JPH02118247A - Gear speed change gear - Google Patents

Abstract

PURPOSE:To obtain the speed change stages of above five advancing stages by placing simple type first, double pinion type second, and simple type third planetary gear sets in order and selectively operating first to third clutches and brakes. CONSTITUTION:Simple type first, double pinion type second, and simple type third planetary gear sets 22, 32, 42 are placed coaxially with input/output shafts 12, 14, and a first ring gear 28 is linked to second and third carriers 40, 52, while linking first and second sun gears 24, 34 together, and second and third ring gears 38, 50 to an output gear 15. 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 simple 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 and a first pinion that meshes with the first sun gear rotatably supported and coaxial with the first carrier and the first sun gear which are rotatably arranged with respect to the storage case. a first planetary gear set consisting of a simple planetary gear set in combination with a first ring gear which is disposed symmetrically and is rotatably arranged with respect to the housing case and meshes with the first pinion; and a first planetary gear set that is rotatably supported with respect to the housing case. A second carrier and a second sun gear that rotatably support a second sun gear, a second pinion that meshes with the second sun gear, and a third pinion that meshes with the second pinion, and are rotatably arranged with respect to the storage case. a second planetary gear set consisting of a double pinion simple planetary gear set in combination with a second ring gear arranged coaxially with the storage case and rotatably arranged with respect to the housing case and meshing with the third pinion; and a first planetary gear set. A third planetary gear set consisting of a simple planetary gear set of a similar combination, first to third clutch means, and first to third brake means, the first sun gear and the second sun gear are connected, The first ring gear, the second carrier, and the third carrier are connected, the second ring gear, 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 sun gear and the second sun gear. The second clutch means is arranged to connect the input shaft to the first carrier, the third clutch means is arranged to connect the input shaft to the third sun gear, and the first brake means accommodates the first carrier. The second brake means is arranged to be able to restrain the first ring gear, the second carrier, and the third carrier relative to the housing case, and the third brake means is configured to restrain the third sun gear from the housing case. It is arranged so that it can be restrained against.

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 rotatably supporting a first pinion meshing with the first sun gear and rotatably disposed relative to the accommodation case; a first planetary gear set consisting of a simple planetary gear set in combination with a first ring gear that is rotatably disposed relative to the first ring gear and meshes with the first pinion; a second sun gear that is rotatably supported with respect to the housing case; A second carrier that rotatably supports a second pinion that meshes with the second pinion and a third pinion that meshes with the second pinion and is rotatably arranged with respect to the storage case and a second sun gear that is coaxially arranged and accommodated. a second planetary gear set consisting of a double pinion simple planetary gear set in combination with a second ring gear that is rotatably arranged with respect to the case and meshing with a third pinion; and a simple planetary gear set in the same combination as the first planetary gear set. a third planetary gear set, first to third clutch means, and first to third brake means, the first sun gear, the second sun gear, and the third ring gear are connected;
The first ring gear and the second carrier are connected, the second ring gear, the third carrier and the output shaft are connected, and the first clutch means connects the input shaft to the first sun gear, the second sun gear and the third sun gear.
The second clutch means is arranged so as to be able to connect the input shaft to the first carrier, the third clutch means is arranged so as to be able to connect the input shaft to the third sun gear, and the first brake means is arranged so as to be able to connect the input shaft to the third sun gear. The first carrier is arranged so as to be able to be restrained with respect to the accommodation case, the second brake means is arranged so that the first ring gear and the second carrier can be restrained with respect to the accommodation case, and the third brake means is arranged so that the first carrier can be restrained with respect to the accommodation case. It is arranged so that it can be restrained against.

[Operation] In the first and second inventions serving as the above means, 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] Fig. 1 shows a first embodiment of the gear transmission of the first invention.
The embodiment is shown in a skeleton diagram with the lower half omitted.

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

) contains the components.

The input shaft 12 serving as the input end is connected to the transmission case 1
0, and this input shaft 12
A first intermediate shaft 16 is arranged adjacent to and coaxially with the input shaft 12 in a straight line. The first intermediate shaft 16 is rotatably supported on the transmission case 10. Outside the first intermediate shaft 16, a second intermediate shaft 18 and an output shaft 14 serving as an output end are arranged in order from the side closest to the input shaft 12, and each is arranged in a transmission case independently of the first intermediate shaft 16. 10. An output gear 15 is fixed to the output shaft 14.

The first planetary gear set 22 includes a first sun gear 24 that is concentrically fixed to the second intermediate shaft 18, and a first sun gear 24 that is concentrically fixed to the second intermediate shaft 18.
4, a first ring gear 28 that meshes with the first pinion 26, and a first ring gear 28 that meshes with the first pinion 26.
6 and a first carrier 30 that rotatably supports the gear. 1st ring gear 2
8 and 11 carriers 30 are transmission case 1
It is arranged rotatably with respect to 0.

The second planetary gear set 32 includes a second sun gear 34 concentrically fixed to the second intermediate shaft 18, and a second sun gear 34 fixed to the second intermediate shaft 18.
4, a plurality of third pinions 37 that mesh with the second pinion 36, a second ring gear 38 that meshes with the third pinion 37, and a second pinion 36 and a third pinion 37. This is a double pinion simple planetary gear set including a second carrier 40 rotatably supported. The second ring gear 38 and the second carrier 40 are rotatably arranged with respect to the transmission case 10.

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;
This is a simple planetary gear set including a third carrier 52 that rotatably supports the gear 6. 3rd ring gear 5
0 and the third carrier 52 are the transmission case l
It is arranged rotatably with respect to O.

Here, the first ring gear 28, the second carrier 40 and the third
It is connected to the carrier 52 so that they rotate together. In addition, the second ring gear 38 and the third ring gear 50
and the output shaft 14 are connected to rotate together.

The first clutch means 54 is arranged to connect the input shaft 12 and the second intermediate shaft 18. The second clutch means 56 is arranged to connect the input shaft 12 and the first carrier 30. The third clutch means 58 is arranged to connect the input shaft 12 and the first intermediate shaft 16. 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 carrier 30 against rotation with respect to the transmission case IO. The second brake means 62 is arranged so as to be able to restrain the first ring gear 28, the second carrier 40, and the third carrier 52 in a non-rotatable manner relative to the transmission case IO. The third brake means 64
The third sun gear 44 is arranged so as to be non-rotatable via the intermediate shaft 16. 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 ρl of 0.317, the second planetary gear set 32 has a gear ratio ρ2 of 0.458, and the third planetary gear set 42 has a gear ratio ρ3 of 0.317. 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 (O 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 and the second intermediate shaft 18 are connected, and the rotation of the first carrier 30 is restrained.

The power input from the input shaft 12 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and is transmitted from the second sun gear 34 to the second sun gear 34 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

Further, a part of the power transmitted to the second sun gear 34 is transmitted to the second carrier 40 and the first ring gear 28 via the second pinion 36 and the third pinion 37, and from the first ring gear 28 to the first pinion 26. from the first sun gear 24 to the second intermediate shaft 18
is transmitted to the second sun gear 34 via.

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 stops rotating, and the first ring gear 28 rotates together with the input shaft 12. 12 and is rotating in the opposite direction. Further, in the second planetary gear set 32, the second intermediate shaft 1
The second sun gear 34 connected to the input shaft 12 rotates together with the first sun gear 24, and the second carrier 40 rotates together with the first ring gear 28 in the opposite direction to the input shaft 12. A ring gear 38 is rotating 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 rotates together with the first ring gear 28 and the second carrier 40 in the opposite direction to the input shaft 12, and the third ring gear 50 rotates together with the second ring gear 38 in the same direction as the input shaft 12. It's rotating.

In this first speed, the third planetary gear set 42 is not involved in the speed change ratio, and the first planetary gear set 22 and the second planetary gear set 32 have a ratio of 1/(ρ2−ρ
A gear ratio of l+ρlρ2) is obtained, which is 3.4 in this example.
I got a value of 94.

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 and the second intermediate shaft 18 remain connected, and the rotation of the first ring gear 28, the second carrier 40, and the third carrier 52 is newly restrained.

The power input from the input shaft 12 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and is transmitted from the second sun gear 34 to the second sun gear 34 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first Ring gear 28 has stopped rotating. Further, in the second planetary gear set 32, the second intermediate shaft 1
The second sun gear 34 connected to the input shaft 12 rotates together with the first sun gear 24, the second carrier 40 stops rotating, and the second ring gear 38 rotates in the same direction as the input shaft 12. . Also, the third planetary gear set 4
2, 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 together with the second ring gear 38 in the same direction as the input shaft 12. are doing.

In this second 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 in this embodiment is 2.123. are 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 hand 64 is activated instead.

As a result, the input shaft 12 and the second intermediate shaft 18 remain connected, and the rotation of the third sun gear 44 is newly restricted.

The power input from the input shaft 12 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and is transmitted from the second sun gear 34 to the second sun gear 34 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

Further, a part of the power transmitted to the second ring gear 38 is
The signal is transmitted to the third ring gear 50 from the third ring gear 50 via the fourth pinion 46 to the third carrier 52 and the second
The signal is transmitted to the carrier 40 , and from the second carrier 40 to the second ring gear 38 via the second pinion 36 and the third pinion 37 .

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first A 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 connected to the second intermediate shaft 18 is connected to the first
It rotates together with the sun gear 24 and the input shaft 12, and the second
The carrier 40 rotates together with the first ring gear 28 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. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating,
The third carrier 52 rotates together with the first ring gear 28 and the second carrier 40 in the same direction as the input shaft 12, and the third ring gear 50 rotates together with the second ring gear 38 in the same direction as the input shaft 12. It's rotating.

In this third speed, the first planetary gear set 22 does not participate in the gear ratio, and the second planetary gear set 32 and the third planetary gear set 42 shift the gear ratio to (ρ2+ρ3).
/ρ2(1+ρ3) is obtained, and in this example, 1
．． A numerical value of 3'79 was 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 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 carrier 30 are newly connected, while the input shaft 12 and the second intermediate shaft 18 remain connected.

The power input from the input shaft 12 via the first clutch means 54 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and from the second sun gear 34 via the second pinion 36 and third pinion 37. The signal is transmitted to the second ring gear 38 , and from the second ring gear 38 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 carrier 30, and from the first carrier 30 via the first pinion 26, the power is transmitted to the first ring gear 28.
and is transmitted to the second carrier 40 from the second carrier 40 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

Further, a part of the power transmitted to the first carrier 30 is transmitted to the first sun gear 24 via the first pinion 26,
The signal is transmitted from the first sun gear 24 to the second sun gear 34 via the second intermediate shaft 18, and from the second sun gear 34 to the output shaft 14 in the same manner as described above.

At this time, in the first planetary gear set 22, the first sun gear 24, first carrier 30, and first ring gear 28 are all rotating together with the input shaft I2. Further, in the second planetary gear set 32, the second sun gear 34, second carrier 40, and second ring gear 38 all rotate together with the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44, the third carrier 52, and the third ring gear 50 all rotate 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 carrier 30 remain connected, and the rotation of the third sun gear 44 is newly restricted.

The power input from the input shaft 12 is transmitted to the first carrier 30, from the first carrier 30 via the first pinion 26 to the first sun gear 24, and from the first sun gear 24 via the second intermediate shaft 18. from the second sun gear 34 to the second ring gear 38 via the second pinion 36 and third pinion 37.
The signal is transmitted from the ring gear 38 to the output shaft 14. Further, a part of the power transmitted to the first carrier 30 is transmitted to the first ring gear 28 and the second carrier 40 via the first pinion 26.
and is transmitted to the third carrier 52 , from the third carrier 52 via the fourth pinion 46 to the third ring gear 50 , and from the third ring gear 50 to the output shaft 14 . In addition, a part of the power transmitted to the second carrier 40 is
The signal is transmitted to the second ring gear 38 via the second pinion 36 and the third pinion 37, and then to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the same direction as 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 integrally with the first sun gear 24 in the same direction as the input shaft 12, and the second carrier 40 rotates integrally with the first ring gear 28, rotating the input shaft 12 integrally with the first ring gear 28. The second ring gear 38 is rotating 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 is connected to the first ring gear 28 and the second ring gear.
The third ring gear 50 rotates together with the carrier 40 in the same direction as the input shaft 12, and the third ring gear 50 rotates together with the second ring gear 38 in the same direction as the input shaft 12.

In this fifth 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, (ρ2 (
1+ρ1)+ρ1p3)/ρ2 (1+ρ1)(1+ρ
3) is obtained, and in this example, a numerical 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 activated, the third brake means 640 is deactivated, and the second brake means 62 is activated instead.

As a result, the input shaft 12 and the first carrier 30 remain connected, and the first U puffer gear 28 and the second carrier 4 are newly connected.
The rotation of the zero and third carriers 52 is restricted.

The power manually applied from the input shaft 12 is transmitted from the first carrier 30 to the first sun gear 24 via the first pinion 26 , and from the first sun gear 24 to the second intermediate shaft 18 via the second intermediate shaft 18 .
from the second sun gear 34 to the second ring gear 38 via the second pinion 36 and third pinion 37, and from the second ring gear 38 to the output shaft 14.
transmitted to.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the same direction as 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 first sun gear 24 in the same direction as the input shaft 12, the second carrier 40 stops rotating, and the second ring gear 38 rotates in the same direction as the input shaft 12. 12
is rotating in the same direction. 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 ring gear 38 to rotate the input shaft. It is rotating in the same direction as 12.

In this sixth 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 control the speed ratio ρ1/ρ2(1
+ρ1) 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 first ring gear 28, the second carrier 40, and 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 rotates in the opposite direction to the input shaft 12, the first carrier 30 rotates in the opposite direction to the input shaft 12, and the first ring gear 24 rotates in the opposite direction to the input shaft 12.
8 has stopped rotating. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first sun gear 24 in the opposite direction to the input shaft 12, the second carrier 40 stops rotating, and the second ring gear 38 rotates in the opposite direction to the input shaft 12. 1
It is rotating in the opposite direction to 2. 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, and the third carrier 5
2 has stopped rotating, and the third ring gear 50 is rotating together with the second ring gear 38 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 hand 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 carrier 30 is restrained from rotating.

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. In addition, a part of the power transmitted to the third sun gear 44 is
The signal is transmitted via the fourth pinion 46 to the third carrier 52 and the first ring gear 28, and from the first ring gear 28 via the first pinion 26 to the first sun gear 24.
The signal is transmitted from the sun gear 24 to the second sun gear 34 via the second intermediate shaft 18, and from the second sun gear 34 to the second pinion 3.
6 and the third pinion 37 to the second ring gear 38 , and from the second ring gear 38 to the output shaft 14 . Further, a part of the power transmitted to the second sun gear 34 is transmitted to the second carrier 40 via the second pinion 36 and the third pinion 37, and then transmitted to the first ring gear 28.

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 stops rotating, and the first U blow gear 28 rotates in the opposite direction to the input shaft 12.
It is rotating in the same direction as 2. Further, in the second planetary gear set 32, the second sun gear 34 is connected to the first sun gear 24.
The second carrier 40 rotates integrally with the first ring gear 28 in the opposite direction to the input shaft 12, and the second carrier 40 rotates integrally with the first ring gear 28, rotating the input shaft 12 in the opposite direction.
2, the second ring gear 38 rotates in the same direction as the input shaft 12.
is rotating in the opposite direction. Further, in the third planetary gear set 42, a third sun gear 44 connected to the first intermediate shaft 16 rotates together with the input shaft 12, and the third carrier 52
rotates in the same direction as the input shaft 12 together with the first ring gear 28 and the second carrier 40, and the third ring gear 50 rotates in the same direction as the input shaft 12.
rotates in the opposite direction to the input shaft 12 together with the second ring gear 38 .

In this reversing, the first planetary gear set 22, the second planetary gear set 32, and the third planetary gear set 42 are involved in the gear ratio, so that -(ρ2
(1+ρ1)+ρlρ3)/ρ3(ρ2-ρ1+ρlρ
2) is obtained, and in this example, a numerical value of -5,583 is obtained.

The gear transmission of the first embodiment configured and operated as described above can solve the desired problem, and also has good efficiency and low fuel consumption because power circulation does not occur between the 4th and 6th speeds. It has the advantage of improving. Also, the first sun gear 2
4 and the second sun gear 34 can be integrated into a long pinion, and the second planetary gear set 32 and the third planetary gear set 42 can be combined as shown in FIG. 11, which will be described later. The structure can also be simplified.

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 can 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 second intermediate shaft 18. .

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 second intermediate shaft 18 to the input shaft 12, so the engine brake is released, improving fuel efficiency and quietness. It has the advantage of improving performance.

In addition, when shifting between 1st to 4th speeds and 5th or 6th speed, the second intermediate shaft 1
8 rotates faster than the input shaft 2, and in 1st to 4th speeds, the second intermediate shaft 18 is at the same speed as or less than the same speed as the input shaft 12, so when shifting up, it is a one-way The first clutch means 54 is automatically released from operation by the action of the clutch 68, and when downshifting, the rotation of the second intermediate shaft 18 and input shaft 12 are synchronized before the first clutch means 54 is activated. Shift shock can be suppressed without precisely setting the timing for starting or disengaging the clutch means 54, and shift control becomes easy.

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 shown in FIG. 3, and by selectively operating the multi-disc clutch 70, engine braking can be applied as necessary, such as when exiting the vehicle.

The second clutch means 56 can have a configuration similar to that shown in FIGS. 3 and 4 above, and in the fourth, fifth and sixth speeds in which the second clutch means 56 is in the operating state. The engine brake is released, improving fuel efficiency and quietness, and depending on the configuration, the engine brake can be applied as needed.

The third clutch means 58 has the same structure as shown in FIGS. 3 and 4, and includes a multi-disc clutch 66 and a one-way clutch 68 connected in series as shown in FIG. A one-way clutch 72 whose engagement direction is opposite to the above 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, in the first gear and reverse (part 2) when the first brake means 60 operates, fuel efficiency and quietness are improved, 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, 10, 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, 5th speed, and 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 configuration shown in FIG. 4, the first brake means 60 has the configuration shown in FIG. 3, and the second clutch means 54 has the configuration 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, as described above, the second planetary gear set 32
The third planetary gear set 42 has a combined structure.

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 first intermediate shaft 16 and the second intermediate shaft 18 are arranged apart from each other in the axial direction, and the input shaft 12 is passed inside these intermediate shafts 16 and 18, and accordingly, the third clutch The arrangement position of the means 58 has been changed. 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).

) contains the components.

The input shaft 12 serving as the input end is connected to the transmission case 1
0, and this input shaft I2
A first intermediate shaft 16 is arranged adjacent to and coaxially with the input shaft 12 in a straight line. The first middle 1'lJj shaft 16 is rotatably supported on the transmission case IO. Outside the first intermediate shaft 16, in order from the side closest to the input shaft 12, a second intermediate shaft 18 and an output shaft 14 serving as an output end are arranged.
are arranged, and each is rotatably supported with respect to the transmission case 10 independently of the first intermediate shaft 16. An output gear 15 is fixed to the output shaft 14.

The first planetary gear set 22 has a first sun gear 24 fixed concentrically to the second intermediate shaft 18, and is constructed of the same combination as in the first embodiment. The second planetary gear set 32 has a second sun gear 34 fixed concentrically to the second intermediate shaft 18, and is constructed of the same combination as in 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 ring gear 28 and the second carrier 40 are connected to rotate together.

Further, the second ring gear 38, the third carrier 52, and the output shaft 14 are connected to rotate together. Further, the third ring gear 50 is connected to the second intermediate shaft 18 and rotates integrally with the first sun gear 24 and the second sun gear 34.

The first clutch means 54 is arranged to connect the input shaft 12 and the second intermediate shaft 18. The second clutch means 56 is arranged so as to be able to connect the input shaft 12 to the first carrier 30. The third clutch means 58 is arranged to connect the input shaft 12 and the first intermediate shaft 16. 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 carrier 30 against rotation with respect to the transmission case 10. The second brake means 62 is arranged so as to be able to restrain the first ring gear 28 and the first carrier 30 against rotation with respect to the transmission case 10. The third brake means 64 is arranged so as to be able to restrain the third sun gear 44 non-rotatably with respect to the transmission case 10 via the first intermediate shaft 16.

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 0.317, the second planetary gear set 32 has a gear ratio ρ2 of 0.458, and the third planetary gear set 42 has a gear ratio ρ3 of 0. It is .379.

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. 15 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 640 (○ 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 and the second intermediate shaft 18 are connected, and the rotation of the first carrier 30 is restrained.

The power input from the input shaft 12 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and is transmitted from the second sun gear 34 to the second sun gear 34 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

Further, a part of the power transmitted to the second sun gear 34 is transmitted to the second carrier 40 and the first ring gear 28 via the second pinion 36 and the third pinion 37, and from the first ring gear 28 to the first pinion 26. from the first sun gear 24 to the second intermediate shaft 18
is transmitted to the second sun gear 34 via.

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 stops rotating, and the first ring gear 28 rotates together with the input shaft 12. 12 and is rotating in the opposite direction. Further, in the second planetary gear set 32, the second intermediate shaft 1
The second sun gear 34 connected to the input shaft 12 rotates together with the first sun gear 24, and the second carrier 40 rotates together with the first ring gear 28 in the opposite direction to the input shaft 12. A ring gear 38 is rotating 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 rotates together with the second ring gear 38 in the same direction as the input shaft 12 , and the third ring gear 50 rotates together with the first sun gear 24 and the second sun gear 34 on the input shaft 12 .
It rotates together with 2.

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 are used to set l/(ρ2-ρ
A gear ratio of l+ρlρ2) is obtained, which is 3.4 in this example.
I got a value of 94.

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 rotation of the first ring gear 28 and the second carrier 40 is newly restrained while the input shaft 12 and the second intermediate shaft 18 remain connected.

The power manually applied from the input shaft 12 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and is transmitted from the second sun gear 34 to the second sun gear 34 via the second pinion 36 and the third pinion 37.
The signal is transmitted to the ring gear 38 , and from the second ring gear 38 to the output shaft 14 .

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first Ring gear 28 has stopped rotating. Further, in the second planetary gear set 32, the second intermediate shaft 1
The second sun gear 34 connected to the input shaft 12 rotates together with the first sun gear 24, the second carrier 4o stops rotating, and the second ring gear 38 rotates in the same direction as the input shaft 12. . Also, the third planetary gear set 4
2, the third sun gear 44 rotates in the opposite direction to the input shaft 12, the third carrier 52 rotates together with the second ring gear 38 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.
is rotating together with the input shaft 12 together with the first sun gear 24 and the second sun gear 34 .

In this second 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 2.183 in this embodiment. are 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 input shaft 12 and the second intermediate shaft 18 remain connected, and the rotation of the third sun gear 44 is newly restricted.

The power input from the input shaft 12 is transmitted to the third ring gear 50 via the second intermediate shaft 18, and
0 to the third carrier 52 via the fourth pinion 46, and from the third carrier 52 to the output shaft 14.

At this time, in the first planetary gear set 22, the first sun gear 24 connected to the second intermediate shaft 18 rotates together with the input shaft 12, the first carrier 30 rotates in the same direction as the input shaft 12, and the first A 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 connected to the second intermediate shaft 18 is connected to the first
It rotates together with the sun gear 24 and the input shaft 12, and the second
The carrier 40 rotates together with the first ring gear 28 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. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating,
The third carrier 52 rotates together with the second ring gear 38 in the same direction as the input shaft 12 , and the third ring gear 50 rotates together with the first sun gear 24 and the second sun gear 34 on the input shaft 12 .
It rotates together with 2.

In this third speed, the first planetary gear set 22 and the second planetary gear set 32 are not involved in the gear ratio, and the third planetary gear set 42 provides a gear ratio of ■+ρ3, which is 1.379 in this embodiment. We're getting numbers.

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 activated, the third brake means 640 is deactivated, and the second clutch means 56 is activated instead.

As a result, the first carrier 30 is newly connected to the input shaft 12 while the input shaft 12 and the second intermediate shaft 18 remain connected.

The power input from the input shaft 12 via the first clutch means 54 is transmitted to the second sun gear 34 via the second intermediate shaft 18, and from the second sun gear 34 via the second pinion 36 and third pinion 37. The signal is transmitted to the second ring gear 38 , and from the second ring gear 38 to the output shaft 14 . Further, the power manually applied via the second clutch means 56 is transferred to the first clutch means 56.
The signal is transmitted to the carrier 30 from the first carrier 30 via the first pinion 26 to the first IJ songr 28 and the second
from the second carrier 40 to the second ring gear 38 via the second pinion 36 and third pinion 37, and from the second ring gear 38 to the output shaft 14.
transmitted to. Further, a part of the power transmitted to the first carrier 30 is transmitted to the first sun gear 2 via the first pinion 26.
4, from the first sun gear 24 to the second sun gear 34 via the second intermediate shaft 18, and from the first sun gear 24 to the second sun gear 34 via the second intermediate shaft 18.
is transmitted to the output shaft 14 in the same manner as described above.

At this time, in the first planetary gear set 22, the first sun gear 24, first carrier 30, and first ring gear 28 are all rotating together with the input shaft 12. Further, in the second planetary gear set 32, the second sun gear 34, second carrier 40, and second ring gear 38 all rotate together with the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44, the third carrier 52, and the third ring gear 50 all rotate 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 l can be 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 carrier 30 remain connected, and the third sun gear 44 is newly connected.
is restricted from rotation.

The power input from the input shaft 12 is transmitted to the first carrier 30, from the first carrier 30 via the first pinion 26 to the first sun gear 24, and from the first sun gear 24 via the second intermediate shaft 18. from the second sun gear 34 to the second ring gear 38 via the second pinion 36 and third pinion 37.
The signal is transmitted from the ring gear 38 to the output shaft 14. Further, a part of the power transmitted to the first carrier 30 is transmitted to the first ring gear 28 and the second carrier 4 via the first pinion 26.
0 from the second carrier 40 to the second pinion 36
and is transmitted to the second ring gear 38 via the third pinion 37, and from the second ring gear 38 to the output shaft 14. Further, a part of the power transmitted to the second U puffer gear 38 is transmitted to the third carrier 52.
is transmitted to the third ring gear 50 via the fourth pinion 46, from the third ring gear 50 to the second sun gear 34 via the second intermediate shaft 18, and from the second sun gear 34 to the second pinion 36 and the third pinion. 37 to the second ring gear 38.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the same direction as 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 integrally with the first sun gear 24 in the same direction as the input shaft 12, and the second carrier 40 rotates integrally with the first ring gear 28, rotating the input shaft 12 integrally with the first ring gear 28. The second ring gear 38 is rotating in the same direction as the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 44 stops rotating, the third gear rear 52 rotates together with the second ring gear 38 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. It rotates in the same direction as the input shaft 12 together with the first sun gear 24 and the second sun gear 34 .

In this fifth 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, ((1+ρ
1) (l-ρ2-ρ2ρ3)+ρ1p3)/(1+ρ
1) A gear ratio of (l-ρ2) is obtained, and in this example, the gear ratio is 0.
A value of 848 was 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 and the first carrier 30 remain connected, and the first ring gear 28 and the second carrier 4 are newly connected.
0 is restricted from rotation.

The power input from the input shaft 12 is transmitted from the first carrier 30 to the first sun gear 24 via the first pinion 26, and from the first sun gear 24 to the second intermediate shaft 18.
from the second sun gear 34 to the second ring gear 38 via the second pinion 36 and third pinion 37, and from the second ring gear 38 to the output shaft 14.
transmitted to.

At this time, in the first planetary gear set 22, the first sun gear 24 rotates in the same direction as 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 first sun gear 24 in the same direction as the input shaft 12, the second carrier 40 stops rotating, and the second ring gear 38 rotates in the same direction as the input shaft 12. 12
is rotating in the same direction. 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 together with the second ring gear 38 in the same direction as the input shaft 12, and the third A ring gear 50 rotates together with the first sun gear 24 and the second sun gear 34 in the same direction as the input shaft 12 .

In this sixth 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 control the speed ratio ρ1/ρ2(1
+ρl) is obtained, and in this example, a numerical value of 0.526 is obtained.

Reverse l) In reverse, the third clutch means 58 and the second brake means 62 are activated. Thereby, the input shaft 12 and the first intermediate shaft 16 are connected, and the rotation of the first ring gear 28 and the second carrier 40 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. is transmitted from the second sun gear 34 to the second ring gear 38 via the second intermediate shaft 18 and the third pinion 37, and from the second ring gear 38 to the output shaft 14. transmitted to. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the third carrier 52, and a part of the power transmitted to the second ring gear 38 is transmitted to the third carrier 52.
The signal is transmitted from the carrier 52 to the third ring gear 50 via the fourth pinion 46 .

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 opposite direction to the input shaft 12, and the first ring gear 24 rotates in the opposite direction to the input shaft 12.
8 has stopped rotating. Further, in the second planetary gear set 32, the second sun gear 34 rotates together with the first sun gear 24 in the opposite direction to the input shaft 12, the second carrier 40 stops rotating, and the second ring gear 38 rotates in the opposite direction to the input shaft 12. 1
It is rotating in the opposite direction to 2. 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, and the third carrier 5
2 rotates in the opposite direction to the input shaft 12 integrally with the second ring gear 38, and the third ring gear 50 rotates in the opposite direction to the input shaft 12.
The second sun gear 34 rotates in the opposite direction to the input shaft 12 .

In this backward movement, the first planetary gear set 22 does not take part in the transmission ratio, and the second planetary gear set 32 and the third planetary gear set 32
By the planetary gear set 42, -(1-ρ2-ρ
2ρ3)/ρ2ρ3 is obtained, and in this example -
A numerical value of 2,122 was obtained.

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 carrier 30 is restrained from rotating.

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 to the third ring and gear 50 via the fourth pinion 46. The signal is transmitted from the ring gear 50 to the second sun gear 34 via the second intermediate shaft 18 , and from the second sun gear 34 to the second ring gear 38 via the second pinion 36 and third pinion 37 , and the output from the second ring gear 38 is transmitted to the shaft 14. Further, a part of the power transmitted to the second sun gear 34 is transmitted to the second carrier 40 and the first ring gear 28 via the second pinion 36 and the third pinion 37.
from the first ring gear 28 to the first pinion 26
is transmitted to the first sun gear 24 via the first sun gear 24.
4 to the second sun gear 34 via the second intermediate shaft 18. Further, a part of the power transmitted to the second ring gear 38 is transmitted to the third carrier 52, and a part of the power transmitted to the second ring gear 38 is transmitted to the third carrier 52.
2 to the third ring gear 50 via the fourth pinion 46, and from the third ring gear 50 to the second sun gear 34 via the second intermediate shaft 18.

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 stops rotating, and the first ring gear 28 rotates in the opposite direction to the input shaft 12.
is rotating in the same direction. Further, in the second planetary gear set 32, the second sun gear 34 rotates integrally with the first sun gear 24 in the opposite direction to the input shaft 12, and the second carrier 40 rotates integrally with the first ring gear 28, rotating the input shaft 12 integrally with the second carrier 40.
The second ring gear 38 rotates in the opposite direction to the input shaft 12. Further, in the third planetary gear set 42, the third sun gear 4 connected to the first intermediate shaft 16 is connected to the third planetary gear set 42.
4 rotates together with the input shaft 12, the third carrier 52 rotates together with the second ring gear 38 in the opposite direction to the input shaft 12, and the third ring gear 50 rotates together with the first sun gear 24 and the second sun gear 34. They rotate together in the opposite direction to the input shaft 12.

In this reversing, the first planetary gear set 22, the second planetary gear set 32, and the third planetary gear set 42 are involved in the gear ratio, so that -((l+ρ)
l) (1-ρ2-ρ2ρ3)+ρ1ρ3)/ρ3(
A gear ratio of ρ2-ρ1+ρ1ρ2) is obtained, and in this example, a numerical value of -5,581 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 second sun gear 34 can be integrated into a long pinion. can.

In the above embodiment, the first clutch means 54 to third clutch means 58 and the first brake hand 60 to third brake hand 64 as engagement means are all of a single friction single plate type. 3 to 11, respectively.
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 installed engine, and in this embodiment, the first intermediate shaft 16 and the second intermediate shaft 18 are The input shaft 12 passes inside these intermediate shafts 16, 18, which are arranged axially apart. Further, in accordance with this, the arrangement position of the third clutch means 58 has been 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
Forward movement by combining one set of simple planetary gear set and one set of double pinion simple planetary gear set
When establishing gears higher than 1.5, the gear ratios in normal forward gears except for overdrive are arranged in an arrangement close to a geometric series, and the gear ratio of overdrive can ensure power performance, and the gears of each planetary gear set are The ratio is appropriate, the outer diameter of the gear train can be made small, and the gear can be shifted to the next gear by controlling the two engagement elements.

[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 diagram showing the operating status of the engaging means in the fourth embodiment, FIG. 16 is a skeleton diagram showing the fifth embodiment, and FIG.
The figure is a skeleton diagram showing the sixth embodiment. 12... Input shaft, 14... Output shaft, 2... First planetary gear set, 4... First sun gear, 6... First pinion, 8... First ring gear, 0... - 1st carrier, 2... 2nd planetary gear set, 4... 2nd sun gear, 6... 2nd pinion, 7... 3rd pinion, 2... 2nd ring gear, 0... 1st 2 carrier, 2...Third planetary gear set, 4...Third sun gear, 6...Fourth pinion, 0...Third ring gear, 2...Third carrier, 4...First Clutch means, 6: Second clutch means, 0: Third clutch means, 0: First brake means, 62: Second brake means, 64: Third brake means .

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. A first pinion that rotatably supports a first pinion that meshes with the sun gear and is rotatably arranged relative to the housing case.
a first planetary gear set consisting of a simple planetary gear set that is a combination of a carrier and a first ring gear that is arranged coaxially with the first sun gear and is rotatably arranged with respect to the housing case and meshes with the first pinion;
A second sun gear that is rotatably supported with respect to the storage case, a second pinion that meshes with the second sun gear, and a third pinion that meshes with the second pinion are rotatably supported and rotatably arranged with respect to the storage case. the second carrier and the second
A second pinion disposed coaxially with the sun gear and rotatably disposed with respect to the housing case and meshing with the third pinion.
a second planetary gear set consisting of a double pinion simple planetary gear set in combination with a ring gear;
A third planetary gear set consisting of a simple planetary gear set having the same combination as the first planetary gear set, first to third clutch means, and first to third brake means, the first sun gear and the second sun gear are connected, the first ring gear, the second carrier, and the third carrier are connected, the second ring gear, the third ring gear, and the output shaft are connected, and the first clutch means connects the input shaft to the first sun gear and the second carrier. The second clutch means is arranged so as to be able to connect the input shaft to the first carrier, the third clutch means is arranged so as to be able to connect the input shaft to the third sun gear, and the first brake means is arranged so as to be able to connect the input shaft to the third sun gear. The first carrier is arranged to be able to be restrained relative to the storage case, the second brake means is arranged to be able to restrain the first ring gear, the second carrier, and the third carrier relative to the storage case, and the third brake means is arranged to be able to restrain the first ring gear, the second carrier, and the third carrier relative to the storage case. A gear transmission characterized in that a sun gear is arranged such that it 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. A first pinion that rotatably supports a first pinion that meshes with the sun gear and is rotatably arranged relative to the housing case.
a first planetary gear set consisting of a simple planetary gear set that is a combination of a carrier and a first ring gear that is arranged coaxially with the first sun gear and is rotatably arranged with respect to the housing case and meshes with the first pinion;
A second sun gear that is rotatably supported with respect to the storage case, a second pinion that meshes with the second sun gear, and a third pinion that meshes with the second pinion are rotatably supported and rotatably arranged with respect to the storage case. the second carrier and the second
A second pinion disposed coaxially with the sun gear and rotatably disposed with respect to the housing case and meshing with the third pinion.
a second planetary gear set consisting of a double pinion simple planetary gear set in combination with a ring gear;
The third planetary gear set includes a simple planetary gear set having the same combination as the first 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 first ring gear and the second carrier are connected, the second ring gear and the third carrier are connected to the output shaft, and the first clutch means connects the input shaft to the first sun gear, the second sun gear, and the 3 ring gear, the second clutch means is arranged so as to connect the input shaft to the first carrier, the third clutch means is arranged so as to connect the input shaft to the third sun gear, and the first brake means is the first
The carrier is arranged so as to be able to be restrained relative to the accommodation case, the second brake means is arranged so that the first ring gear and the second carrier are able to be restrained relative to the accommodation case, and the third brake means is arranged so that the third sun gear is able to be restrained relative to the accommodation case. A gear transmission device characterized in that the gear transmission is arranged such that it can be restrained.