JPH02118241A - Gear speed change gear - Google Patents

Abstract

PURPOSE:To obtain the speed change stages of above five advancing stages by placing a double pinion type first and simple type second and third planetary gear sets in order and selectively operating first to third clutches and brakes. CONSTITUTION:Double pinion type first and simple type second and third planetary gear sets 22, 32, 42 are placed coaxially with input/output shafts 12, 14, and a first carrier 30 is linked to a second ring gear 38, while linking first, second, and third sun gears 24, 34, 44 together, and a second carrier 40, a third ring gear 50 and an output gear 15 together. The first gear is obtained by engaging a clutch 54 and a brake 60, while obtaining the second gear by the clutch 54 and a brake 62, the third gear by the clutch 54 and a brake 64, the fourth gear by clutches 54, 56, the fifth gear by the clutch 56 and brake 64, and the sixth gear by the clutch 56 and brake 62 while, further obtaining backing stages by a clutch 58 and brakes 62/60, respectively. Thereby, the speed change stages of advancing six stages can be obtained merely by the control of two engaging elements.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a gear transmission using a planetary gear mechanism suitable as a sub-transmission of an automatic transmission for an automobile.

[Prior Art] This type of gear transmission is constructed by combining a planetary gear set and engagement means such as clutch means and brake means, and gears are changed by controlling the engagement means. . For example, automobiles generally have four forward speeds and one reverse speed, but by increasing the number of speeds, smoother gear shifting becomes possible.

Multi-stage construction is easily possible, but the number of planetary gear sets and engagement means increases, making the structure complex and large.

Therefore, as a gear transmission that can achieve five or more forward gears while minimizing the complexity and size of the structure, we have developed two sets of thimble planetary gear sets and one
A combination of double pinion and simple planetary gear set has been proposed (Japanese Patent Laid-Open No. 1081-1981).
No. 68, No. 51-108170, etc.).

A gear transmission with such a combination can have a very large number of structures, including combinations with engagement means, but there are few that satisfy all of the conditions listed below, and most that lack one of the conditions. It is.

(1) One of the conditions is that the gear ratio in normal forward gears, excluding overdrive, be arranged in a manner close to a geometric series.

(2) One of the conditions is that the overdrive gear ratio must be able to ensure power performance.

(3) One of the conditions is that the gear ratio of each planetary gear set is appropriate and the outer diameter of the gear train can be made small.

(4) One of the conditions is that shifting to the next gear is possible by controlling the two engaging means.

For example, the above-mentioned JP-A-51-108168 and JP-A-51-108168
No. 108170 does not satisfy the condition (4) above, and the gear cannot be shifted to the next gear unless up to four engagement means are controlled. For this reason, it is difficult to accurately synchronize the operating timings of a large number of engaging means, which causes a shift shock.

[Problems to be Solved by the Invention] In view of the above, the present invention satisfies all of the above conditions and combines two sets of simple planetary gear sets and one set of double pinion simple planetary gear sets to shift gears of five or more forward gears. The objective of the present invention is to provide a gear transmission that can establish gears.

[Means for Solving the Problems] In the gear transmission according to the first invention, an input shaft rotatably supported with respect to the housing case, an output shaft rotatably supported with respect to the housing case, and an input shaft rotatably supported with respect to the housing case. A first sun gear rotatably supported with respect to the case, a first pinion meshing with the first sun gear, and a second pinion meshing with the first pinion rotatably supported and rotatably arranged with respect to the storage case. A first planetary gear consisting of a double pinion simple planetary gear set in combination with a first carrier coaxially arranged with the first sun gear and a first ring gear arranged rotatably with respect to the housing case and meshed with the second pinion. a second sun gear that is rotatably supported with respect to the housing case; a second carrier that rotatably supports a third pinion that meshes with the second sun gear and is rotatably disposed with respect to the housing case; a second planetary gear set consisting of a simple planetary gear set in combination with a second ring gear disposed coaxially with the second sun gear and rotatably disposed with respect to the housing case and meshing with the third pinion; A third planetary gear set consisting of a simple planetary gear set having a similar combination, first to third clutch means, first to third brake means, and a first sun gear, a second sun gear, and a third sun gear. are connected, the first carrier and the second ring gear are connected, the second carrier, the third ring gear and the output shaft are connected, and the first clutch means is capable of connecting the input shaft to the first carrier and the second ring gear. The second clutch means is arranged to connect the input shaft to the first ring gear, the third clutch means is arranged to connect the input shaft to the first sun gear, the second sun gear, and the third sun gear, and the second clutch means is arranged to connect the input shaft to the first sun gear, second sun gear, and third sun gear, The brake means is arranged so as to be able to restrain the first ring gear with respect to the housing case, the second brake means is arranged so that the third carrier can be restrained with respect to the housing case, and the third brake means is arranged so that the first ring gear can be restrained with respect to the housing case. and the third sun gear are arranged so as to be able to be restrained with respect to the housing case.

In the gear transmission according to the second invention, the input shaft is rotatably supported with respect to the housing case, the output shaft is rotatably supported with respect to the housing case, and the output shaft is rotatably supported with respect to the housing case. a first sun gear, a first sun gear that rotatably supports a first pinion that meshes with the first sun gear, and a second pinion that meshes with the first binion, and that is rotatably arranged with respect to the housing case; A first planetary gear set consisting of a double pinion simple planetary gear set in combination with a first ring gear that is arranged coaxially and rotatably relative to the housing case and meshes with the second binion, and a first planetary gear set that rotates relative to the housing case. a second sun gear rotatably supported and a third pinion meshing with the second sun gear; and a second carrier rotatably disposed relative to the housing case and coaxially disposed with the second sun gear. a second planetary gear set consisting of a simple planetary gear set in combination with a second ring gear which is rotatably arranged with respect to the storage case and meshes with the third pinion; and a simple planetary gear set in the same combination as the second planetary gear set. A third planetary gear set, first to third clutch means, and first to third brake means, the first sun gear and the third sun gear are connected, and the first carrier and the second sun gear are connected. The first ring gear and the second ring gear are connected, the second carrier, the third ring gear and the output shaft are connected, and the first clutch means connects the input shaft to the first carrier and the second sun gear. The second clutch means is arranged to be able to connect the input shaft to the first ring gear and the second ring gear, the third clutch means is arranged to be able to connect the input shaft to the first sun gear and the third sun gear, and the third clutch means is arranged to be able to connect the input shaft to the first sun gear and the third sun gear. The first brake means is arranged to be able to restrain the first ring gear and the second ring gear to the housing case, the second brake means is arranged to be able to restrain the third carrier to the housing case, and the third brake means is arranged to be able to restrain the first ring gear and the second ring gear to the housing case. The sun gear and the third sun gear are arranged so as to be able to be restrained with respect to the housing case.

[Action] In the first and second inventions that are the means described above, the first speed is selected by the connection by the first clutch means and the restraint by the first brake means, and the first speed is selected by the connection by the first clutch means and the restraint by the second brake means. The second speed is selected by the first clutch means, and the third speed is selected by the connection by the first clutch means and the restraint by the third brake means.
The speed is selected, the fourth speed is selected by connection by the first clutch means and the second clutch means, the fifth speed is selected by connection by the second clutch means and restraint by the third brake means, and the fifth speed is selected by connection by the second clutch means and restraint by the third brake means. The sixth speed is selected by the connection by the third clutch means and the restraint by the second brake means, the first reverse gear is selected by the connection by the third clutch means and the restraint by the second brake means, and the first reverse gear is selected by the connection by the third clutch means and the restraint by the second brake means. 1, the second reverse gear can be selected by restraint by the brake means.

[Example 1] Figure 1 shows the first embodiment of the gear transmission of the first invention.
The embodiment is shown in a skeleton diagram with the lower half omitted.

Components of the gear transmission are housed in a transmission case 10 (only a part of the peripheral wall is shown in the figure) as a housing case.

The input shaft 12 serving as the input end is connected to the transmission case 1
A first intermediate shaft 16 is rotatably supported relative to the input shaft 12 and is disposed adjacent to the input shaft 12 and coaxially in line with the input shaft 12 . The first intermediate shaft 16 is rotatably supported on the transmission case 10. A second intermediate shaft 18 is disposed coaxially with the first intermediate shaft 16 outside the first intermediate shaft 16, and independently of the first intermediate shaft 16,
The transmission case 10 is rotatably supported. Further, an output shaft 14 serving as an output end is disposed coaxially with the second intermediate shaft 18 outside the second intermediate shaft 18 , and the transmission case 14 is arranged independently of the second intermediate shaft 18 .
It is rotatably supported with respect to 0. An output gear 15 is fixed to the output shaft 14.

The first planetary gear set 22 includes a first sun gear 24 concentrically fixed to the first intermediate shaft 16, and a first sun gear 24 fixed to the first intermediate shaft 16.
4, a plurality of second pinions 27 that mesh with the first pinion 26, a first ring gear 28 that meshes with the second pinion 27, and a first pinion 26 and a second pinion 27. This is a double pinion simple planetary gear set including a first carrier 30 rotatably supported. The first ring gear 28 and the first carrier 30 are rotatably arranged with respect to the transmission case 10.

The second planetary gear set 32 includes a second sun gear 34 concentrically fixed to the first intermediate shaft 16, and a second sun gear 34 fixed to the first intermediate shaft 16.
4, a second ring gear 38 that meshes with the third pinion 36, and a third pinion 38 that meshes with the third pinion 36.
6 and a second carrier 40 that rotatably supports the gear. 2nd ring gear 3
8 and the second carrier 40 are the transmission case 1
It is arranged rotatably with respect to 0.

The third planetary gear set 42 includes a third sun gear 44 concentrically fixed to the first intermediate shaft 16, and a third sun gear 44 fixed to the first intermediate shaft 16.
a plurality of fourth pinions 46 meshing with the fourth pinion 4; a third ring gear 50 meshing with the fourth pinion 46;
6 and a third carrier 52 that rotatably supports the gear. 3rd ring gear 5
0 and 3rd carrier 52 are transmission case 1
It is arranged rotatably with respect to 0.

Here, the first carrier 30 and the second ring gear 38 are connected to rotate together.

Further, the second carrier 40, the third ring gear 50, and the output shaft 14 are connected to rotate together.

The first clutch means 54 is connected to the input shaft 12 and the first carrier 30.
and the second ring gear 38. The second clutch means 56 is arranged to connect the input shaft 12 and the first ring gear 28. The third clutch means 58 is connected to the input shaft 12, the first sun gear 24, and the second sun gear 3.
4 and third sun gear 44 are arranged so as to be connectable. These first clutch means 54 to third clutch means 58
The operation is controlled by a hydraulic control device (not shown), and the components are connected as described above.

The first brake means 60 is arranged so as to be able to restrain the first ring gear 28 against the transmission case 10 in a non-rotatable manner. The second brake means 62 is arranged so as to be able to restrain the third carrier 52 against rotation with respect to the transmission case 10. The third brake means 64 is arranged so as to be able to restrain the first sun gear 24, the second sun gear 34, and the third sun gear 44 from rotating relative to the transmission case 10.

The operation of these first to third brake means 60 to 64 is controlled by a hydraulic control device (not shown), and operates to restrain each component as described above.

In this embodiment, the first planetary gear set 22 has a gear ratio ρ1 of 0.385, the second planetary gear set 32 has a gear ratio ρ2 of 0.379, and the third planetary gear set 42 has a gear ratio ρ3 of 0.385. It is 471.

Further, the first clutch means 54 to third clutch means 58 and the first brake means 60 to third brake means 64 are of a friction multi-plate type.

Next, the operation of this embodiment will be explained.

In addition, FIG. 2 shows the first clutch means 5 at each gear stage.
4~Third clutch means 58 and first brake means 60~
The operating status of the third brake means 64 (○ indicates operating status) and the gear ratio are shown.

First speed In the first speed, the first clutch means 54 and the first brake means 60 are operated. Thereby, the input shaft 12, the first carrier 30, and the second ring gear 38 are connected, and the rotation of the first ring gear 28 is restrained.

The power input from the input shaft 12 is transmitted to the second ring gear 38.
from the second ring gear 38 to the third pinion 36
is transmitted to the second carrier 4o via the second carrier 4o.
0 to the output shaft 14. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the second sun gear 34 via the third pinion 36, and from the second sun gear 34 to the first sun gear 24 via the first intermediate shaft 16. from the first sun gear 24 via the first pinion 26.
The signal is transmitted to the carrier 30 and then to the second ring gear 38.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates together with the input shaft 12, and the first ring gear 28
has stopped rotating. Further, in the second planetary gear set 32, the second sun gear 34 rotates in the opposite direction to the input shaft 12, the second carrier 40 rotates in the same direction as the input shaft 12, and the second ring gear 38 rotates in the same direction as the input shaft 12. It rotates together with the shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 rotates in the opposite direction to the input shaft 12, and the third ring gear 50 is integrated with the second carrier 40. Thus, it is rotating in the same direction as the input shaft 12.

In this first speed, the third planetary gear set 42 is not involved in the gear ratio, and the first planetary gear set 22 and the second planetary gear set 32 control the speed ρ1 (1+ρ
A gear ratio of 2)/(ρ1-ρ2+ρ1ρ2) is obtained, and in this example, a numerical value of 3.495 is obtained.

Second speed In the second speed, the first clutch means 54 and the second brake means 62 are operated. That is, when shifting from the first speed, the first clutch means 54 remains activated, the first brake means 60 is deactivated, and the second brake means 62 is activated instead.

As a result, the input shaft 12, the first carrier 30, and the second ring gear 38 remain connected, and the rotation of the third carrier 52 is newly restricted.

The power input from the input shaft 12 is transmitted to the second ring gear 38.
from the second ring gear 38 to the third pinion 36
is transmitted to the second carrier 40 via the second carrier 40.
0 to the output shaft 14. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the second sun gear 34 via the third pinion 36, and from the second sun gear 34 to the third sun gear 44 via the first intermediate shaft 16. from the third sun gear 44 via the fourth pinion 46.
The signal is transmitted to the ring gear 50, and from the third ring gear 50 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates together with the input shaft 12, and the first ring gear 28
is rotating in the same direction as the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 rotates in the opposite direction to the input shaft 12, and the second carrier 40 rotates in the opposite direction to the input shaft 12.
The second ring gear 38 rotates in the same direction as the input shaft 12, and the second ring gear 38 and the first carrier 30 rotate together with the input shaft 12. Also,
In the third planetary gear set 42, the third sun gear 44
rotates in the opposite direction to the input shaft 12, the third carrier 52 stops rotating, and the third ring gear 50 rotates in the same direction as the input shaft 12 together with the second carrier 40.

In this second speed, the first planetary gear set 22 is not involved in the gear ratio, and the second planetary gear set 3
With the second and third planetary gear set 42, (ρ
A gear ratio of 2+ρ3+ρ2ρ3)/ρ3 is obtained, and in this example, a numerical value of 2.184 is obtained.

Third speed In the third speed, the first clutch means 54 and the third brake means 64 are operated. That is, when shifting from the second speed, the first clutch means 54 remains activated, the second brake means 62 is deactivated, and the third brake means 64 is activated instead.

As a result, the rotation of the first sun gear 24, the second sun gear 34, and the third sun gear 44 is newly restrained while the input shaft 12, the first carrier 3o, and the second ring gear 38 remain connected.

The power input from the input shaft 12 is transmitted to the second ring gear 38.
from the second ring gear 38 to the third pinion 36.
is transmitted to the second carrier 4o via the second carrier 4o.
0 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 stops rotating, and the second carrier 40 connects the input shaft 1.
2, and the first ring gear 28 rotates in the same direction as the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 stops rotating, the second carrier 4o rotates in the same direction as the input shaft 12, and the second ring gear 38 is integrated with the input shaft 12 together with the first carrier 30. It's rotating. In addition, the third planetary gear set 42
Then, the third sun gear 44 stops rotating, the third carrier 52 rotates in the same direction as the input shaft 12, and the third ring gear 5
0 rotates together with the second carrier 40 in the same direction as the input shaft 12.

In this third speed, the first planetary gear set 22 and the third planetary gear set 42 are not involved in the gear ratio, and the second planetary gear set 32 provides a gear ratio of 1+ρ2, which is a numerical value of 1.379 in this embodiment. I am getting .

Fourth speed In the fourth speed, the first clutch means 54 and the second clutch means 56 are operated. That is, when shifting from the third speed, the first clutch means 54 remains in operation, the operation of the third brake means 64 is released, and the second clutch means 56 is operated instead.

As a result, the input shaft 12 and the first ring gear 28 are newly connected, while the input shaft 12, the first carrier 30, and the second ring gear 38 remain connected.

The power input from the input shaft 12 via the first clutch means 54 is transmitted to the second ring gear 38, and from the second ring gear 38 via the third pinion 36 to the second carrier 40.
from the second carrier 40 to the output shaft 14. Further, the power input from the input shaft 12 via the second clutch means 56 is transmitted to the first ring gear 28,
The signal is transmitted from the first ring gear 28 to the first sun gear 24 via the second pinion 27 and the first pinion 26, and from the first sun gear 24 via the first intermediate shaft 16 to the second sun gear 3.
4 and from the second sun gear 34 to the third pinion 36
is transmitted to the second carrier 40 via the second carrier 40.
0 to the output shaft 14. A part of the power input from the input shaft 12 via the second clutch means 56 is transmitted from the first ring gear 28 to the first carrier 30 via the second pinion 27, and from the second ring gear 38 to the third pinion 36. The signal is then transmitted to the second carrier 40 via the second carrier 40, and from the second carrier 40 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates together with the input shaft 12, and the first carrier 3
0 rotates together with the input shaft 12, and the first ring gear 28 rotates together with the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 is connected to the input shaft 12.
The second carrier 40 rotates together with the input shaft 12, and the second ring gear 38 rotates together with the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 rotates together with the input shaft 12, and the third sun gear 44 rotates integrally with the input shaft 12.
The carrier 52 rotates together with the input shaft 12, and the third ring gear 50 rotates together with the input shaft 12.

In this fourth speed, the first planetary gear set 22, the second
Since the respective elements of the planetary gear set 32 and the third planetary gear set 42 are all integrated and rotate together with the input shaft 12, a gear ratio of 1 is obtained.

Fifth speed In the fifth speed, the second clutch means 56 and the third brake means 64 are operated. That is, when shifting from the fourth speed, the second clutch means 56 remains in operation, the first clutch means 54 is deactivated, and the third brake means 64 is activated instead.

As a result, the input shaft 12 and the first ring gear 28 remain connected, and the first sun gear 24 and the second sun gear 34 are newly connected.
And the rotation of the third sun gear 44 is restricted.

The power input from the input shaft 12 is transmitted to the first ring gear 28.
is transmitted from the second ring gear 38 to the second carrier 40 via the first pinion 26 and second pinion 27, and from the second ring gear 38 to the second carrier 40 via the third pinion 36. to output shaft 1
4.

At this time, in the first planetary gear set 22, the first sun gear 24 stops rotating, and the first carrier 30 connects the input shaft 1.
2, the first ring gear 28 rotates in the same direction as the input shaft 12.
It rotates as one. Further, in the second planar gear set 32, the second sun gear 34 stops rotating, and the second sun gear 34 stops rotating.
The carrier 4o rotates in the same direction as the input shaft 12, and the second ring gear 38 and the first carrier 30 rotate in the same direction as the input shaft 1.
It is rotating in the same direction as 2. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating, the third carrier 52 rotates in the same direction as the input shaft 12, and the third ring gear 5o is integrated with the second carrier 40 to rotate the input shaft. It is rotating in the same direction as 12.

In this fifth speed, the third planetary gear set 42 does not participate in the gear ratio, and the first planetary gear set 22 and the second planetary gear set 32 shift the speed to (1+ρ1).
A gear ratio of (1+ρ2) is obtained, which is 0.84 in this example.
I got a value of 8.

Sixth speed In the sixth speed, the second clutch means 56 and the second brake means 62 are operated. That is, when shifting from the fifth speed, the second clutch means 56 remains in operation, the third brake means 64 is deactivated, and the second brake means 62 is activated instead. As a result, the input shaft 12 and the first ring gear 28 remain connected, and the rotation of the third carrier 52 is newly restrained.

The power input from the input shaft 12 is transferred to the first ring gear 28.
is transmitted from the second ring gear 38 to the second carrier 40 via the first pinion 26 and second pinion 27, and from the second ring gear 38 to the second carrier 40 via the third pinion 36. to output shaft 1
4. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the second sun gear 34 via the third pinion 36, and from the second sun gear 34 to the first intermediate shaft 1.
6 to the first sun gear 24, and from the first sun gear 24 to the first carrier 30 via the first pinion 26. Further, a part of the power transmitted to the second carrier 40 is transmitted to the third ring gear 50, and is transmitted from the third ring gear 50 to the third sun gear 4 via the fourth pinion 46.
from the third sun gear 44 to the first sun gear 24 via the first intermediate shaft 16;
is transmitted to the first carrier 30 via the first pinion 26.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first ring gear 24 rotates in the same direction as the input shaft 12.
8 rotates together with the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 rotates in the opposite direction to the input shaft 12, and the second carrier 40 rotates in the opposite direction to the input shaft 12.
The second ring gear 38 rotates together with the first carrier 30 in the same direction as the input shaft 12 . Further, in the third planetary gear set 42, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 stops rotating, and the third ring gear 50 is integrated with the second carrier 40 to rotate the input shaft. It is rotating in the same direction as 12.

In this sixth speed, the first planetary gear set 22, the second
The planetary gear set 32 and the third planetary gear set 42 are involved in the gear ratio, and by them, (ρ3-(
A gear ratio of 1+ρ3)(ρ1-ρ2+ρ1ρ2))/ρ3 is obtained, and in this example, a numerical value of 0.526 is obtained.

Reverse (Part 1) In reverse, the third clutch means 58 and the second brake means 62 are operated. Thereby, the input shaft 12 and the first intermediate shaft 16 are connected, and the rotation of the third carrier 52 is restrained.

The power input from the input shaft 12 is transmitted to the third sun gear 44 via the first intermediate shaft 16, and from the third sun gear 44 via the fourth pinion 46 to the third ring gear 50. and is transmitted to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the first intermediate shaft 16 rotates together with the input shaft 12, the first carrier 30 rotates in the opposite direction to the input shaft 12, and the first The ring gear 28 is in the opposite direction to the input shaft 12.
It's rotating. Further, in the second planetary gear set 32, a second sun gear 34 connected to the first intermediate shaft 16 rotates together with the input shaft 12, and a second carrier 40 rotates together with the input shaft 12.
2, and the second ring gear 38 rotates together with the first carrier 30 in the opposite direction to the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 connected to the first intermediate shaft 16 rotates together with the input shaft 12, the third carrier 52 stops rotating, and the third sun gear 44 is connected to the first intermediate shaft 16.
The ring gear 50 rotates together with the second carrier 40 in the opposite direction to the input shaft 12.

In this retraction, the first planetary gear set 22 and the second
The planetary gear set 32 is not involved in the gear ratio and is
The planetary gear set 42 provides a gear ratio of -1/ρ3, which in this embodiment is -2,123.

Reverse (Part 2) In addition, in this embodiment, a larger gear ratio can be used for reverse, and it is possible to combine it with the aforementioned reverse to create two reverse gears, or to arbitrarily select either one. There is.

In this backward movement, the third clutch means 58 and the first brake means 60 are operated. This allows the input shaft 12 and the first
The intermediate shaft 16 is connected, and the first ring gear 28
is restricted from rotation.

The power input from the input shaft 12 is transmitted to the first sun gear 24 via the first intermediate shaft 16, and from the first sun gear 24 to the first pinion 26 and the second pinion 27.
The signal is transmitted to the carrier 30 and the second ring gear 38, and the second
It is transmitted from the ring gear 38 to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft 14.
transmitted to. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the second sun gear 34 via the third pinion 36, and from the second sun gear 34 to the first intermediate shaft 16.
is transmitted to the first sun gear 24 via.

At this time, in the first bracket gear set 22, the first gear 24 connected to the first intermediate shaft 16 rotates together with the input shaft 12, and the first carrier 30 rotates in the opposite direction to the input shaft 12. However, the first ring gear 28 has stopped rotating.

Further, in the second planetary gear set 32, the second sun gear 34 connected to the first intermediate shaft 16 rotates together with the input shaft 12, the first carrier 30 rotates in the opposite direction to the input shaft 12, and the second ring gear 38 rotates integrally with the first carrier 30 in the opposite direction to the input shaft 12. Also, the third
In the planetary gear set 42, a third sun gear 44 connected to the first intermediate shaft 16 rotates together with the input shaft 12,
The third carrier 52 rotates in the same direction as the input shaft 12, and the third carrier 52 rotates in the same direction as the input shaft 12.
The ring gear 50 rotates together with the second carrier 40 in the opposite direction to the input shaft 12.

In this backward movement, the third planetary gear set 42 does not take part in the transmission ratio, and the first planetary gear set 22 and the second planetary gear set 42
-(1-ρ1) by the planetary gear set 32
A gear ratio of (1+ρ2)/(ρ1-ρ2+ρ1ρ2) is obtained, and in this example, a numerical value of -5,583 is obtained.

In the gear transmission of the first embodiment constructed and operated as described above, the desired problems can be solved, and the first sun gear 24, second sun gear 34, and third sun gear 44 are integrated into a long pinion. This allows the device to be made more compact, and since power circulation does not occur in the second to fifth speeds, there is an advantage that efficiency is improved and fuel consumption is improved.

In addition, in the above embodiment, the first clutch means 54 to third clutch means 58 and the first brake means 6 as engaging means are used.
Although all of the zero to third brake means 64 are constructed of a single friction multi-plate type, they may also be constructed as described below.

The first clutch means 54 can have the configuration shown in FIG. That is, the one-way clutch 68 may be connected in series to the multi-disc clutch 66 of the friction multi-disc type described above, thereby making it possible to transmit torque only from the input shaft 12 to the first carrier 30.

Therefore, in the first to fourth speeds in which the first clutch means 54 is in the operating state, no torque is transmitted from the first carrier 30 to the input shaft 12, and the engine brake is released, improving fuel efficiency and quietness. It has the advantage of improving

Furthermore, when shifting between 1st to 4th speeds and 5th or 6th speed, the first carrier 30 rotates faster than the input shaft 12 in the 5th or 6th speed. , in the first to fourth speeds, the first carrier 30 is at a speed equal to or less than the same as the input shaft 12, so when upshifting, the first clutch means 54 is automatically activated by the action of the one-way clutch 680. The timing of starting or releasing the first clutch means 54 is set precisely because the first clutch means 54 is in the deactivated state and the first carrier 30 and the input shaft 12 are rotated in synchronization with each other during downshifting. Even without this, shift shock can be suppressed and shift control becomes easier.

Further, the first clutch means 54 can have the configuration shown in FIG. 4. That is, as shown in FIG. 3, the multi-disc clutch 66 and the one-way clutch 68 may be coupled in series, and the multi-disc clutch 70 may be coupled in parallel.

Therefore, it has the same advantages as the one in FIG. 3, and by selectively operating the multi-disc clutch 70, engine braking can be applied as needed, such as when exiting the vehicle.

The second clutch means 56 can have the same configuration as shown in FIGS. 3 and 4 above, and the engine brake is not applied in the fourth to sixth speeds in which the second clutch means 56 is in the operating state. This improves fuel efficiency and quietness, and depending on the configuration, engine braking can be applied as needed.

The third clutch hand 58 has the same configuration as shown in FIGS. 3 and 4, and as shown in FIG. A one-way clutch 72 whose engagement direction is opposite to that of 68 is connected in parallel,
As shown in FIG. 6, it may be composed of a multi-disc clutch 66 and a one-way clutch 72 connected in parallel, and in this case also, the third clutch means 58 is activated. In (1 and 2), fuel efficiency and quietness are improved, and depending on the configuration, engine braking can be applied as needed.

Further, this third clutch means 58 is connected to the first clutch means 5.
By operating simultaneously with the fourth or second clutch means 56, a power transmission path different from that of the above embodiment can be taken in the fourth speed. In the fourth speed, which is operated simultaneously with the first clutch means 54, fuel efficiency and quietness are improved by releasing the one-way clutch 68 as described above. Furthermore, in the fourth speed due to the simultaneous operation with the second clutch means 56, the one-way clutch 72 is automatically released, thereby improving fuel efficiency and quietness, and also improving the speed between the fourth speed and the fifth or sixth speed. This makes it easier to control the speed change between the two.

The first braking means 60 has the same construction as shown in FIGS. 3 and 4, and a multi-disc clutch 66 and a one-way clutch 6 connected in series as shown in FIG.
8, a multi-disc clutch 70 and a one-way clutch 72 coupled in series are coupled in parallel, and a multi-disc clutch 66 and a one-way clutch 72 coupled in series as shown in FIG. There are two types of brakes, one in which the brakes are connected in parallel, one in which the band brake has a band brake 74 that applies braking force in one direction as shown in FIG.
As shown in the figure, a band brake 74 is connected in parallel with a band brake 76 whose braking direction is opposite to that of the band brake 74, and a multi-disc clutch 66 and a band brake 74 are connected in parallel as shown in FIG. It can be configured in such a way that it is combined with

In these cases as well, fuel efficiency and quietness are improved in the first speed and in reverse (2) when the first brake means 60 is activated, and depending on the configuration, engine braking can be applied as necessary. Furthermore, 1st gear and 2nd gear
It becomes easy to control the speed change between speeds 1 to 6.

The second brake means 62 is shown in FIGS. 4, 7, and 8.
The configuration can be the same as that shown in FIG. 9, FIG. 10, and FIG. 11, and the fuel efficiency and The quietness is improved, and depending on the configuration, engine braking can be applied as needed, and furthermore, the speed change control between the second speed and the third to sixth speeds becomes easier.

The third brake means 64, like the second brake means 62, may have the same construction as shown in FIGS. 4, 7, 8, 9, 1O, and 11. In the third and fifth speeds where the third brake means 64 operates, fuel efficiency and quietness are improved, and depending on the configuration, engine braking can be applied as necessary. Shift control between 4th speed and 5th speed (!: 6th speed) becomes easy.

FIG. 12 shows a second embodiment as an example which is provided with engagement means different from the first embodiment described above.

In the gear transmission of this second embodiment, the first clutch means 54 has the structure shown in FIG. 4, the first brake means 6o has the structure shown in FIG.
The brake means 62 has the structure shown in FIG. 4, and the third brake means 64 has the structure shown in FIG.

Further, FIG. 13 shows a third embodiment in which the first invention is applied to a front wheel drive vehicle with a horizontally installed engine.

In this embodiment, the input shaft 12 is passed inside the first intermediate shaft 16, and the position of the third clutch means 58 is changed accordingly. The output gear 15 is linked to a differential gear 82 via an intermediate gear 80, and a shaft 84 of the differential gear 82 is connected to a drive shaft.

In the case of this embodiment as well, the engaging means can be configured as described above.

FIG. 14 shows a fourth embodiment of the gear transmission according to the second invention.

The gear transmission is housed in a transmission case 10 (only a part of the peripheral wall is shown in the figure).

component is contained in the container.

The input shaft 12 serving as the input end is connected to the transmission case 1
A first intermediate shaft 16 is rotatably supported relative to the input shaft 12 and is disposed adjacent to the input shaft 12 and coaxially in line with the input shaft 12 . The first intermediate shaft 16 is rotatably supported on the transmission case 10. A second intermediate shaft 18 is disposed coaxially with the first intermediate shaft 16 outside the first intermediate shaft 16, and is rotatably supported with respect to the transmission case 10 independently of the first intermediate shaft 16. ing. Further, a second intermediate shaft 1 is provided outwardly from the second intermediate shaft 18.
An output shaft 14 serving as an output end is arranged coaxially with the second
Transmission case 10 independently of intermediate shaft 18
is rotatably supported against. An output gear 15 is fixed to the output shaft 14. Further, between the input shaft 12 and the second intermediate shaft 18, a first
A third intermediate shaft 20 is disposed coaxially with the intermediate shaft 16, and the first
Transmission case 10 independently of intermediate shaft 16
is rotatably supported against.

The first planetary gear set 22 has a first sun gear 24 fixed concentrically to the first intermediate shaft 16, and is constructed from the same combination as in the first embodiment. The second planetary gear set 32 has a second sun gear 34 fixed concentrically to the third intermediate shaft 20, and is constructed from the same combination as the first embodiment. The third planetary gear set 42 is
A third sun gear 44 is fixed concentrically to the first intermediate shaft 16, and is constructed from the same combination as the first embodiment.

Here, the first carrier 30 is connected to the third intermediate shaft 20 and rotates integrally with the second sun gear 34. Further, the first ring gear 28 and the second ring gear 38 are connected to rotate together. Further, the second carrier 4o, the third ring gear 50, and the output shaft 14 are connected to rotate together.

The first clutch means 54 is connected to the input shaft 12 and the first carrier 30.
and second sun gear 34.

The second clutch means 56 is connected to the input shaft 12 and the first ring gear 2.
8 and the second ring gear 38 are arranged so as to be connectable. The third clutch means 58 is connected to the input shaft 12 and the first intermediate shaft 1.
6 are arranged so as to be connectable. The operation of these first clutch means 54 to third clutch means 58 is controlled by a hydraulic control device (not shown), and operates to connect each component as described above.

The first brake means 60 is arranged so as to be able to restrain the first ring gear 28 and the second ring gear 38 from rotating with respect to the transmission case 10. The second brake means 62 is connected to the third carrier 5 via the second intermediate shaft 18.
2 is arranged so as to be non-rotatably restrained relative to the transmission case 10. Third brake means 6
4 is connected to the first sun gear 24 and the third sun gear via the first intermediate shaft 16.
The sun gear 44 is arranged so as to be non-rotatably restrained relative to the transmission case 10. The operation of these first to third brake means 60 to 64 is controlled by a hydraulic control device (not shown), and operates to restrain each component as described above.

In this embodiment, the first planetary gear set 22 has a gear ratio ρ1 of 0.385, the second planetary gear set 32 has a gear ratio p2 of 0.400, and the third planetary gear set 42 has a gear ratio p3 of 0.385. It is 471.

Further, the first clutch means 54 to third clutch means 58 and the first brake means 60 to third brake means 64 are of a friction multi-plate type.

Next, the operation of this embodiment will be explained.

In addition, FIG. 13 shows the first clutch means 54 to third clutch means 58 and first brake means 60 at each gear stage.
- The operating status of the third brake means 64 (○ indicates the operating state) and the gear ratio are shown.

First speed In the first speed, the first clutch means 54 and the first brake means 60 are operated. Thereby, the input shaft 12, the first carrier 30, and the second sun gear 34 are connected, and the rotation of the first ring gear 28 and the second ring gear 38 is restrained.

The power input from the input shaft 12 is transmitted to the second sun gear 34, from the second sun gear 34 via the third pinion 36 to the second carrier 40, and from the second carrier 40 to the output shaft 14. .

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates together with the input shaft 12, and the first ring gear 28
has stopped rotating. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the input shaft 12 together with the first carrier 30, the second carrier 40 rotates in the same direction as the input shaft 12, and the second ring gear 38 rotates. It's stopped. In addition, the third planetary gear set 42
In this case, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 rotates in the opposite direction to the input shaft 12, and the third ring gear 50 and the second carrier 40 rotate together with the input shaft 12. are rotating in the same direction.

In this first speed, the first planetary gear center 22 and the third planetary gear set 42 do not take part in the gear ratio, and the second planetary gear set 32 shifts the gear ratio between (l + ρ2)/
A gear ratio of ρ2 is obtained, and in this example, a numerical value of 3.500 is obtained.

Second speed In the second speed, the first clutch means 54 and the second brake means 62 are operated. That is, during the shift from the first speed, the first clutch means 54 remains activated, the first brake means 6o is deactivated, and the second brake means 62 is activated instead.

As a result, the input shaft 12, the first carrier 3o, and the second sun gear 34 remain connected, and the third carrier 5o is newly connected.
2 is restricted from rotation.

The power input from the input shaft 12 is transmitted to the first carrier 30 and the second sun gear 34, from the second sun gear 34 to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft. 14. Further, the power transmitted to the first carrier 3° is transmitted to the first sun gear 24 via the first pinion 26, and transmitted from the first sun gear 24 to the third sun gear 44 via the first intermediate shaft 16, The signal is transmitted from the third sun gear 44 to the third ring gear 50 via the fourth pinion 46.
0 to the output shaft 14. Also, the second sun gear 3
A part of the force transmitted to the second ring gear 4 is transmitted to the second ring gear 38 and the first ring gear 28 via the third pinion 36, and from the first ring gear 28 to the first pinion 26 and the second ring gear 28.
It is transmitted to the first sun gear 44 via the pinion 27.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates together with the input shaft 12, and the first ring gear 28
is rotating in the same direction as input I#12. Further, in the second planetary gear set 32, the second sun gear 34 is connected to the first
It rotates together with the input shaft 12 together with the carrier 3o, and the second
The carrier 40 rotates in the same direction as the input shaft 12, and the second ring gear 38 rotates together with the first ring gear 28 in the same direction as the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 stops rotating, and the third sun gear 44 rotates in the opposite direction to the input shaft 12.
The ring gear 5o is rotating in the same direction as the input shaft 12.

In this second speed, the first planetary gear set 22, the second
The planetary gear set 32 and the third planetary gear set 42 are related to the gear ratio, so that (ρ1+ρ3
A gear ratio of +ρ2ρ3)/ρ3 (1-ρ1+ρ2) is obtained, and in this example, a numerical value of 2.184 is obtained.

Third speed In the third speed, the first clutch means 54 and the third brake means 64 are operated. That is, when shifting from the second speed, the first clutch means 54 remains activated, the second brake hand 62 is deactivated, and the third brake means 64 is activated instead.

As a result, the input shaft 12, the first carrier 30, and the second sun gear 34 remain connected, and the first sun gear 24 is newly connected.
And the rotation of the third sun gear 44 is restricted.

The power input from the input shaft 12 is transmitted to the first carrier 30 and the second sun gear 34, from the second sun gear 34 to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft. 14. Further, a part of the power input to the first carrier 30 is transmitted via the second pinion 27 to the first ring gear 28 and the second ring gear 38, and from the second ring gear 38 via the third pinion 36 to the second ring gear 38. The signal is transmitted to the carrier 40, and from the second carrier 40 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 stops rotating, and the second carrier 40 connects the input shaft 1.
2, and the first ring gear 28 rotates in the same direction as the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the input shaft 12 together with the first carrier 30, the second carrier 40 rotates in the same direction as the input shaft 12, and the second ring gear 38 rotates in the same direction as the input shaft 12.
It rotates together with the ring gear 28 in the same direction as the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating, and the third carrier 52
rotates in the same direction as the input shaft 12, and the third ring gear 50 rotates in the same direction as the input shaft 12 together with the second carrier 40.

In this third speed, the third planetary gear set 42 is not involved in the gear ratio, and the first planetary gear set 22 and the second planetary gear set 32 provide (1+ρ1)/
A gear ratio of (1-ρI+ρ2) is obtained, and in this example, a numerical value of 1.379 is obtained.

Fourth speed In the fourth speed, the first clutch means 54 and the second clutch means 56 are operated. That is, when shifting from the third speed, the first clutch means 54 remains in operation, the third brake means 64 is deactivated, and the second clutch means 56 is activated instead.

As a result, the input shaft 12, the first carrier 30, and the second sun gear 34 remain connected, and the input shaft 12 is newly connected to the first sun gear.
Ring gear 28 and second ring gear 38 are connected.

The power manually applied from the input shaft 12 via the first clutch means 54 is transmitted to the second sun gear 34, and the power is transmitted to the second sun gear 34.
4 to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft 14. Further, the power manually applied from the input shaft 12 via the second clutch means 56 is transmitted from the second ring gear 38 to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft 14. Ru.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates together with the input shaft 12, and the second carrier 4
0 rotates together with the input shaft 12, and the first ring gear 28 rotates together with the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 is connected to the input shaft 12.
The second carrier 40 rotates together with the input shaft 12, and the second ring gear 38 rotates together with the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 rotates together with the input shaft 12, and the third sun gear 44 rotates integrally with the input shaft 12.
The carrier 52 rotates together with the input shaft 12, and the third ring gear 50 rotates together with the input shaft 12.

In this fourth speed, the first planetary gear set 22, the second
Since the respective elements of the planetary gear set 32 and the third planetary gear set 42 are all integrated and rotate together with the input shaft 12, a gear ratio of 1 is obtained.

Fifth speed In the fifth speed, the second clutch means 56 and the third brake means 64 are operated. That is, when shifting from the fourth speed, the second clutch means 56 remains in operation, the first clutch means 54 is deactivated, and the third brake means 64 is activated instead.

As a result, the input shaft 12, the first ring gear 28 and the second
The rotation of the first sun gear 24 and the third sun gear 44 is newly restricted while the ring gear 38 remains connected.

The power input from the input shaft 12 is transferred to the second ring gear 38.
is transmitted to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft 14.

Further, the power manually applied from the input shaft 12 is transmitted from the first ring gear 28 to the first carrier 30 and the second sun gear 34 via the first pinion 26 and the second pinion 27, and from the second sun gear 34 to the third pinion. 36 to the second carrier 40, and from the second carrier 40 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 stops rotating, and the first carrier 30 connects the input shaft 1.
2, the first ring gear 28 rotates in the same direction as the input shaft 12.
It rotates as one. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first carrier 30 in the same direction as the input shaft 12, the second carrier 40 rotates in the same direction as the input shaft 12, and the second sun gear 34 rotates in the same direction as the input shaft 12. ring gear 3
8 rotates together with the first ring gear 28 and the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating, and the third carrier 52
rotates in the same direction as the input shaft 12, and the third ring gear 50 rotates in the same direction as the input shaft 12 together with the second carrier 40.

In this fifth speed, the third planetary gear set 42 does not participate in the gear ratio, and the first planetary gear set 22 and the second planetary gear set 32 shift the speed to (1-ρ1)(
A gear ratio of 1+ρ2)/(1-ρ1+ρ2) is obtained,
In this example, a value of 0.848 is obtained.

Sixth speed In the sixth speed, the second clutch means 56 and the second brake means 62 are operated. That is, when shifting from the fifth speed, the second clutch means 56 remains in operation, the third brake means 64 is deactivated, and the second brake means 62 is activated instead.

As a result, the input shaft 12, the first ring gear 28 and the second
The rotation of the third carrier 52 is newly restricted while the ring gear 38 remains connected.

The power input from the input shaft 12 is transmitted to the second ring gear 38.
is transmitted to the second carrier 40 via the third pinion 36, and from the second carrier 40 to the output shaft 14.

Further, the power input from the input shaft 12 is transmitted from the first ring gear 28 to the first carrier 30 and the second sun gear 34 via the first pinion 26 and the second pinion 27, and from the second sun gear 34 to the third pinion. 2nd through 36
The signal is transmitted to the carrier 40, and from the second carrier 40 to the output shaft 14. Further, a part of the power transmitted to the second carrier 40 is transmitted to the third ring gear 50, and a part of the power transmitted to the second carrier 40 is transmitted to the third ring gear 50.
Transmitted from the ring gear 50 to the third sun gear 44 via the fourth pinion 46, transmitted from the third sun gear 44 to the first sun gear 24 via the first intermediate shaft 16, and transmitted from the first sun gear 24 to the first pinion 26 and the third sun gear 44. It is transmitted to the first carrier 30 via the second pinion 27.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first ring gear 24 rotates in the same direction as the input shaft 12.
8 rotates together with the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first carrier 30 in the same direction as the input shaft 12, the second carrier 40 rotates in the same direction as the input shaft 12, and the second sun gear 34 rotates in the same direction as the input shaft 12. A ring gear 38 rotates together with the first ring gear 28 and the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 stops rotating, and the third ring gear 50 is integrated with the second carrier 40 to rotate the input shaft. It is rotating in the same direction as 12.

In this sixth speed, the first planetary gear set 22, the second
The planetary gear set 32 and the third planetary gear set 42 are involved in the gear ratio, and by them, (ρ3 (
1-ρ1+ρ2)-ρ1ρ2(1+ρ3))/ρ3(1
−ρ1+ρ2), and in this example, 0.5
We have obtained a value of 26.

Reverse (Part 1) In reverse, the third clutch means 58 and the second brake means 62 are operated. Thereby, the input shaft 12 and the first intermediate shaft 16 are connected, and the rotation of the third carrier 52 is restrained.

The power manually applied from the input shaft 12 is transmitted to the third sun gear 44 via the first intermediate shaft 16, and from the third sun gear 44 via the fourth pinion 46 to the third ring gear 50. and is transmitted to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates together with the input shaft 12, and the first carrier 3
0 rotates in the opposite direction to the input shaft 12, and the first ring gear 28
is rotating in the opposite direction to the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first carrier 30 in the opposite direction to the input shaft 12, the second carrier 40 rotates in the opposite direction to the input shaft 12, and the second sun gear 34 rotates in the opposite direction to the input shaft 12. A ring gear 38 rotates integrally with the first ring gear 28 in the opposite direction to the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 is connected to the input shaft 1.
2, the third carrier 52 stops rotating,
The third ring gear 50 rotates together with the second carrier 40 in the opposite direction to the input shaft 12.

In this retraction, the first planetary gear set 22 and the second
The planetary gear set 32 is not involved in the gear ratio and is
The planetary gear set 42 provides a gear ratio of -1/ρ3, which in this embodiment is -2,123.

Reverse (Part 2) In addition, in this embodiment, the reverse can be set to a larger gear ratio, and it can be combined with the aforementioned reverse to create two reverse speeds, or
Either one can be arbitrarily selected.

In this backward movement, the third clutch means 58 and the first brake means 60 are activated. This allows the input shaft 12 and the first
The intermediate shaft 16 is connected, and the first ring gear 28
And the rotation of the second ring gear 38 is restricted.

Power input from the input shaft 12 is transmitted to the first sun gear 24 via the first intermediate shaft 16, and from the first sun gear 24 via the first pinion 26 to the first carrier 30 and the second gear.
The signal is transmitted to the sun gear 34, and from the second sun gear 34 via the third pinion 36 to the second carrier 40, and the second
The signal is transmitted from the carrier 40 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the first intermediate shaft 16 rotates together with the input shaft 12, the first carrier 30 rotates in the opposite direction to the input shaft 12, and the first Ring gear 28 has stopped rotating. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first carrier 30 in the opposite direction to the input shaft 12, the second carrier 40 rotates in the opposite direction to the input shaft 12, and the second sun gear 34 rotates in the opposite direction to the input shaft 12. Ring gear 38 has stopped rotating.

Further, in the third planetary gear set 42, the third sun gear 44 connected to the first intermediate shaft 16 rotates together with the input shaft 12, the third carrier 52 rotates in the same direction as the input shaft 12, and the third ring gear 50 rotates integrally with the second carrier 40 in the opposite direction to the input shaft 12.

In this backward movement, the third planetary gear set 42 does not take part in the transmission ratio, and the first planetary gear set 22 and the second planetary gear set 42
-(1-ρ1) by the planetary gear set 32
A gear ratio of (1+ρ2)/ρ1ρ2 is obtained, and in this example, a numerical value of -5,591 is obtained.

In the gear transmission of the fourth embodiment configured and operated as described above, the desired problem can be solved, and the first sun gear 24 and the third sun gear 44 can be integrated into long pinions. Furthermore, since power circulation does not occur in the frequently used 3rd to 5th gears, efficiency is improved and fuel efficiency is improved.

In the above embodiment, the first clutch means 54 to third clutch means 58 and the first brake means 60 to third brake means 64 as engagement means are all constructed of a single friction single plate type. However, each of the above figures 3 to 11
It is also possible to adopt the configuration described in the figures.

FIG. 16 shows a fifth embodiment as an example, which is provided with engagement means different from that of the fourth embodiment.

In the gear transmission of this fifth embodiment, the first clutch means 54, first brake means 60, second brake means 62, and third brake means 64 have the same construction as in the second embodiment.

Further, FIG. 17 shows a sixth embodiment in which the second invention is applied to a front wheel drive vehicle with a horizontally mounted engine, and in this embodiment, the input shaft 12 is connected to the first. The third clutch means 58 is passed inside the intermediate shaft 16, and the position of the third clutch means 58 is accordingly changed.

In the case of this embodiment as well, the engaging means can be configured as described above.

[Effect of the invention] As explained above, the gear transmission according to the present invention has two
When combining one set of simple planetary gear sets and one set of double pinion simple planetary gear sets to establish a gear stage of five or more forward gears, the gear ratio in the normal forward gears excluding overdrive becomes an arrangement close to a geometric series, The overdrive gear ratio can ensure power performance, the gear ratio of each planetary gear set is appropriate, the outer diameter of the gear train can be made small, and the gear shift to the next gear can be done by controlling the two engagement elements. It has the following effect.

[Brief explanation of drawings]

Fig. 1 is a skeleton diagram showing a first embodiment of the gear transmission according to the present invention, Fig. 2 is a table showing the operating status of the engagement means in the first embodiment, and Figs. 12 is a skeleton diagram showing a second embodiment, FIG. 13 is a skeleton diagram showing a third embodiment, and FIG. 14 is a skeleton diagram showing a fourth embodiment of the present invention. , 1st
5 is a table showing the operating status of the engaging means in the fourth embodiment, FIG. 16 is a skeleton diagram showing the fifth embodiment, and 1T.
The figure is a skeleton diagram showing the sixth embodiment. 12...Input shaft, 14...Output shaft, 22...First
Planetary gear set, 24...first sun gear, 26
... 1st binion, 27... 2nd binion, 28.
...First ring gear, 30...First carrier, 32.
...Second planetary gear set, 34...Second sun gear, 36...Third pinion, 38...Second ring gear, 40...Second carrier, 42...Third planetary gear set, 44... ... Third sun gear, 46... Fourth pinion, 50... Third ring gear, 52... Third carrier, 54... First clutch means, 56...
Second clutch means, 58...Third clutch means, 60
...first brake means, 62...second brake means, 64...third brake means. Figure 1 Figure 42 Figure Figure Figure 6 Figure A Figure Figure Figure 10 Figure Figure Figure 1 Dodori O Do9 Dod Leather Figure Figure

Claims (2)

[Claims] (1) An input shaft rotatably supported with respect to the housing case, an output shaft rotatably supported with respect to the housing case, a first sun gear rotatably supported with respect to the housing case, and a first sun gear rotatably supported with respect to the housing case. The first carrier rotatably supports a first pinion that meshes with the sun gear and a second pinion that meshes with the first pinion and is rotatably arranged with respect to the storage case, and is arranged coaxially with the first sun gear. A first planetary gear set consisting of a double pinion simple planetary gear set in combination with a first ring gear that is rotatably arranged with respect to the housing case and meshes with a second pinion, and a second planetary gear set that is rotatably supported with respect to the housing case. A second pinion that rotatably supports a sun gear and a third pinion meshing with the second sun gear and is rotatably arranged with respect to the storage case.
a second planetary gear set that is a simple planetary gear set that is a combination of a carrier and a second ring gear that is coaxially disposed on the second sun gear and rotatably disposed relative to the housing case and meshes with the third pinion;
The third planetary gear set includes a simple planetary gear set having the same combination as the second planetary gear set, first to third clutch means, and first to third brake means, and includes a first sun gear and a second sun gear. and third
The sun gear is connected, the first carrier and the second ring gear are connected, the second carrier, the third ring gear and the output shaft are connected, and the first clutch means connects the input shaft to the first carrier and the second ring gear. The second clutch means is arranged so that the input shaft can be coupled to the first ring gear, and the third clutch means is arranged so that the input shaft can be coupled to the first sun gear, the second sun gear, and the third sun gear. , the first brake means is arranged so as to be able to restrain the first ring gear with respect to the housing case, the second brake means is arranged so that the third carrier can be restrained with respect to the housing case, and the third brake means is arranged so as to be able to restrain the first ring gear with respect to the housing case. A gear transmission characterized in that a second sun gear and a third sun gear are arranged such that they can be restrained with respect to a housing case. (2) An input shaft rotatably supported with respect to the housing case, an output shaft rotatably supported with respect to the housing case, a first sun gear rotatably supported with respect to the housing case, and a first sun gear rotatably supported with respect to the housing case. The first carrier rotatably supports a first pinion that meshes with the sun gear and a second pinion that meshes with the first pinion and is rotatably arranged with respect to the storage case, and is arranged coaxially with the first sun gear. A first planetary gear set consisting of a double pinion simple planetary gear set in combination with a first ring gear that is rotatably arranged with respect to the housing case and meshes with a second pinion, and a second planetary gear set that is rotatably supported with respect to the housing case. A second pinion that rotatably supports a sun gear and a third pinion meshing with the second sun gear and is rotatably arranged with respect to the storage case.
a second planetary gear set consisting of a simple planetary gear set in combination with a carrier and a second ring gear that is coaxially disposed on the second sun gear and rotatably disposed relative to the housing case and meshes with the third pinion;
The third planetary gear set includes a simple planetary gear set having the same combination as the second planetary gear set, first to third clutch means, and first to third brake means, and includes a first sun gear and a third sun gear. are connected, the first carrier and the second sun gear are connected, the first ring gear and the second ring gear are connected, the second carrier, the third ring gear and the output shaft are connected, and the first clutch means is connected to the input shaft. The shaft is arranged to be connectable to the first carrier and the second sun gear, the second clutch means is arranged to be able to connect the input shaft to the first ring gear and the second ring gear, and the third clutch means is arranged to connect the input shaft to the first ring gear. The first brake means is arranged to be connectable to the sun gear and the third sun gear, the first brake means is arranged to be able to restrain the first ring gear and the second ring gear to the housing case, and the second brake means is arranged to connect the third carrier to the housing case. A gear transmission characterized in that the third brake means is arranged such that the first sun gear and the third sun gear can be restrained with respect to the housing case.