JP4423780B2 - Transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a transmission, for example, a transmission used for an automatic transmission of an automobile.
[0002]
[Prior art]
A conventional transmission is described in Japanese Patent Publication No. 2-149562. The transmission disclosed in this publication has three planetary gears arranged in series, and each planetary gear includes one ring gear, a carrier, and a sun gear. This transmission can use gears to switch between five forward gears and one reverse gear through five frictional engagement elements driven by external force.
[0003]
[Problems to be solved by the invention]
However, in this transmission, the sun gear of the planetary gear in the first row is always connected to the input shaft, so that the pinion gear rotates at high speed without load, particularly at the first speed of forward movement. There is a problem that the gear noise generated at the meshing portion increases. Moreover, it is not preferable also from the surface of the durability of a gear by rotating without load.
[0004]
Therefore, it is a technical object of the present invention to provide a transmission that can switch between six forward gears and one reverse gear without causing such problems. Is.
[0005]
[Means for Solving the Problems]
The first technical means taken in order to solve the above technical problem is as shown in the characteristic item 1.
"With the input axis,
An output shaft;
A first-row double pinion planetary gear G1 connecting the sun gear S1 to the input shaft;
A second row of single pinion planetary gears G2 connecting the sun gear S2 to the output shaft;
A third row of single pinion planetary gears G3 connecting the ring gear R3 to the ring gear R2 of the second row of single pinion planetary gears G2,
A fourth row single pinion planetary gear G4 connecting the ring gear R4 to the ring gear R1 of the first row double pinion planetary gear G1,
The ring gear R3 of the third row single pinion planetary gear G3 and the carrier PC4 of the fourth row single pinion planetary gear G4 are connected, and the sun gear S3 of the third row single pinion planetary gear G3 and the fourth row single pinion gear G3. The sun gear S4 of the planetary gear G4 is connected, and the first shaft element J1 connected to the ring gear R4 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. A second shaft element J2, a third shaft element J3 connected to the carrier PC4 of the third row single pinion planetary gear G3, and a fourth shaft connected to the sun gear S3 of the third row single pinion planetary gear G3. The shaft element J4, and A planetary gear unit G34 of the third shaft element J3 coupled to said output shaft,
A first friction clutch element C1 for selectively connecting the carrier PC1 of the double pinion planetary gear G1 in the first row and the second shaft element J2,
A second friction clutch element C2 for selectively connecting the input shaft and the second shaft element J2,
A third friction clutch element C3 for selectively connecting the input shaft and the carrier PC2 of the second row single pinion planetary gear G2;
A first friction brake element B1 for selectively fixing the carrier PC1;
A second friction brake element B2 for selectively fixing the fourth shaft element J4;
A transmission comprising: "
It is to have constituted.
[0007]
DETAILED DESCRIPTION OF THE INVENTION
Specific examples of the present invention will be described with reference to the accompanying drawings. In this specific example, the case where it is used in an automatic transmission for an automobile will be described.
[0008]
FIG. 1 is a schematic view showing a gear train of an automatic transmission 10 according to a first embodiment of the present invention, and corresponds to claim 1.
[0009]
The automatic transmission 10 is disposed in the housing 1, and the output from the torque converter 2 that outputs the output to the transmission 10 through the shearing force of the viscous medium is advanced by the engine (not shown) according to the switching of the friction engagement element. The speed is switched between 6th speed and reverse 1st speed, and output to the axle (not shown).
[0010]
The transmission 10 includes an input shaft 11 that is an output shaft of the torque converter 2, an output shaft 12 that is coupled to the axle via a differential device (not shown),
A first-row double pinion planetary gear G1 connecting the sun gear S1 to the input shaft;
A second row of single pinion planetary gears G2 connecting the sun gear S2 to the output shaft;
A third row of single pinion planetary gears G3 connecting the ring gear R3 to the ring gear R2 of the second row of single pinion planetary gears G2,
A fourth row single pinion planetary gear G4 connecting the ring gear R4 to the ring gear R1 of the first row double pinion planetary gear G1,
The ring gear R3 of the third row single pinion planetary gear G3 and the carrier PC4 of the fourth row single pinion planetary gear G4 are connected, and the sun gear S3 of the third row single pinion planetary gear G3 and the fourth row single pinion gear G3. The sun gear S4 of the planetary gear G4 is connected, and the first shaft element J1 connected to the ring gear R4 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. A second shaft element J2, a third shaft element J3 connected to the carrier PC4 of the third row single pinion planetary gear G3, and a fourth shaft connected to the sun gear S3 of the third row single pinion planetary gear G3. The shaft element J4, and A planetary gear unit G34 of the third shaft element J3 coupled to said output shaft,
A first friction clutch element C1 for selectively connecting the carrier PC1 of the double pinion planetary gear G1 in the first row and the second shaft element J2,
A second friction clutch element C2 for selectively connecting the input shaft and the second shaft element J2,
A third friction clutch element C3 for selectively connecting the input shaft and the carrier PC2 of the second row single pinion planetary gear G2;
A first friction brake element B1 for selectively fixing the carrier PC1;
And a second friction brake element B2 for selectively fixing the fourth shaft element J4.
[0011]
Accordingly, the coupling or fixing of the frictional engagement elements (C1, C2, C3, B1, B2) is engaged / released (non-engaged) according to the supplied hydraulic pressure. 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 = 0.45, and 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 = 0.588. In the planetary gear G3, ρ3 = the number of teeth of the sun gear S3 / the number of teeth of the ring gear R3 = 0.4, and in the fourth planetary gear G4, 4 = the number of teeth of the sun gear S4 / the number of teeth of the ring gear R4 = 0.29.
[0012]
The table of FIG. 3 shows each friction engagement element (C1, C2, C3, B1, B2) and gear ratio in the first specific example. In the table, ◯ indicates an engaged state, and a blank indicates a released (non-engaged) state.
[0013]
The switching of the gear position in the table of FIG. 3 will be described.
[0014]
First speed: By fixing the rotation of the carrier PC1 in the first row by the engagement of the first friction brake element B1, the torque from the input shaft 11 is input to the first shaft element J1 as an increased ring gear output. To do. On the other hand, when the rotation of the fourth shaft element J4 is locked by the second friction brake element B2, the third shaft element J3 rotates at a reduced speed to form the first speed.
[0015]
Second speed: When the first friction clutch element C1 is engaged, the carrier PC1 and the second shaft element J2 in the first row are connected, and torque from the input shaft 11 is transmitted to the planetary gear unit 34. . On the other hand, when the rotation of the fourth shaft element J4 is locked by the second friction brake element B2, the third shaft element J3 rotates at a reduced speed to form the second speed.
[0016]
Third speed: Torque of the input shaft 11 is input to the second shaft element J2 via the engaged second friction clutch element C2. On the other hand, when the rotation of the fourth shaft element J4 is locked by the second friction brake element B2, the third shaft element J3 rotates at a reduced speed to form the third speed.
[0017]
Fourth speed: The torque of the input shaft 11 is input to the second shaft element J2 via the engaged second friction clutch element C2. On the other hand, the torque of the input shaft 11 is input to the carrier PC2 in the second row via the engaged third friction clutch element C3. As a result, the planetary gear 34 is rotated integrally to form the fourth speed.
[0018]
5th speed: Torque of the input shaft 11 is input to the carrier PC2 in the second row via the engaged third friction clutch element C3. On the other hand, the rotation of the carrier PC1 in the first row is locked by the first friction brake element B1, and as a result, the increased torque of the input shaft 11 output from the ring gear is applied to the first shaft element J1. The third shaft element J3 is rotated at an increased speed to form the fifth speed.
[0019]
Sixth speed: Torque of the input shaft 11 is input to the second shaft element J2 via the engaged second friction clutch element C2. On the other hand, the rotation of the carrier PC1 in the first row is locked by the first friction brake element B1, and as a result, the increased torque of the input shaft 11 output from the ring gear is applied to the first shaft element J1. As a result, the third shaft element J3 rotates at an increased speed to form the sixth speed. To enter.
[0020]
Reverse: The rotation of the carrier PC1 in the first row is locked by the first friction brake element B1, so that the increased torque of the input shaft 11 output from the ring gear is input to the first shaft element J1. The On the other hand, the engaged second friction clutch element C2 connects the carrier PC1 and the second shaft element J2 in the first row, so that the rotation of the second shaft element J2 is locked. The third shaft element J3 rotates in the reverse direction to form reverse.
[0021]
FIG. 2 shows a transmission 20 in the second embodiment. The transmission 20 is one obtained by reversing the arrangement in the axial direction of the single pinion planetary gear of a single pinion planetary gear and the fourth column of the second row with respect to the transmission 10 described above, also, the engagement of the transmission 20 combination and the gear ratios of the elements are the same as the combination and the gear ratios of the engagement elements of the transmission apparatus 10 shown in the table of FIG. 3, description will be omitted.
[0022]
Although specific examples of the present invention have been described above, the present invention is not intended to be limited to the specific examples described above, and any method / apparatus according to the gist of the present invention may be used.
[0023]
【The invention's effect】
As described above, in the transmission according to the present invention, the input shaft is selectively connected to the second shaft element via the first friction clutch element C1, and the sun gear of the planetary gears in the first row is fixed. Therefore, the rotation of the carrier of the first row planetary gear is slower than when the input shaft is always connected to the sun gear of the first row planetary gear. Therefore, the number of rotations of the sun gear of the first planetary gear can be suppressed, gear noise can be reduced, and the durability of the gear can be improved.
[Brief description of the drawings]
FIG. 1 is a schematic view of a transmission according to a first embodiment of the present invention.
FIG. 2 is a schematic view of a transmission according to a second embodiment of the present invention .
FIG. 3 is a table showing switching means that operates at each gear position in the transmission of FIG . 1 ;
[Explanation of symbols]
2 : Torque converter 10: Transmission
11 : Input shaft
12: output shaft 20: transmission G1: first train double pinion planetary gear G2: second row of single pinion planetary gear G3: third column of single pinion planetary gear G34: planetary gear unit S1, S2, S3: the sun gear R1, R2, R3: a ring gear PC1, PC2, PC3: key catcher rear <br/> C1, C2, C3: friction clutch element B1, B2, B3: friction brake elements J1, J2, J3, J43: longitudinal element

Claims (1)

An input shaft;
An output shaft;
A first-row double pinion planetary gear G1 connecting the sun gear S1 to the input shaft;
A second row of single pinion planetary gears G2 connecting the sun gear S2 to the output shaft;
A third row of single pinion planetary gears G3 connecting the ring gear R3 to the ring gear R2 of the second row of single pinion planetary gears G2,
A fourth row single pinion planetary gear G4 connecting the ring gear R4 to the ring gear R1 of the first row double pinion planetary gear G1,
The ring gear R3 of the third row single pinion planetary gear G3 and the carrier PC4 of the fourth row single pinion planetary gear G4 are connected, and the sun gear S3 of the third row single pinion planetary gear G3 and the fourth row single pinion gear G3. The sun gear S4 of the planetary gear G4 is connected, and the first shaft element J1 connected to the ring gear R4 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. A second shaft element J2, a third shaft element J3 connected to the carrier PC4 of the third row single pinion planetary gear G3, and a fourth shaft connected to the sun gear S3 of the third row single pinion planetary gear G3. The shaft element J4, and A planetary gear unit G34 of the third shaft element J3 coupled to said output shaft,
A first friction clutch element C1 for selectively connecting the carrier PC1 of the double pinion planetary gear G1 in the first row and the second shaft element J2,
A second friction clutch element C2 for selectively connecting the input shaft and the second shaft element J2,
A third friction clutch element C3 for selectively connecting the input shaft and the carrier PC2 of the second row single pinion planetary gear G2;
A first friction brake element B1 for selectively fixing the carrier PC1;
A second friction brake element B2 for selectively fixing the fourth shaft element J4;
A transmission comprising:

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