourth row;
A third shaft element J3 connecting the ring gear R2 of the second row of single pinion planetary gears G2 and the carrier PC3 of the third row of single pinion planetary gears G3 to the output shaft 12, and the fourth row of single pinion planetary gears; A fourth shaft element J4 connecting the sun gear S4 of the G4 to the input shaft 11 and the fourth shaft element J;
And a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2, and a second friction clutch element C2 for selectively connecting the input shaft 11 and the second shaft element J2.
A first friction brake element B1 for selectively fixing the first shaft element J1 and a second friction brake element for selectively fixing a ring gear R4 of the fourth row of single pinion planetary gears G4. B2 and a third friction brake element B3 for selectively fixing the sun gear S1 of the first row of double pinion planetary gears G1.

Then, by engaging / disengaging the friction engagement elements (C1, C2, B1, B2, B3) shown in FIG. 7, a forward speed 6 and a reverse 1 speed can be formed. FIG. 14 is a modified example of the transmission according to the tenth example.

Although the embodiments of the present invention have been described above, the present invention is not intended to be limited to the above-described embodiments.
Any method / apparatus may be used as long as the method / apparatus conforms to the gist of the present invention.

[0042]

As described above, in the transmission according to the present invention, by appropriately controlling the planetary gear mechanism by using two friction clutch elements and three friction brake elements, the transmission in the axial direction of the transmission can be realized. Is shorter than in the prior art (three friction clutch elements and two friction brake elements are used) to obtain six forward speeds and one reverse speed.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a transmission according to a first embodiment of the present invention.

FIG. 2 is a table showing switching means operating at each shift speed in the transmission of FIG. 1;

FIG. 3 is a schematic diagram of a transmission according to a second embodiment of the present invention.

FIG. 4 is a schematic diagram of a transmission according to a third embodiment of the present invention.

FIG. 5 is a schematic diagram of a transmission according to a fourth embodiment of the present invention.

FIG. 6 is a schematic diagram of a transmission according to a fifth embodiment of the present invention.

FIG. 7 is a table showing switching means operating at each shift speed in the transmission of FIG. 6;

FIG. 8 is a schematic diagram of a transmission according to a sixth embodiment of the present invention.

FIG. 9 is a schematic diagram of a transmission according to a seventh embodiment of the present invention.

FIG. 10 is a schematic diagram of a transmission according to an eighth embodiment of the present invention.

FIG. 11 is a schematic view of a transmission according to a ninth embodiment of the present invention.

FIG. 12 is a schematic view of a transmission according to a modification of the transmission of FIG. 11;

FIG. 13 is a schematic view of a transmission according to a tenth embodiment of the present invention.

FIG. 14 is a schematic diagram of a transmission according to a modification of the transmission of FIG. 13;

[Explanation of symbols]

 : Torque converter: Input shaft: Output shaft G1: Double row pinion planetary gear in the first row G2: Single planetary gear in the second row G3: Single planetary gear in the third row S1, S2, S3: Sun gear R1, R2, R3: Ring gear PC1, PC2, PC3: Carrier C1, C2: Friction clutch element B1, B2, B3: Friction brake element J1, J2, J3, J4: Shaft element

Claims (10)

[Claims] An input shaft, an output shaft, a first row of double pinion planetary gears provided with a sun gear constantly connected to the input shaft, a second row of single pinion planetary gears; A single-pinion planetary gear G3 in a row, a single-pinion planetary gear G4 in a fourth row, a ring gear R1 of the double-pinion planetary gear G1 in the first row, a ring gear R2 in the single-pinion planetary gear G2 in the second row, and a single-ring in the third row. A first shaft element J1 connecting the sun gear S3 of the pinion planetary gear G3 to the carrier PC4 of the fourth row of single pinion planetary gears G4 and a carrier PC2 of the second row of single pinion planetary gears G2 and the third row of single Pinion planetarigi A second shaft element J2 connecting the carrier PC3 of the gear G3, a sun gear S4 of the fourth row of single-pinion planetary gears G4, and a ring gear R3 of the third row of single-pinion planetary gears G3 to the output shaft 12; A third shaft element J3 that connects the input shaft 11 and the sun gear S2 of the single-pinion planetary gear G2 in the second row.
A first friction clutch element C1 for selectively connecting the ring gear G2 of the second row of single pinion planetary gears G2 and the sun gear S3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4, and a third frictional element for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1. And a friction brake element B3. 2. An input shaft 11, an output shaft 12, a first row of double pinion planetary gears G1 including a sun gear S1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, A single-pinion planetary gear G3 in a row, a single-pinion planetary gear G4 in a fourth row, and a ring gear R2 of the second-row single-pinion planetary gear G2 interconnected with a ring gear R1 of the double-pinion planetary gear G1 in the first row; A first shaft element J1 connecting the third row of single pinion planetary gears G3 to the sun gear S3; a carrier PC4 of the fourth row of single pinion planetary gears G4; a carrier PC2 of the second row of single pinion planetary gears G2; Single row 3rd row A second shaft element J2 connecting the carrier PC3 of the on-planetary gear G3 to the output shaft 12, a sun gear S4 of the fourth row of single-pinion planetary gears G4, and a ring gear R3 of the third row of single-pinion planetary gears G3. A third shaft element J3 to be connected; a fourth shaft element J4 to connect the input shaft 11 and the sun gear S2 of the single-pinion planetary gear G2 in the second row.
A first friction clutch element C1 for selectively connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the carrier PC3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4, and a third frictional brake element B2 for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1. And a friction brake element B3. 3. A first row of double pinion planetary gears G1 including a carrier C1 constantly connected to the input shaft 11, an output shaft 12, and the input shaft 11, a second row of single pinion planetary gears G2, A single-pinion planetary gear G3 in a row, a single-pinion planetary gear G4 in a fourth row, a ring gear R1 of the double-pinion planetary gear G1 in the first row, a ring gear R2 in the single-pinion planetary gear G2 in the second row, and a single-ring in the third row. A first shaft element J1 connecting the sun gear S3 of the pinion planetary gear G3 to the carrier PC4 of the fourth row of single pinion planetary gears G4 and a carrier PC2 of the second row of single pinion planetary gears G2 and the third row of single Pinion planetarigi A second shaft element J2 connecting the carrier PC3 of the gear G3, a sun gear S4 of the fourth row of single-pinion planetary gears G4, and a ring gear R3 of the third row of single-pinion planetary gears G3 to the output shaft 12; A third shaft element J3 that connects the input shaft 11 and the sun gear S2 of the single-pinion planetary gear G2 in the second row.
A first friction clutch element C1 for selectively connecting the ring gear R2 of the second row of single pinion planetary gears G2 and the sun gear S3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4, and a third frictional element for selectively fixing the sun gear S1 of the first row double pinion planetary gear G1. And a friction brake element B3. 4. A first row of double pinion planetary gears G1 including an input shaft 11, an output shaft 12, a carrier PC11 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, and a third row of single pinion planetary gears G2. A single-pinion planetary gear G3 in a row, a single-pinion planetary gear G4 in a fourth row, and a ring gear R2 of the second-row single-pinion planetary gear G2 interconnected with a ring gear R1 of the double-pinion planetary gear G1 in the first row; A first shaft element J1 connecting the third row of single pinion planetary gears G3 to the sun gear S3; a carrier PC4 of the fourth row of single pinion planetary gears G4 and a carrier PC2 of the second row of single pinion planetary gears G2; 3rd row single A second shaft element J2 connecting the carrier PC3 of the pinion planetary gear G3 to the output shaft 12, a sun gear S4 of the fourth row single pinion planetary gear G4, and a ring gear R3 of the third row single pinion planetary gear G3. A third shaft element J3 to be connected; a fourth shaft element J4 to connect the input shaft 11 and the sun gear S2 of the single-pinion planetary gear G2 in the second row.
A first friction clutch element C1 for selectively connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the carrier PC3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4, and a third frictional element for selectively fixing the sun gear S1 of the first row double pinion planetary gear G1. And a friction brake element B3. 5. An input shaft 11, an output shaft 12, a first row of double pinion planetary gears G1 including a sun gear S1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 for connecting the carrier PC4 of the fourth row of single pinion planetary gears G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3. The sun gear S4 of the fourth row single pinion planetary gear G4, the ring gear R2 of the second row single pinion planetary gear G2, and the carrier PC3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. A third shaft element J3, a fourth shaft element J4 for connecting the sun gear S3 of the third row single pinion planetary gear G3, and a selective connection between the input shaft 11 and the fourth shaft element J4. Friction clutch element C1 for the input shaft 1 A second friction clutch element C2 for selectively coupling the first shaft element J1 to the second shaft element J2, and a first friction brake element B1 for selectively fixing the first shaft element J1. A second friction brake element B2 for selectively fixing a ring gear R4 of the fourth row single pinion planetary gear G4; and a second friction brake element B2 for selectively fixing a carrier PC1 of the first row double pinion planetary gear G1. And a friction brake element B3. 6. An input shaft 11, an output shaft 12, a first row of double pinion planetary gears G1 including a sun gear S1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 for connecting the carrier PC4 of the fourth row of single pinion planetary gears G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3. The sun gear S4 of the fourth row single pinion planetary gear G4, the ring gear R2 of the second row single pinion planetary gear G2, and the carrier PC3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. And a fourth shaft element J4 connecting the input shaft 11 and the sun gear S3 of the single-pinion planetary gear G3 in the third row.
A first friction clutch element C1 for selectively connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row of single pinion planetary gears G4, and a third frictional brake element B2 for selectively fixing the carrier PC1 of the first row of double pinion planetary gears G1. And a friction brake element B3. 7. An input shaft 11, an output shaft 12, a first row of double pinion planetary gears G1 including a carrier PC1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 for connecting the carrier PC4 of the fourth row of single pinion planetary gears G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3. The sun gear S4 of the fourth row single pinion planetary gear G4, the ring gear R2 of the second row single pinion planetary gear G2, and the carrier PC3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. A third shaft element J3, a fourth shaft element J4 for connecting the sun gear S3 of the third row single pinion planetary gear G3, and a selective connection between the input shaft 11 and the fourth shaft element J4. Friction clutch element C1 for the input shaft 1 A second friction clutch element C2 for selectively coupling the first shaft element J1 to the second shaft element J2, and a first friction brake element B1 for selectively fixing the first shaft element J1. A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4; and a second friction brake element B2 for selectively fixing the sun gear S1 of the first row double pinion planetary gear G1. And a friction brake element B3. 8. A first row of double pinion planetary gears G1 including a carrier PC1 constantly connected to the input shaft 11, an output shaft 12, and the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 for connecting the carrier PC4 of the fourth row of single pinion planetary gears G4 to the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G3. The sun gear S4 of the fourth row single pinion planetary gear G4, the ring gear R2 of the second row single pinion planetary gear G2, and the carrier PC3 of the third row single pinion planetary gear G3 are connected to the output shaft 12. And a fourth shaft element J4 connecting the input shaft 11 and the sun gear S3 of the single-pinion planetary gear G3 in the third row.
A first friction clutch element C1 for selectively connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G2; A second friction clutch element C2 for selectively connecting the second shaft element J2, a first friction brake element B1 for selectively fixing the first shaft element J1, A second friction brake element B2 for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4, and a third frictional element for selectively fixing the sun gear S1 of the first row double pinion planetary gear G1. A transmission device comprising: a friction brake element B3; 9. A first row of double pinion planetary gears G1 including an input shaft 11, an output shaft 12, a sun gear S1 constantly connected to the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G2; and a ring gear of the second row of single pinion planetary gears G2. R2, a third shaft element J3 connecting the carrier PC3 of the third row single pinion planetary gear G3 and the carrier PC4 of the fourth row single pinion planetary gear G4 to the output shaft 12; A fourth shaft element J4 connected to the sun gear S3 of the pinion planetary gear G3 and the sun gear S4 of the fourth row of single pinion planetary gears G4.
A first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4; and selectively connecting the input shaft 11 and the second shaft element J2. A second friction clutch element C2, a first friction brake element B1 for selectively fixing the first shaft element J1, and a ring gear R4 of the single pinion planetary gear G4 in the fourth row. And a third friction brake element B3 for selectively fixing a carrier PC1 of the first row of double pinion planetary gears G1. 10. A first row of double pinion planetary gears G1 including a carrier PC1 constantly connected to the input shaft 11, an output shaft 12, and the input shaft 11, a second row of single pinion planetary gears G2, A third row of single pinion planetary gears G3 including a ring gear R3 and a carrier PC3 respectively connected to the carrier PC2 and the ring gear R2 of the two rows of single pinion planetary gears G2; a fourth row of single pinion planetary gears G4; A first shaft element J1 connecting the ring gear R1 of the double pinion planetary gear G1 and the second row of single pinion planetary gears G2 sun gear S2.
A second shaft element J2 connecting the carrier PC2 of the second row of single pinion planetary gears G2 and the ring gear R3 of the third row of single pinion planetary gears G2; and a carrier of the fourth row of single pinion planetary gears G4. PC3, a third shaft element J3 for connecting the ring gear R2 of the third row single pinion planetary gear G2 and the carrier PC3 of the third row single pinion planetary gear G3 to the output shaft 12, and a fourth row single pinion A fourth shaft element J4 for connecting the sun gear S4 of the planetary gear G4, a first friction clutch element C1 for selectively connecting the input shaft 11 and the fourth shaft element J4, and the input shaft 11; Friction clutch for selectively connecting the second shaft element J2 and the second shaft element J2 Element C2, a first friction brake element B1 for selectively fixing the first shaft element J1, and a second frictional element for selectively fixing the ring gear R4 of the fourth row single pinion planetary gear G4. And a third friction brake element B3 for selectively fixing the sun gear S1 of the first row of double pinion planetary gears G1.