JP2000274497A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly set a gear ratio of retreat without increasing a pinion rotating speed by specifying a combination of five frictionally engaging elements by planetary gears of three rows. SOLUTION: At the first speed, torque of an input shaft 11 is transmitted to a shaft element J4 by engaging a clutch element C1, and an element J2 is fixed by a brake element B2 to decelerate an element J3. At the second speed, an element J1 is fixed by an element B1 by engaging an element C1 to decelerate the element J3. At the third speed, rotation of a ring gear R1 is locked by a fixation of an element B3 by engaging the element C1, and output of a carrier PC1 by increasing torque is transmitted to the element J1 to decelerate the element J3. At the fourth speed, torque is transmitted to the elements J1, 2 by engaging the elements C1, 2 to be integrally rotated together with the shaft 11. At the fifth speed, torque is transmitted to the element J2 by engaging the element C2, and the element B3 is fixed to increase a speed of the element J3. At the sixth speed, torque is transmitted to the element J2 by engaging the element C2, and the element J1 is fixed by the element B1 to increase a speed of the element J3. At the retreat, the element J1 is fixed by the elements B2, 3 to inversely rotate the element J3.

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 A conventional transmission is disclosed in, for example,
There is a technique disclosed in JP-A-323381. In this publication, three planetary gear units are arranged in series, and each planetary gear unit uses one ring gear, carrier, and sun gear. A transmission that can switch between six forward gears and one reverse gear through five engagement elements (two clutches and three brakes) driven by external force using these gears is disclosed. ing.

[0003]

However, if the transmission disclosed in the above publication is designed so that the pinion rotational speed does not increase when the shift speed is 5th or 6th, the reverse gear ratio increases. As a result, there is a problem that the degree of freedom in design is low.

In order to solve the above-mentioned problems, the present invention uses three rows of planetary gears and five frictional engagement elements to reduce the number of pinion revolutions when the shift speed is a high speed such as a fifth speed or a sixth speed. It is a technical object of the present invention to provide a six-speed forward transmission capable of appropriately designing the reverse gear ratio without increasing the gear ratio.

[0005]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a first aspect of the present invention is an input shaft, an output shaft, a first row of single pinion planetary gears in which a sun gear is connected to an input shaft, and a second row. And the third row of double pinion planetary gears and the third row of double pinion planetary gears are connected to the third row of double pinion planetary gear carriers and the second row of single pinion planetary gears. The first gear connected to the sun gear of the pinion planetary gear
, A second shaft element connected to the carrier of the third row of double pinion planetary gears, a third shaft element connected to the ring gear of the second row of single pinion planetary gears, and a third row of double A Ravigneaux-type gear unit having a fourth shaft element connected to a sun gear of a pinion planetary gear and connecting a third shaft element to an output shaft; and a sun gear and a Ravigneaux-type gear unit of a single-row single pinion planetary gear A first friction clutch element C1 for selectively coupling the fourth shaft element of
A second friction clutch element C2 for selectively connecting the sun gear of the single-pinion planetary gear in the first row and the second shaft element of the Ravigneaux-type gear unit; a first friction element and a second friction element of the Ravigneaux-type gear unit; A first friction brake element B1 for selectively fixing a carrier of a single row single pinion planetary gear, and a second friction brake element B1 for selectively fixing a second shaft element of a Ravigneaux type gear unit.
And a third friction brake element B3 for selectively fixing the ring gear of the single-pinion planetary gears in the first row.

According to the first aspect, the speed is set to the fifth speed or the sixth speed.
A forward six-speed and one-reverse one-speed transmission can be configured that can appropriately design the reverse gear ratio without increasing the pinion rotation speed at high speed.

In order to solve the above-mentioned problems, a second aspect of the invention is a ring gear of a first row of single pinion planetary gears in which an input shaft, an output shaft, and a sun gear are connected to an input shaft, and a second row of single pinion planetary gears. And the ring gear of the third row of double pinion planetary gears and the carrier of the second row of single pinion planetary gears and the carrier of the third row of double pinion planetary gears, and are connected to the sun gear of the second row of single pinion planetary gears. A first axial element to be
A second shaft element connected to the carrier of the double pinion planetary gears in the row, a third shaft element connected to the ring gear of the single pinion planetary gears in the second row, and a sun gear of the double pinion planetary gears in the third row. A Ravigneaux-type gear unit including a fourth shaft element, and a third shaft element connected to the output shaft, a sun gear of a single-row single-pinion planetary gear, and a fourth shaft element of a Ravigneaux-type gear unit. A first friction clutch element C1 for selectively connecting the second shaft element of the Ravigneaux-type gear unit and a sun gear of the single-pinion planetary gear in the first row.
Frictional clutch element C2, a third frictional clutch element C3 for selectively connecting the carrier of the single-row single pinion planetary gear and the first shaft element of the Ravigneaux gear unit, and a friction clutch element C2 of the Ravigneaux gear unit. A first friction brake element B1 for selectively fixing the first shaft element, and a second friction brake element B2 for selectively fixing the second shaft element of the Ravigneaux-type gear unit. Transmission equipped.

[0008] According to the second aspect, the gear position is set to the fifth speed or the sixth speed.
A forward six-speed and one-reverse one-speed transmission can be configured that can appropriately design the reverse gear ratio without increasing the pinion rotation speed at high speed. Claim 2
According to this, by providing the third friction clutch element C3, the torque of the input shaft can be separated from the Ravigneaux-type gear unit, and the high-speed rotation of the pinion gear in the Ravigneaux-type gear unit with no load can be suppressed. Thus, the gear noise can be reduced and the durability of the gear can be improved.

[0009]

Embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is used for an automatic transmission for an automobile will be described.

FIG. 1 is a schematic diagram showing a gear train of an automatic transmission 10 according to a first embodiment of the present invention.
The automatic transmission 10 is disposed in the housing 1, and outputs the output of the engine (not shown) to the transmission 10 through the shearing force of the viscous medium. The output from the torque converter 2 advances in accordance with the switching of the friction engagement element. The speed is switched between the sixth speed and the first reverse speed, and output to an axle not shown.

The transmission 10 has an input shaft 11 as an output shaft of the torque converter 2, an output shaft 12 connected to the axle via a differential (not shown), and a sun gear S1 connected to the input shaft 11. Single row single pinion planetary gear G1 (hereinafter, referred to as first planetary gear G1)
And the second row of single pinion planetary gears (hereinafter referred to as
A ring gear R2 of a second planetary gear G2) and a ring gear R3 of a third row of double pinion planetary gears (hereinafter referred to as a third planetary gear G3) are connected, and a carrier PC2 of the second planetary gear G2 and a carrier of the third planetary gear G3. PC3 and the first planetary gear G2 connected to the sun gear S2.
Shaft element J1 and the carrier P of the third planetary gear G3
A second shaft element J2 connected to C3 and a third shaft element J connected to the ring gear R2 of the second planetary gear G2.
3 and a Ravigneaux type gear unit G having a fourth shaft element J4 connected to the sun gear S3 of the third planetary gear G3 and connecting the third shaft element J3 to the output shaft 12.
23, a first friction clutch element C1 for selectively connecting the sun gear S1 of the first planetary gear G1 and the fourth shaft element J4 of the Ravigneaux type gear unit G23, and a sun gear S1 and a Ravigneaux gear of the first planetary gear G1. A second shaft for selectively connecting the second shaft element J2 of the unit G23;
Frictional clutch element C2 and Ravigneaux type gear unit G
23 first shaft element J1 and first planetary gear G1
A first friction brake element B1 for selectively fixing the carrier PC1, a second friction brake element B2 for selectively fixing the second shaft element J2 of the Ravigneaux type gear unit G23, and a first planetary gear G1. A third friction brake element B3 for selectively fixing the ring gear R1.

In the first planetary gear G1, ρ1 = the number of teeth of the sun gear S1 / the number of teeth of the ring gear R1 = 0.6, the second
In the planetary gear G2, ρ2 = the number of teeth of the sun gear S2 /
Number of teeth of ring gear R2 = 0.6, third planetary gear G
In No. 3, ρ3 = number of teeth of sun gear S3 / number of teeth of ring gear R3 = 0.3.

Table 1 shows combinations of engagement elements and gear ratios in the first embodiment.

[0014]

[Table 1]

In Table 1, 表 indicates an engaged state, and a blank indicates an open state.

A description will now be given of the switching of the shift speeds in Table 1. At the first speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux-type gear unit G23, and the second friction brake element B2 performs the Ravigneaux-type operation. By fixing the second shaft element J2 of the gear unit G23, the third shaft element J3 is rotated at a reduced speed to form the first speed.

In the second speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux-type gear unit G23, and to the first friction brake element B1. Ravigneaux gear unit G2
The third axis element J1 is fixed by fixing the third axis element J1.
3 is rotated at a reduced speed to form the second speed.

In the third speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux type gear unit G23, and the third friction brake element B3 is engaged. The rotation of the ring gear R1 of the first planetary gear G1 is locked by the fixation, and the output of the carrier PC1 in which the torque of the input shaft 11 is increased is transmitted to the first shaft element J1 of the Ravigneaux type gear unit G23. The shaft element J3 is rotated at a reduced speed to form the third speed.

At the fourth speed, the first friction clutch element C1 and the second friction clutch element C2 are engaged to apply the torque of the input shaft 11 to the first shaft element J1 and the second shaft element of the Ravigneaux type gear unit G23. The transmission to the element J2 causes the Ravigneaux type gear unit G23 to rotate integrally with the input shaft 11,
Form speed.

At the fifth speed, the second friction clutch element C2 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the Ravigneaux type gear unit G23, and the third friction brake element B3 is engaged. The rotation of the ring gear R1 of the first planetary gear G1 is locked by the fixation, and the output of the carrier PC1 in which the torque of the input shaft 11 is increased is transmitted to the first shaft element J1 of the Ravigneaux type gear unit G23. The shaft element J3 is rotated at an increased speed to form a fifth speed which is an overdrive.

At the sixth speed, the second friction clutch element C2 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the Ravigneaux-type gear unit G23, and to the first friction brake element B1. Ravigneaux gear unit G2
The third axis element J1 is fixed by fixing the third axis element J1.
3 is rotated at an increased speed to form a sixth speed which is an overdrive.

In reverse, the rotation of the ring gear R1 of the first planetary gear G1 is stopped by fixing the third friction brake element B3, and the torque of the input shaft 11 is increased by the first shaft element J1 of the Ravigneaux type gear unit G23. By transmitting the output of the carrier PC1 and fixing the first shaft element J1 with the second friction brake element B2, the third shaft element J3 of the Ravigneaux type gear unit G23 is rotated in the reverse direction, and To form

By switching the respective friction engagement elements as described above, the first to fourth gears are undershifted by three rows of planetary gears G1, G2, G3 and five friction engagement elements C1, C2, B1, B2, B3. The transmission 10 of the sixth forward speed and the first reverse speed in which the drive, the fifth speed and the sixth speed are overdrive can be constituted.

Next, a description will be given of a transmission 20 according to a second embodiment of the present invention. FIG. 2 is a schematic diagram showing a gear train of the automatic transmission 20 according to the second embodiment.

The transmission 20 of the second embodiment differs from the transmission 10 of the first embodiment in that the friction brake element B3 for selectively fixing the ring gear R1 of the first planetary gear G1 is eliminated. The ring gear R1 is always fixed to the housing 1, and the carrier PC1 of the first planetary gear G1 and the Ravigneaux-type gear unit G2
3 except that a third friction clutch element C3 for selectively connecting the first shaft element J1 to the third shaft element J1 is provided. The other configuration is the same, and therefore the description is omitted, and the same configuration is the same. Assign a sign.

Table 2 shows the combinations of the engagement elements and the gear ratios according to the second embodiment.

[0027]

[Table 2]

In Table 2, .largecircle. Indicates an engaged state, and a blank indicates an open state.

A description will now be given of the switching of the shift speed in Table 2. At the first speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux-type gear unit G23, and the second friction brake element B2 performs the Ravigneaux-type operation. By fixing the second shaft element J2 of the gear unit G23, the third shaft element J3 is rotated at a reduced speed to form the first speed.

In the second speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux-type gear unit G23, and to the first friction brake element B1. Ravigneaux gear unit G2
The third axis element J1 is fixed by fixing the third axis element J1.
3 is rotated at a reduced speed to form the second speed.

In the third speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the fourth shaft element J4 of the Ravigneaux type gear unit G23, and the third friction clutch element C3 is engaged. By transmitting the output of the carrier PC1 in which the torque of the input shaft 11 is increased to the first shaft element J1 of the Ravigneaux type gear unit G23 by the engagement, the third shaft element J1 becomes the third shaft element J1.
Is rotated at a reduced speed to form the third speed.

In the fourth speed, the first friction clutch element C1 and the second friction clutch element C2 are engaged to apply the torque of the input shaft 11 to the first shaft element J1 and the second shaft element of the Ravigneaux type gear unit G23. The transmission to the element J2 causes the Ravigneaux type gear unit G23 to rotate integrally with the input shaft 11,
Form speed.

In the fifth speed, the second friction clutch element C2 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the Ravigneaux type gear unit G23, and the third friction clutch element C3 is engaged. By transmitting the output of the carrier PC1 in which the torque of the input shaft 11 is increased to the first shaft element J1 of the Ravigneaux type gear unit G23 by the engagement, the third shaft element J1 becomes the third shaft element J1.
Of the shaft element J3 is rotated at an increased speed to form a fifth speed which is an overdrive.

At the sixth speed, the second friction clutch element C2 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the Ravigneaux-type gear unit G23, and to the first friction brake element B1. Ravigneaux gear unit G2
The third axis element J1 is fixed by fixing the third axis element J1.
3 is rotated at an increased speed to form a sixth speed which is an overdrive.

In reverse, the carrier PC in which the torque of the input shaft 11 is increased by the first shaft element J1 of the Ravigneaux type gear unit G23 by engagement of the third friction clutch element C3.
1 and the first shaft element J1 is fixed by the second friction brake element B2, whereby the third shaft element J3 of the Ravigneaux-type gear unit G23 is rotated in the reverse direction to form a reverse movement. .

By switching the respective friction engagement elements as described above, the first to fourth gears are undershifted by three rows of planetary gears G1, G2, G3 and five friction engagement elements C1, C2, C0, B1, B2. The transmission 20 of the forward 6th speed and the 1st reverse speed of the overdrive can be constituted by the drive, the 5th speed and the 6th speed.

Further, by using the third friction clutch element C3, it is possible to separate the carrier PC1 from the first shaft element J1 when no load is applied to the first shaft element J1. High-speed no-load rotation of the pinion gear in the gear unit G23 can be suppressed. Thus, gear noise can be reduced and the durability of the gear can be improved.

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, and any form of transmission that conforms to the gist of the present invention can be used. It may be.

[0039]

According to the first aspect of the present invention, it is possible to appropriately design the reverse gear ratio without increasing the pinion rotational speed when the shift speed is the fifth speed or the sixth speed, and the forward six speed and the reverse first speed can be designed. A stepped transmission can be configured.

According to the second aspect, the shift speed is set to the fifth speed or the sixth speed.
A forward six-speed and one-reverse one-speed transmission can be configured that can appropriately design the reverse gear ratio without increasing the pinion rotation speed at high speed. Claim 2
According to this, by providing the third friction clutch element C3, the torque of the input shaft can be separated from the Ravigneaux-type gear unit, and the high-speed rotation of the pinion gear in the Ravigneaux-type gear unit with no load can be suppressed. Thus, the gear noise can be reduced and the durability of the gear can be improved.

[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 schematic diagram of a transmission according to a second embodiment of the present invention.

[Description of Signs] 1 ... Housing 2 ... Torque converter 10, 20 ... Transmission device 11 ... Input shaft 12 ... Output shaft G1 ... First row single pinion planetary gear G2 ...・ Second row single pinion planetary gear G3 ・ ・ ・ Third row double pinion planetary gear G23 ・ ・ ・ Ravigneaux type gear unit S1, S2, S3 ・ ・ ・ Sun gear R1, R2, R3 ・ ・ ・ Ring gear PC1, PC2, PC3 ... Carrier C0, C1, C2 ... Friction clutch element B1, B2, B3 ... Friction brake element J1, J2, J3, J4 ... Shaft element

Claims (2)

[Claims] An input shaft, an output shaft, a first row of single pinion planetary gears having a sun gear connected to the input shaft, a second row of single pinion planetary gear ring gears, and a third row of double pinion planetary gear ring gears. And a first shaft element connected to a carrier of the second row of single pinion planetary gears and a carrier of the third row of double pinion planetary gears, and connected to a sun gear of the second row of single pinion planetary gears. A second shaft element connected to the carrier of the third row of double pinion planetary gears, a third shaft element connected to the ring gear of the second row of single pinion planetary gears, and the third row of double pinions A fourth shaft element connected to a sun gear of the planetary gear; And a Ravigneaux type gear unit in which the third shaft element is connected to the output shaft; and a sun gear of the first row single pinion planetary gear and the fourth shaft element of the Ravigneaux gear unit are selectively connected. Friction clutch element C1 for
And a second friction clutch element C2 for selectively connecting the sun gear of the first row single pinion planetary gear and the second shaft element of the Ravigneaux type gear unit.
A first friction brake element B for selectively fixing the first shaft element of the Ravigneaux type gear unit and the carrier of the first row of single pinion planetary gears;
1, a second friction brake element B2 for selectively fixing the second shaft element of the Ravigneaux type gear unit, and a second friction brake element B2 for selectively fixing the ring gear of the first row of single pinion planetary gears. And a third friction brake element B3. 2. An input shaft, an output shaft, a first row of single pinion planetary gears having a sun gear connected to the input shaft, a second row of single pinion planetary gear ring gears, and a third row of double pinion planetary gear ring gears. And a first shaft element connected to a carrier of the second row of single pinion planetary gears and a carrier of the third row of double pinion planetary gears, and connected to a sun gear of the second row of single pinion planetary gears. A second shaft element connected to the carrier of the third row of double pinion planetary gears, a third shaft element connected to the ring gear of the second row of single pinion planetary gears, and the third row of double pinions A fourth shaft element connected to a sun gear of the planetary gear; A Ravigneaux type gear unit in which the third shaft element is connected to the output shaft, and a sun gear of the first row single pinion planetary gear and the fourth shaft element of the Ravigneaux type gear unit are selectively connected. Friction clutch element C1 for
And a second friction clutch element C2 for selectively connecting the sun gear of the first row single pinion planetary gear and the second shaft element of the Ravigneaux type gear unit.
A third friction clutch element C3 for selectively connecting the carrier of the first row of single pinion planetary gears and the first shaft element of the Ravigneaux type gear unit;
A first friction brake element B1 for selectively fixing the first shaft element of the Ravigneaux gear unit; and a first friction brake element B1 for selectively fixing the second shaft element of the Ravigneaux gear unit. And a second friction brake element B2.