WO2016021292A1

WO2016021292A1 - Planetary gear transmission

Info

Publication number: WO2016021292A1
Application number: PCT/JP2015/066054
Authority: WO
Inventors: 伸人安田; 拓松尾
Original assignee: 株式会社小松製作所
Priority date: 2014-08-05
Filing date: 2015-06-03
Publication date: 2016-02-11
Also published as: JP2017160919A

Abstract

Provided is a planetary gear transmission in which a first sun gear (11) and a second sun gear (21) rotate integrally with an input shaft (7). A second carrier (24) rotates integrally with a first ring gear (13). A third sun gear (31) rotates integrally with a first intermediate shaft (81). A third ring gear (33) rotates integrally with a second carrier (24). A fourth sun gear (41) rotates integrally with a first intermediate shaft (81). A fourth ring gear (43) rotates integrally with a third carrier (34). A fourth carrier (44) outputs power. A first clutch (51) connects the input shaft (7) and the first intermediate shaft (81). A second clutch (52) connects the input shaft (7) and a third carrier (34). A third clutch (53) connects the input shaft (7) and a first carrier (14). A first braking mechanism (61) brakes the rotation of the first carrier (14). A second braking mechanism (62) brakes the rotation of the first ring gear (13). A third braking mechanism (63) brakes the rotation of a second ring gear (23). A fourth braking mechanism (64) brakes the rotation of the fourth ring gear (43).

Description

Planetary gear type transmission

The present invention relates to a planetary gear type transmission.

Construction vehicles such as dump trucks are provided with a planetary gear type transmission having a plurality of planetary gear mechanisms. The planetary gear type transmission can obtain a desired reduction ratio by using each planetary gear mechanism in an appropriate combination. For example, the planetary gear type transmission disclosed in Patent Document 1 has nine forward speeds and one reverse speed stage.

Japanese Examined Patent Publication No. 6-78778

The planetary gear type transmission described above has only one reverse speed stage. However, in order to improve fuel efficiency or driving performance, an increase in the reverse speed stage is desired.

An object of the present invention is to provide a planetary gear type transmission having a plurality of reverse speed stages.

The planetary gear type transmission according to the first aspect of the present invention includes an input shaft, a first intermediate shaft, a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, a fourth planetary gear mechanism, and a first clutch. , A second clutch, a third clutch, a first braking mechanism, a second braking mechanism, a third braking mechanism, and a fourth braking mechanism. The input shaft is configured to rotate about the rotation shaft. The first intermediate shaft is configured to rotate about the rotation shaft. The first planetary gear mechanism includes a first sun gear, a first planetary gear, a first ring gear, and a first carrier. The first sun gear is configured to rotate integrally with the input shaft. The second planetary gear mechanism has a second sun gear, a second planetary gear, a second ring gear, and a second carrier. The second sun gear is configured to rotate integrally with the input shaft. The second carrier is configured to rotate integrally with the first ring gear. The third planetary gear mechanism has a third sun gear, a third planetary gear, a third ring gear, and a third carrier. The third sun gear is configured to rotate integrally with the first intermediate shaft. The third ring gear is configured to rotate integrally with the second carrier. The fourth planetary gear mechanism has a fourth sun gear, a fourth planetary gear, a fourth ring gear, and a fourth carrier. The fourth sun gear is configured to rotate integrally with the first intermediate shaft. The fourth ring gear is configured to rotate integrally with the third carrier. The fourth carrier is configured to output power. The first clutch is configured to connect the input shaft and the first intermediate shaft. The second clutch is configured to connect the input shaft and the third carrier. The third clutch is configured to connect the input shaft and the first carrier. The first braking mechanism is configured to brake the rotation of the first carrier. The second braking mechanism is configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear. The third braking mechanism is configured to brake the rotation of the second ring gear. The fourth braking mechanism is configured to brake the rotation of the fourth ring gear.

The planetary gear type transmission according to the second aspect of the present invention includes an input shaft, a first intermediate shaft, a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, a fourth planetary gear mechanism, and a first clutch. , A second clutch, a third clutch, a first braking mechanism, a second braking mechanism, a third braking mechanism, and a fourth braking mechanism. The input shaft is configured to rotate about the rotation shaft. The first intermediate shaft is configured to rotate about the rotation shaft. The first planetary gear mechanism includes a first sun gear, a first planetary gear, a first ring gear, and a first carrier. The first sun gear is configured to rotate integrally with the input shaft. The second planetary gear mechanism has a second sun gear, a second planetary gear, a second ring gear, and a second carrier. The second sun gear is configured to rotate integrally with the input shaft. The second carrier is configured to rotate integrally with the first ring gear. The third planetary gear mechanism has a third sun gear, a third planetary gear, a third ring gear, and a third carrier. The third sun gear is configured to rotate integrally with the first intermediate shaft. The third ring gear is configured to rotate integrally with the second carrier. The fourth planetary gear mechanism has a fourth sun gear, a fourth planetary gear, a fourth ring gear, and a fourth carrier. The fourth sun gear is configured to rotate integrally with the first intermediate shaft. The fourth ring gear is configured to rotate integrally with the third carrier. The fourth carrier is configured to output power. The first clutch is configured to connect the input shaft and the first intermediate shaft. The second clutch is configured to connect the input shaft and the third carrier. The third clutch is configured to connect the first ring gear and the first carrier. The first braking mechanism is configured to brake the rotation of the first carrier. The second braking mechanism is configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear. The third braking mechanism is configured to brake the rotation of the second ring gear. The fourth braking mechanism is configured to brake the rotation of the fourth ring gear.

The planetary gear type transmission according to the third aspect of the present invention includes an input shaft, a first intermediate shaft, a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, a fourth planetary gear mechanism, and a first clutch. , A second clutch, a third clutch, a first braking mechanism, a second braking mechanism, a third braking mechanism, and a fourth braking mechanism. The input shaft is configured to rotate about the rotation shaft. The first intermediate shaft is configured to rotate about the rotation shaft. The first planetary gear mechanism includes a first sun gear, a first planetary gear, a first ring gear, and a first carrier. The first sun gear is configured to rotate integrally with the input shaft. The second planetary gear mechanism has a second sun gear, a second planetary gear, a second ring gear, and a second carrier. The second sun gear is configured to rotate integrally with the input shaft. The second carrier is configured to rotate integrally with the first ring gear. The third planetary gear mechanism has a third sun gear, a third planetary gear, a third ring gear, and a third carrier. The third sun gear is configured to rotate integrally with the first intermediate shaft. The third ring gear is configured to rotate integrally with the second carrier. The fourth planetary gear mechanism has a fourth sun gear, a fourth planetary gear, a fourth ring gear, and a fourth carrier. The fourth sun gear is configured to rotate integrally with the first intermediate shaft. The fourth ring gear is configured to rotate integrally with the third carrier. The fourth carrier is configured to output power. The first clutch is configured to connect the input shaft and the first intermediate shaft. The second clutch is configured to connect the input shaft and the third carrier. The third clutch is configured to connect the third ring gear and the third carrier. The first braking mechanism is configured to brake the rotation of the first carrier. The second braking mechanism is configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear. The third braking mechanism is configured to brake the rotation of the second ring gear. The fourth braking mechanism is configured to brake the rotation of the fourth ring gear.

Preferably, the input shaft is hollow. The first intermediate shaft is disposed in the input shaft.

Preferably, the planetary gear type transmission further includes a second intermediate shaft. The second intermediate shaft is disposed between the input shaft and the first intermediate shaft. The second intermediate shaft is configured to rotate integrally with the third carrier.

Preferably, the planetary gear type transmission further includes an output shaft configured to rotate integrally with the fourth carrier.

Preferably, the first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism are arranged in this order along the rotation axis direction.

Preferably, the planetary gear type transmission further includes a casing for accommodating each planetary gear mechanism. A space is formed between the third clutch and the casing in the radial direction of the rotation shaft. According to this configuration, when the third clutch is a hydraulic clutch, it is easy to configure a hydraulic circuit for sending oil to the third clutch.

Preferably, the second braking mechanism is disposed on the radially outer side of the first ring gear. The first braking mechanism is disposed on the input side of the second braking mechanism in the rotation axis direction. The third clutch is disposed between the first braking mechanism and the second braking mechanism in the rotation axis direction.

Preferably, the third clutch is disposed between the third planetary gear mechanism and the fourth planetary gear mechanism in the rotation axis direction.

The planetary gear type transmission according to the present invention can have a plurality of reverse speed stages.

1 is a schematic view of a planetary gear type transmission according to a first embodiment. The table | surface which shows the clutch or braking mechanism which becomes an ON state in each speed step of the planetary gear type transmission which concerns on 1st Embodiment. The figure which shows transmission of power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the 1st speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the 2nd speed state of advance. The figure which shows transmission of power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the 3rd speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the 4th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the 5th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the 6th speed state of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the 7th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of 8th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is the state of the 9th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is in the state of the reverse 1st speed. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 1st Embodiment is a 2nd speed state of reverse drive. The schematic diagram of the planetary gear type gearbox concerning a 2nd embodiment. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of the 1st speed of advance. The figure which shows transmission of power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of 2nd speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of the 3rd speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is the state of the 4th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of the 5th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is a 6th speed state of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is a 7th speed state of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of 8th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of the 9th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of the reverse 1st speed. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 2nd Embodiment is in the state of 2nd speed of reverse drive. The schematic diagram of the planetary gear type gearbox concerning a 3rd embodiment. The table | surface which shows the clutch or braking mechanism which becomes an ON state in each speed stage of the planetary gear type transmission which concerns on 3rd Embodiment. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 1st speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of 2nd speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 3rd speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 4th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 5th forward speed. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 6th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 7th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the 8th speed state of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 9th speed of advance. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the state of the 1st speed of reverse. The figure which shows transmission of motive power when the planetary gear type transmission which concerns on 3rd Embodiment is in the 2nd speed state of reverse. The schematic diagram of the planetary gear type gearbox concerning a modification.

Hereinafter, embodiments of a planetary gear type transmission according to the present invention will be described with reference to the drawings. In the following description, the rotation axis direction indicates the direction in which the rotation axis extends. The radial direction of the rotation axis indicates the radial direction of a circle around the rotation axis. Specifically, the rotation axis direction is the left-right direction in FIGS. 1, 14, and 26, and the radial direction is the up-down direction in FIG. 1, FIG. 14, and FIG. The rotation axis indicates the center line of the input shaft. The input side indicates the side on which the planetary gear type transmission inputs power, and the output side indicates the side on which the planetary gear type transmission outputs power. Specifically, the input side is the left side of FIGS. 1, 14, and 26, and the output side is the right side of FIGS. 1, 14, and 26.

[First Embodiment]
FIG. 1 is a schematic view of a planetary gear type transmission according to the first embodiment. As shown in FIG. 1, the planetary gear type transmission 100 shifts and outputs the rotational speed of power from an engine (not shown) or the like. Note that power from the engine or the like may be input to the planetary gear type transmission 100 via a torque converter.

The planetary gear type transmission 100 includes a plurality of planetary gear mechanisms 1 to 4, a plurality of clutches 51 to 53, a plurality of braking mechanisms 61 to 64, an input shaft 7, a first intermediate shaft 81, a second intermediate shaft 82, and a casing. 9 is provided. The casing 9 accommodates the planetary gear mechanisms 1 to 4, clutches 51 to 53, brake mechanisms 61 to 64, the input shaft 7, the first intermediate shaft 81, and the second intermediate shaft 82.

The planetary gear type transmission 100 includes a first planetary gear mechanism 1, a second planetary gear mechanism 2, a third planetary gear mechanism 3, and a fourth planetary gear mechanism 4 as a plurality of planetary gear mechanisms. The planetary gear type transmission 100 includes a first clutch 51, a second clutch 52, and a third clutch 53 as a plurality of clutches. The planetary gear type transmission 100 includes a first braking mechanism 61, a second braking mechanism 62, a third braking mechanism 63, and a fourth braking mechanism 64 as a plurality of braking mechanisms.

The first planetary gear mechanism 1, the second planetary gear mechanism 2, the third planetary gear mechanism 3, and the fourth planetary gear mechanism 4 are arranged in this order along the rotation axis direction. Specifically, the first planetary gear mechanism 1, the second planetary gear mechanism 2, the third planetary gear mechanism, and the fourth planetary gear mechanism are arranged in this order from the input side to the output side.

The input shaft 7 is configured to rotate around the rotation axis O. The rotation axis O is the center line of the input shaft 7. The input shaft 7 is hollow. Specifically, the input shaft 7 is cylindrical. Power from an engine or the like is input to the input shaft 7.

The first intermediate shaft 81 is configured to rotate around the rotation axis O. That is, the first intermediate shaft 81 extends in the rotation axis direction. The first intermediate shaft 81 is disposed in the input shaft 7. The central axis of the first intermediate shaft 81 and the central axis of the input shaft 7 are substantially the same.

The second intermediate shaft 82 is configured to rotate about the rotation axis O. That is, the second intermediate shaft 82 extends in the rotation axis direction. The second intermediate shaft 82 is disposed in the input shaft 7. The second intermediate shaft 82 is hollow. Specifically, the second intermediate shaft 82 is cylindrical. The first intermediate shaft 81 is disposed in the second intermediate shaft 82. That is, the first intermediate shaft 81 is disposed in the second intermediate shaft 82, and the second intermediate shaft 82 is disposed in the input shaft 7. The first intermediate shaft 81, the second intermediate shaft 82, and the input shaft 7 are arranged in this order toward the radially outer side.

The first planetary gear mechanism 1 includes a first sun gear 11, a plurality of first planetary gears 12, a first ring gear 13, and a first carrier 14.

The first sun gear 11 is configured to rotate integrally with the input shaft 7. Specifically, the first sun gear 11 is fixed to the input shaft 7. The first sun gear 11 and the input shaft 7 may be formed by a single member.

Each first planetary gear 12 is configured to mesh with the first sun gear 11. Each first planetary gear 12 is disposed on the radially outer side of the first sun gear 11. Specifically, the first planetary gears 12 are arranged at intervals in the circumferential direction.

Each first planetary gear 12 is configured to revolve around the first sun gear 11. That is, each first planetary gear 12 is configured to rotate about the rotation axis O. Each first planetary gear 12 is configured to rotate.

The first ring gear 13 is in mesh with each first planetary gear 12. The first ring gear 13 is configured to rotate around the rotation axis O.

The first carrier 14 supports each first planetary gear 12. Each first planetary gear 12 can rotate while being supported by the first carrier 14. The first carrier 14 is configured to rotate about the rotation axis O.

The second planetary gear mechanism 2 includes a second sun gear 21, a plurality of second planetary gears 22, a second ring gear 23, and a second carrier 24.

The second sun gear 21 is configured to rotate integrally with the input shaft 7. Specifically, the second sun gear 21 is fixed to the input shaft 7. The second sun gear 21 and the input shaft 7 may be formed by a single member.

Each second planetary gear 22 is configured to mesh with the second sun gear 21. Each second planetary gear 22 is disposed on the radially outer side of the second sun gear 21. Specifically, the second planetary gears 22 are arranged at intervals in the circumferential direction.

Each second planetary gear 22 is configured to revolve around the second sun gear 21. That is, each second planetary gear 22 is configured to rotate about the rotation axis O. Each second planetary gear 22 is configured to rotate.

The second ring gear 23 meshes with each second planetary gear 22. The second ring gear 23 is configured to rotate around the rotation axis O.

The second carrier 24 supports each second planetary gear 22. Each of the second planetary gears 22 can rotate while being supported by the second carrier 24. The second carrier 24 is configured to rotate around the rotation axis O.

The second carrier 24 is configured to rotate integrally with the first ring gear 13. Specifically, the second carrier 24 is connected to the first ring gear 13. The second carrier 24 and the first ring gear 13 may be formed by one member.

The third planetary gear mechanism 3 has a third sun gear 31, a plurality of third planetary gears 32, a third ring gear 33, and a third carrier 34.

The third sun gear 31 is configured to rotate integrally with the first intermediate shaft 81. Specifically, the third sun gear 31 is fixed to the first intermediate shaft 81. Note that the third sun gear 31 and the first intermediate shaft 81 may be formed by a single member.

Each third planetary gear 32 is configured to mesh with the third sun gear 31. Each third planetary gear 32 is disposed on the radially outer side of the third sun gear 31. Specifically, the third planetary gears 32 are arranged at intervals in the circumferential direction.

Each third planetary gear 32 is configured to revolve around the third sun gear 31. That is, each third planetary gear 32 is configured to rotate about the rotation axis O. Each third planetary gear 32 is configured to rotate.

The third ring gear 33 is in mesh with each third planetary gear 32. The third ring gear 33 is configured to rotate around the rotation axis O.

The third ring gear 33 is configured to rotate integrally with the second carrier 24. Specifically, the third ring gear 33 is connected to the second carrier 24. That is, the first ring gear 13, the second carrier 24, and the third ring gear 33 are configured to rotate integrally. Note that the third ring gear 33 and the second carrier 24 may be formed of a single member.

The third carrier 34 supports each third planetary gear 32. Each third planetary gear 32 can rotate while being supported by the third carrier 34. The third carrier 34 is configured to rotate about the rotation axis O.

The third carrier 34 is configured to rotate integrally with the second intermediate shaft 82. Specifically, the third carrier 34 is fixed to the second intermediate shaft 82. The third carrier 34 and the second intermediate shaft 82 may be formed by one member.

The fourth planetary gear mechanism 4 includes a fourth sun gear 41, a plurality of fourth planetary gears 42, a fourth ring gear 43, and a fourth carrier 44.

The fourth sun gear 41 is configured to rotate integrally with the first intermediate shaft 81. Specifically, the fourth sun gear 41 is fixed to the first intermediate shaft 81. Note that the fourth sun gear 41 and the first intermediate shaft 81 may be formed of a single member.

Each fourth planetary gear 42 is configured to mesh with the fourth sun gear 41. Each fourth planetary gear 42 is disposed on the radially outer side of the fourth sun gear 41. Specifically, the fourth planetary gears 42 are arranged at intervals in the circumferential direction.

Each fourth planetary gear 42 is configured to revolve around the fourth sun gear 41. That is, each fourth planetary gear 42 is configured to rotate about the rotation axis O. Each fourth planetary gear 42 is configured to rotate.

The fourth ring gear 43 is in mesh with each fourth planetary gear 42. The fourth ring gear is configured to rotate about the rotation axis O.

The fourth ring gear 43 is configured to rotate integrally with the third carrier 34. Specifically, the fourth ring gear 43 is connected to the third carrier 34. That is, the second intermediate shaft 82, the third carrier 34, and the fourth ring gear 43 are configured to rotate integrally with each other. Note that the fourth ring gear 43 and the third carrier 34 may be formed of a single member.

The fourth carrier 44 supports each fourth planetary gear 42. Each fourth planetary gear 42 can rotate while being supported by the fourth carrier 44. The fourth carrier 44 is configured to rotate about the rotation axis O.

The fourth carrier 44 outputs power. Specifically, the fourth carrier 44 outputs power having a rotational speed changed by the planetary gear type transmission 100. The fourth carrier 44 rotates integrally with the output shaft 10. For this reason, the output shaft 10 outputs the shifted power. The fourth carrier 44 and the output shaft 10 may be formed by a single member.

The first clutch 51 is configured to connect the input shaft 7 and the first intermediate shaft 81. Specifically, the first clutch 51 connects the input shaft 7 and the first intermediate shaft 81 so that they can be disconnected. When the first clutch 51 is on, the first clutch 51 connects the input shaft 7 and the first intermediate shaft 81. Therefore, the input shaft 7 and the first intermediate shaft 81 rotate integrally.

When the first clutch 51 is in the off state, the first clutch 51 disconnects the connection between the input shaft 7 and the first intermediate shaft 81. Accordingly, the first intermediate shaft 81 is rotatable relative to the input shaft 7. The first clutch 51 is, for example, a hydraulic clutch mechanism, and can be composed of a plurality of disks.

The second clutch 52 is configured to connect the input shaft 7 and the third carrier 34. That is, the second clutch 52 connects the input shaft 7 and the third carrier 34 so that they can be disconnected. Specifically, the second clutch 52 connects the input shaft 7 and the third carrier 34 by connecting the input shaft 7 and the second intermediate shaft 82. The second clutch 52 is, for example, a hydraulic clutch mechanism and can be composed of a plurality of disks.

When the second clutch 52 is on, the second clutch 52 connects the input shaft 7 and the second intermediate shaft 82. That is, the second clutch 52 connects the input shaft 7 and the third carrier 34 via the second intermediate shaft 82. Therefore, the input shaft 7 and the third carrier 34 rotate integrally.

When the second clutch 52 is off, the second clutch 52 disconnects the connection between the input shaft 7 and the third carrier 34. That is, the second clutch 52 blocks the connection between the input shaft 7 and the third carrier 34 by blocking the connection between the input shaft 7 and the second intermediate shaft 82. Therefore, the second intermediate shaft 82 and the third carrier 34 can rotate relative to the input shaft 7.

The third clutch 53 is configured to connect the input shaft 7 and the first carrier 14. Specifically, the third clutch 53 connects the input shaft 7 and the first carrier 14 so that they can be disconnected. The third clutch 53 is, for example, a hydraulic clutch mechanism, and can be composed of a plurality of disks.

When the third clutch 53 is on, the third clutch 53 connects the input shaft 7 and the first carrier 14. Therefore, the input shaft 7 and the first carrier 14 rotate integrally.

When the third clutch 53 is in the off state, the third clutch 53 disconnects the connection between the input shaft 7 and the first carrier 14. Therefore, the first carrier 14 can rotate relative to the input shaft 7.

The first braking mechanism 61 is configured to brake the rotation of the first carrier 14. Specifically, the first braking mechanism 61 is configured to connect the first carrier 14 and the casing 9.

When the first braking mechanism 61 is on, the first braking mechanism 61 brakes the rotation of the first carrier 14. That is, when the first braking mechanism 61 is in the on state, the first braking mechanism 61 connects the first carrier 14 and the casing 9. Therefore, the first carrier 14 cannot rotate.

On the other hand, when the first braking mechanism 61 is in the off state, the first braking mechanism 61 does not brake the rotation of the first carrier 14. That is, when the first braking mechanism 61 is in the off state, the first braking mechanism 61 does not connect the first carrier 14 and the casing 9. Accordingly, the first carrier 14 is rotatable.

The first braking mechanism 61 is disposed on the input side with respect to the second braking mechanism 62 in the rotation axis direction.

The second braking mechanism 62 is configured to brake the rotation of the first ring gear 13. Specifically, the second braking mechanism 62 is configured to connect the first ring gear 13 and the casing 9.

When the second braking mechanism 62 is on, the second braking mechanism 62 brakes the rotation of the first ring gear 13. That is, when the second braking mechanism 62 is in the on state, the second braking mechanism 62 connects the first ring gear 13 and the casing 9. Therefore, the first ring gear 13 cannot rotate.

On the other hand, when the second brake mechanism 62 is in the off state, the second brake mechanism 62 does not brake the rotation of the first ring gear 13. That is, when the second braking mechanism 62 is in the off state, the second braking mechanism 62 does not connect the first ring gear 13 and the casing 9. Therefore, the first ring gear 13 is rotatable. The second braking mechanism 62 is disposed on the radially outer side of the first ring gear 13.

The third braking mechanism 63 is configured to brake the rotation of the second ring gear 23. Specifically, the third braking mechanism 63 is configured to connect the second ring gear 23 and the casing 9.

When the third brake mechanism 63 is on, the third brake mechanism 63 brakes the rotation of the second ring gear 23. That is, when the third braking mechanism 63 is in the on state, the third braking mechanism 63 connects the second ring gear 23 and the casing 9. Therefore, the second ring gear 23 cannot rotate.

On the other hand, when the third braking mechanism 63 is in the off state, the third braking mechanism 63 does not brake the rotation of the second ring gear 23. That is, when the third braking mechanism 63 is in the off state, the third braking mechanism 63 does not connect the second ring gear 23 and the casing 9. Therefore, the second ring gear 23 is rotatable. Note that the third braking mechanism 63 is disposed on the radially outer side of the second ring gear 23.

The fourth braking mechanism 64 is configured to brake the rotation of the fourth ring gear 43. Specifically, the fourth braking mechanism 64 is configured to connect the fourth ring gear 43 and the casing 9.

When the fourth brake mechanism 64 is on, the fourth brake mechanism 64 brakes the rotation of the fourth ring gear 43. That is, when the fourth braking mechanism 64 is in the on state, the fourth braking mechanism 64 connects the fourth ring gear 43 and the casing 9. Therefore, the fourth ring gear 43 cannot rotate.

On the other hand, when the fourth brake mechanism 64 is in the off state, the fourth brake mechanism 64 does not brake the rotation of the fourth ring gear 43. That is, when the fourth braking mechanism 64 is in the off state, the fourth braking mechanism 64 does not connect the fourth ring gear 43 and the casing 9. Therefore, the fourth ring gear 43 is rotatable. The fourth braking mechanism 64 is disposed on the radially outer side of the fourth ring gear 43.

The operation of the planetary gear type transmission 100 configured as described above will be described. The planetary gear type transmission 100 has nine speed stages in the forward direction and two speed stages in the reverse direction. FIG. 2 is a table showing each clutch or each braking mechanism that is turned on at each speed stage. 2 indicate the clutches or braking mechanisms that are turned on.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the first forward speed (F1), the first braking mechanism 61 is turned on and the fourth braking mechanism 64 is turned on. To. The second braking mechanism 62, the third braking mechanism 63, and the first to third clutches 51 to 53 are in an off state.

Since the first braking mechanism 61 is turned on, the first carrier 14 cannot rotate. Further, since the fourth braking mechanism 64 is turned on, the fourth ring gear 43 cannot be rotated. Since the third carrier 34 rotates integrally with the fourth ring gear 43, the third carrier 34 also cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first sun gear 11 rotates integrally with the input shaft 7. The rotation of the first sun gear 11 causes each first planetary gear 12 to rotate. In addition, since the 1st carrier 14 cannot rotate, each 1st planetary gear 12 does not revolve.

The first ring gear 13 is rotated by the rotation of each first planetary gear 12. The second carrier 24 rotates integrally with the first ring gear 13.

The third ring gear 33 rotates integrally with the second carrier 24. As the third ring gear 33 rotates, each third planetary gear 32 rotates. In addition, since the 3rd carrier 34 cannot rotate, each 3rd planetary gear 32 does not revolve.

The third sun gear 31 is rotated by the rotation of each third planetary gear 32. The fourth sun gear 41 rotates integrally with the third sun gear 31. The rotation of the fourth sun gear 41 causes each fourth planetary gear 42 to rotate and revolve. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the second forward speed (F2), the first clutch 51 is turned on and the fourth braking mechanism 64 is turned on. To do. That is, in switching between the first speed (F1) and the second speed (F2), the fourth braking mechanism 64 is kept on. Note that the second clutch 52, the third clutch 53, and the first to third braking mechanisms 61 to 63 are in an off state.

Since the first clutch 51 is turned on, the first intermediate shaft 81 rotates integrally with the input shaft 7. Further, since the fourth braking mechanism 64 is turned on, the fourth ring gear 43 cannot be rotated. Since the third carrier 34 rotates integrally with the fourth ring gear 43, the third carrier 34 also cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first intermediate shaft 81 rotates integrally with the input shaft 7.

The fourth sun gear 41 rotates integrally with the first intermediate shaft 81. The rotation of the fourth sun gear 41 causes each fourth planetary gear 42 to rotate and revolve. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the third forward speed (F3), the first clutch 51 is turned on and the first braking mechanism 61 is turned on. To do. That is, in switching between the second speed (F2) and the third speed (F3), the first clutch 51 remains on. The second to fourth braking mechanisms 62 to 64, the second clutch 52, and the third clutch 53 are in the off state.

Since the first clutch 51 is turned on, the first intermediate shaft 81 rotates integrally with the input shaft 7. In addition, since the first braking mechanism 61 is turned on, the first carrier 14 cannot be rotated.

The third ring gear 33 rotates integrally with the second carrier 24. The third sun gear 31 rotates integrally with the first intermediate shaft 81. With the rotation of the third sun gear 31 and the rotation of the third ring gear 33, each third planetary gear 32 revolves while rotating. Then, the third carrier 34 rotates.

The fourth ring gear 43 rotates integrally with the third carrier 34. The fourth sun gear 41 rotates integrally with the first intermediate shaft 81. By the rotation of the fourth ring gear 43 and the rotation of the fourth sun gear 41, each fourth planetary gear 42 revolves while rotating. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the fourth forward speed (F4), the first clutch 51 is turned on and the second braking mechanism 62 is turned on. To do. That is, in switching between the third speed (F3) and the fourth speed (F4), the first clutch 51 remains on. The first braking mechanism 61, the third braking mechanism 63, the fourth braking mechanism 64, the second clutch 52, and the third clutch 53 are in an off state.

Since the first clutch 51 is turned on, the first intermediate shaft 81 rotates integrally with the input shaft 7. Further, since the second brake mechanism 62 is turned on, the first ring gear 13 cannot be rotated. Since the second carrier 24 rotates integrally with the first ring gear 13, the second carrier 24 also cannot rotate. Furthermore, since the third ring gear 33 rotates integrally with the second carrier 24, the third ring gear 33 cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first intermediate shaft 81 rotates integrally with the input shaft 7. Then, the third sun gear 31 and the fourth sun gear 41 rotate integrally with the first intermediate shaft 81.

The rotation of the third sun gear 31 causes each third planetary gear 32 to rotate and revolve. Then, the third carrier 34 rotates. The fourth ring gear 43 rotates integrally with the third carrier 34.

The rotation of the fourth ring gear 43 and the rotation of the fourth sun gear 41 cause each fourth planetary gear 42 to revolve while rotating. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the fifth forward speed (F5), the first clutch 51 is turned on and the third braking mechanism 63 is turned on. To do. That is, in switching between the fourth speed (F4) and the fifth speed (F5), the first clutch 51 remains on. The first braking mechanism 61, the second braking mechanism 62, the fourth braking mechanism 64, the second clutch 52, and the third clutch 53 are in an off state.

Since the first clutch 51 is turned on, the first intermediate shaft 81 rotates integrally with the input shaft 7. Further, since the third braking mechanism 63 is turned on, the second ring gear 23 cannot be rotated.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the input shaft 7 and the first intermediate shaft 81 rotate integrally with each other. The second sun gear 21 rotates integrally with the input shaft 7, and the third sun gear 31 and the fourth sun gear 41 rotate integrally with the first intermediate shaft 81.

The rotation of the second sun gear 21 causes each second planetary gear 22 to rotate and revolve. Then, the second carrier 24 rotates. The third ring gear 33 rotates integrally with the second carrier 24.

The rotation of the third sun gear 31 and the rotation of the third ring gear 33 cause each third planetary gear 32 to rotate and revolve. Then, the third carrier 34 rotates. The fourth ring gear 43 rotates integrally with the third carrier 34.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the sixth forward speed (F6), the first clutch 51 is turned on and the second clutch 52 is turned on. . That is, in switching between the fifth speed (F5) and the sixth speed (F6), the first clutch 51 remains on. Note that the first to fourth braking mechanisms 61 to 64 and the third clutch 53 are in an off state.

Since the first clutch 51 is turned on, the first intermediate shaft 81 rotates integrally with the input shaft 7. Further, since the second clutch 52 is turned on, the second intermediate shaft 82 rotates integrally with the input shaft 7.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the input shaft 7, the first intermediate shaft 81, and the second intermediate shaft 82 rotate integrally with each other. The third sun gear 31 and the fourth sun gear 41 rotate integrally with the first intermediate shaft 81. The third carrier 34 rotates integrally with the second intermediate shaft 82. The fourth ring gear 43 rotates integrally with the third carrier 34.

The fourth planetary gears 42 revolve by the rotation of the fourth sun gear 41 and the rotation of the fourth ring gear 43. In addition, since the 4th sun gear 41 and the 4th ring gear 43 rotate at the same rotational speed, each 4th planetary gear 42 does not autorotate. For this reason, each fourth planetary gear 42 revolves at the same rotational speed as the fourth sun gear 41 and the fourth ring gear 43. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a rotational speed that is not changed. That is, the planetary gear type transmission 100 in the sixth speed state does not change the rotational speed of the power from the engine or the like.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the seventh forward speed (F7), the second clutch 52 is turned on and the third braking mechanism 63 is turned on. To do. That is, in switching between the sixth speed (F6) and the seventh speed (F7), the second clutch 52 remains on. The first braking mechanism 61, the second braking mechanism 62, the fourth braking mechanism 64, the first clutch 51, and the third clutch 53 are in an off state.

Since the second clutch 52 is turned on, the second intermediate shaft 82 rotates integrally with the input shaft 7. Further, since the third braking mechanism 63 is turned on, the second ring gear 23 cannot be rotated.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the input shaft 7 and the second intermediate shaft 82 rotate integrally with each other. The second sun gear 21 rotates integrally with the input shaft 7. The third carrier 34 rotates integrally with the second intermediate shaft 82.

Each third planetary gear 32 revolves by the rotation of the third carrier 34. Further, each third planetary gear 32 rotates by the rotation of the third ring gear 33 and the rotation of the third carrier 34. As a result, the third sun gear 31 rotates.

The fourth sun gear 41 rotates integrally with the third sun gear 31. The fourth ring gear 43 rotates integrally with the third carrier 34. Due to the rotation of the fourth sun gear 41 and the rotation of the fourth ring gear 43, each fourth planetary gear 42 revolves while rotating. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the eighth forward speed (F8), the second clutch 52 is turned on and the second braking mechanism 62 is turned on. To do. That is, in switching between the seventh speed (F7) and the eighth speed (F8), the second clutch 52 remains on. The first braking mechanism 61, the third braking mechanism 63, the fourth braking mechanism 64, the first clutch 51, and the third clutch 53 are in an off state.

Since the second clutch 52 is turned on, the second intermediate shaft 82 rotates integrally with the input shaft 7. Further, since the second braking mechanism 62 is turned on, the first ring gear 13 cannot be rotated. Since the second carrier 24 rotates integrally with the first ring gear 13, the second carrier 24 also cannot rotate. Furthermore, since the third ring gear 33 rotates integrally with the second carrier 24, the third ring gear 33 cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the second intermediate shaft 82 rotates integrally with the input shaft 7. Then, the third carrier 34 rotates integrally with the second intermediate shaft 82.

Rotation of the third carrier 34 causes each third planetary gear 32 to revolve and rotate. Then, the third sun gear 31 rotates.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the ninth forward speed (F9), the second clutch 52 is turned on and the first braking mechanism 61 is turned on. To do. That is, in switching between the eighth speed (F8) and the ninth speed (F9), the second clutch 52 remains on. The second to fourth braking mechanisms 62 to 64, the first clutch 51, and the third clutch 53 are in an off state.

Since the second clutch 52 is turned on, the second intermediate shaft 82 rotates integrally with the input shaft 7. In addition, since the first braking mechanism 61 is turned on, the first carrier 14 cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first sun gear 11 rotates integrally with the input shaft 7. The rotation of the first sun gear 11 causes each first planetary gear 12 to rotate. Since the first carrier 14 cannot rotate as described above, each first planetary gear 12 does not revolve.

The third ring gear 33 rotates integrally with the second carrier 24. The third carrier 34 rotates integrally with the second intermediate shaft 82. As a result, each third planetary gear 32 rotates and revolves. And the 3rd sun gear 31 rotates.

The fourth ring gear 43 rotates integrally with the third carrier 34. The fourth sun gear 41 rotates integrally with the third sun gear 31. Due to the rotation of the fourth ring gear 43 and the rotation of the fourth sun gear 41, each fourth planetary gear 42 revolves while rotating. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the first reverse speed (R1), the third braking mechanism 63 is turned on and the fourth braking mechanism 64 is turned on. To. The first braking mechanism 61, the second braking mechanism 62, and the first to third clutches 51 to 53 are in an off state.

Since the third braking mechanism 63 is turned on, the second ring gear 23 cannot be rotated. Further, since the fourth braking mechanism 64 is turned on, the fourth ring gear 43 cannot be rotated. Since the third carrier 34 rotates integrally with the fourth ring gear 43, the third carrier 34 also cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the second sun gear 21 rotates integrally with the input shaft 7. The rotation of the second sun gear 21 causes each second planetary gear 22 to rotate and revolve. Then, the second carrier 24 rotates.

As shown in FIG. 2, when the speed stage of the planetary gear type transmission 100 is set to the second reverse speed (R2), the third clutch 53 is turned on and the fourth braking mechanism 64 is turned on. To do. That is, in switching between the first speed (R1) and the second speed (R2), the fourth braking mechanism 64 is kept on. The first to third braking mechanisms 61 to 63, the first clutch 51, and the second clutch 52 are in an off state.

Since the third clutch 53 is turned on, the first carrier 14 rotates integrally with the input shaft 7. Further, since the fourth braking mechanism 64 is turned on, the fourth ring gear 43 cannot be rotated. Since the third carrier 34 rotates integrally with the fourth ring gear 43, the third carrier 34 also cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first sun gear 11 and the first carrier 14 rotate integrally with the input shaft 7. The first sun gear 11 and the first carrier 14 rotate at the same rotational speed. For this reason, each first planetary gear 12 revolves without rotating. The first ring gear 13 is rotated by the revolution of each first planetary gear 12. The first ring gear 13 rotates at the same rotational speed as the revolution of each first planetary gear 12. That is, the first sun gear 11, the first ring gear 13, and the first carrier 14 rotate integrally with each other.

The second carrier 24 rotates integrally with the first ring gear 13. The third ring gear 33 rotates integrally with the second carrier 24. As the third ring gear 33 rotates, each third planetary gear 32 rotates. In addition, since the 3rd carrier 34 cannot rotate, each 3rd planetary gear 32 does not revolve. The third sun gear 31 is rotated by the rotation of each third planetary gear 32.

The fourth sun gear 41 rotates integrally with the third sun gear 31. The rotation of the fourth sun gear 41 causes each fourth planetary gear 42 to rotate and revolve. As a result, the fourth carrier 44 rotates, and the fourth carrier 44 outputs power having a shifted rotation speed.

Next, how to obtain the reduction ratio at each speed stage described above will be described. The reduction ratio at each speed stage is obtained using at least one of the following first to fourth relational expressions.

The first relational expression is an expression related to the first planetary gear mechanism 1 and is expressed by the following expression (1).

Here, s ₁ is the number of teeth of the first sun gear 11, r ₁ is the number of teeth of the first ring gear 13, N _s1 is the rotational speed ratio of the first sun gear 11, and N _r1 is the rotational speed ratio of the first ring gear 13. , N _c1 is the rotation speed ratio of the first carrier 14.

The second relational expression is an expression relating to the second planetary gear mechanism 2, and is expressed by the following expression (2).

Here, s ₂ is the number of teeth of the second sun gear 21, r ₂ is the number of teeth of the second ring gear 23, N _s2 is the rotation speed ratio of the second sun gear 21, and N _r2 is the rotation speed ratio of the second ring gear 23. , N _c2 is the rotation speed ratio of the second carrier 24.

The third relational expression is an expression related to the third planetary gear mechanism 3, and is expressed by the following expression (3).

Here, s ₃ is the number of teeth of the third sun gear 31, r ₃ is the number of teeth of the third ring gear 33, N _s3 is the rotational speed ratio of the third sun gear 31, and N _r3 is the rotational speed ratio of the third ring gear 33. , N _c3 is the rotation speed ratio of the third carrier 34.

The fourth relational expression is an expression relating to the fourth planetary gear mechanism 4 and is expressed by the following expression (4).

Here, s ₄ is the number of teeth of the fourth sun gear 41, r ₄ is the number of teeth of the fourth ring gear 43, N _s4 is the rotational speed ratio of the fourth sun gear 41, and N _r4 is the rotational speed ratio of the fourth ring gear 43. , N _c4 is the rotation speed ratio of the fourth carrier 44.

First, how to obtain the reduction ratio at the first forward speed will be described. The rotational speed ratio N _r1 of the first ring gear 13 in the first planetary gear mechanism 1 is obtained from the first relational expression. Since the first sun gear 11 rotates integrally with the input shaft 8, the rotation speed ratio N _s1 of the first sun gear 11 is 1. Further, since the first carrier 14 does not rotate, the rotation speed ratio N _c1 of the first carrier 14 is zero.

Next, the rotation speed ratio N _s3 of the third sun gear 31 in the third planetary gear mechanism is obtained from the third relational expression. The third ring gear 33 to rotate integrally with the first ring gear 13, the rotational speed ratio N _r3 of the third ring gear 33 is the same as the rotational speed ratio N _r1 of the first ring gear 13. Further, since the third carrier 34 does not rotate, the rotation speed ratio _Nc3 of the third carrier 34 is zero.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 in the fourth planetary gear mechanism is obtained from the fourth relational expression. Since the fourth sun gear 41 rotates integrally with the third sun gear 31, the rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31. Further, since the fourth ring gear 43 does not rotate, the rotation speed ratio N _r4 of the fourth ring gear 43 is zero.

The reciprocal number of the rotation speed ratio _Nc4 of the fourth carrier 44 obtained as described above is the reduction ratio of the planetary gear type transmission 100. For example, the first sun gear 11 has 30 teeth, the second sun gear 21 has 57 teeth, the third sun gear 31 has 48 teeth, the fourth sun gear 41 has 30 teeth, and the first to fourth rings. When the number of teeth of each of the

gears

13, 23, 33, and 43 is 90, the reduction ratio of the forward first speed is about 6.4. Similarly, the reduction ratios obtained at the respective speed stages are shown in FIG.

At the second forward speed, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. Thereby, the reduction ratio in the second forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is 1, and the rotation speed ratio N _r4 of the fourth ring gear 43 is 0.

At the third forward speed, the rotation speed ratio N _r1 of the first ring gear 13 is obtained by the first relational expression. The rotation speed ratio N _s1 of the first sun gear 11 is 1, and the rotation speed ratio N _c1 of the first carrier 14 is 0.

Next, the rotation speed ratio N _c3 of the third carrier 34 is obtained by the third relational expression. The rotation speed ratio N _s3 of the third sun gear 31 is 1. The rotation speed ratio N _r3 of the third ring gear 33 is the same as the rotation speed ratio N _r1 of the first ring gear 13.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the third forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is 1, and the rotation speed ratio N _r4 of the fourth ring gear 43 is the same as the rotation speed ratio N _c3 of the third carrier 34.

At the fourth forward speed, the rotation speed ratio N _c3 of the third carrier 34 is obtained by the third relational expression. The rotation speed ratio N _s3 of the third sun gear 31 is 1, and the rotation speed ratio N _r3 of the third ring gear 33 is 0.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the fourth forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is 1, and the rotation speed ratio N _r4 of the fourth ring gear 43 is the same as the rotation speed ratio N _c3 of the third carrier 34.

At the fifth forward speed, the rotation speed ratio N _c2 of the second carrier 24 is obtained by the second relational expression. The rotation speed ratio N _s2 of the second sun gear 21 is 1, and the rotation speed ratio N _r2 of the second ring gear 23 is 0.

Next, the rotation speed ratio N _c3 of the third carrier 34 is obtained by the third relational expression. The rotation speed ratio N _s3 of the third sun gear 31 is 1, and the rotation speed ratio N _r3 of the third ring gear 33 is the same as the rotation speed ratio N _c2 of the second carrier 24.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the fifth forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is 1, and the rotation speed ratio N _r4 of the fourth ring gear 43 is the same as the rotation speed ratio N _c3 of the third carrier 34.

In the forward 6th speed, no shift is performed as described above.

At the seventh forward speed, the rotation speed ratio N _c2 of the second carrier 24 is obtained by the second relational expression. The rotation speed ratio N _s2 of the second sun gear 21 is 1, and the rotation speed ratio N _r2 of the second ring gear 23 is 0.

Next, the rotation speed ratio N _s3 of the third sun gear 31 is obtained by the third relational expression. The rotation speed ratio N _c3 of the third carrier 34 is 1, and the rotation speed ratio N _r3 of the third ring gear 33 is the same as the rotation speed ratio N _c2 of the second carrier 24.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the seventh forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31, and the rotation speed ratio N _r4 of the fourth ring gear 43 is 1.

At the eighth forward speed, the rotation speed ratio N _s3 of the third sun gear 31 is obtained by the third relational expression. The rotation speed ratio N _c3 of the third carrier 34 is 1, and the rotation speed ratio N _r3 of the third ring gear 33 is 0.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the eighth forward speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31, and the rotation speed ratio N _r4 of the fourth ring gear 43 is 1.

At the ninth forward speed, the rotation speed ratio N _r1 of the first ring gear 13 is obtained by the first relational expression. The rotation speed ratio N _s1 of the first sun gear 11 is 1, and the rotation speed ratio N _c1 of the first carrier 14 is 0.

Next, the rotation speed ratio N _s3 of the third sun gear 31 is obtained by the third relational expression. The rotation speed ratio N _c3 of the third carrier 34 is 1, and the rotation speed ratio N _r3 of the third ring gear 33 is the same as the rotation speed ratio N _r1 of the first ring gear 13.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the ninth forward speed is obtained. The rotation speed ratio N _r4 of the fourth ring gear 43 is 1, and the rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31.

In the first reverse speed, the rotation speed ratio N _c2 of the second carrier 24 is obtained by the second relational expression. The rotation speed ratio N _s2 of the second sun gear 21 is 1, and the rotation speed ratio N _r2 of the second ring gear 23 is 0.

Next, the rotation speed ratio N _s3 of the third sun gear 31 is obtained by the third relational expression. The rotation speed ratio N _c3 of the third carrier 34 is 0, and the rotation speed ratio N _r3 of the third ring gear 33 is the same as the rotation speed ratio N _c2 of the second carrier 24.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio at the first reverse speed is obtained. The rotation speed ratio N _r4 of the fourth ring gear 43 is 0, and the rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31.

In the second reverse speed, the rotation speed ratio N _s3 of the third sun gear 31 is obtained by the third relational expression. The rotation speed ratio N _r3 of the third ring gear 33 is 1, and the rotation speed ratio N _c3 of the third carrier 34 is 0.

Next, the rotation speed ratio N _c4 of the fourth carrier 44 is obtained by the fourth relational expression. As a result, the reduction ratio in the second reverse speed is obtained. The rotation speed ratio N _s4 of the fourth sun gear 41 is the same as the rotation speed ratio N _s3 of the third sun gear 31, and the rotation speed ratio N _r4 of the fourth ring gear 43 is zero.

[Second Embodiment]
FIG. 14 is a schematic view of a planetary gear type transmission according to the second embodiment. As shown in FIG. 14, the planetary gear type transmission 100 shifts and outputs the rotational speed of power from an engine (not shown) or the like. Note that power from the engine or the like may be input to the planetary gear type transmission 100 via a torque converter.

The fourth carrier 44 outputs power. Specifically, the fourth carrier 44 outputs power having a rotational speed changed by the planetary gear type transmission 100. The fourth carrier 44 rotates integrally with the output shaft. For this reason, the output shaft 10 outputs the shifted power. The fourth carrier 44 and the output shaft 10 may be formed by a single member.

The third clutch 53 is configured to connect the first ring gear 13 and the first carrier 14. Specifically, the third clutch 53 connects the first ring gear 13 and the first carrier 14 so that they can be disconnected. The third clutch 53 is, for example, a hydraulic clutch mechanism, and can be composed of a plurality of disks.

When the third clutch 53 is on, the third clutch 53 connects the first ring gear 13 and the first carrier 14. Accordingly, the first ring gear 13 and the first carrier 14 rotate integrally.

When the third clutch 53 is in the off state, the third clutch 53 disconnects the connection between the first ring gear 13 and the first carrier 14. Therefore, the first ring gear 13 and the first carrier 14 can rotate relative to each other.

The third clutch 53 is disposed between the first braking mechanism 61 and the second braking mechanism 62 in the rotation axis direction. A space S is formed between the third clutch 53 and the casing 9 in the radial direction of the rotation shaft.

The operation of the planetary gear type transmission 100 configured as described above will be described. The planetary gear type transmission 100 has nine speed stages in the forward direction and two speed stages in the reverse direction.

Since the third clutch 53 is turned on, the first carrier 14 rotates integrally with the first ring gear 13. Further, since the fourth braking mechanism 64 is turned on, the fourth ring gear 43 cannot be rotated. Since the third carrier 34 rotates integrally with the fourth ring gear 43, the third carrier 34 also cannot rotate.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first sun gear 11 rotates integrally with the input shaft 7. And each 1st planetary gear 12 revolves and the 1st career 14 rotates. The first ring gear 13 rotates integrally with the first carrier 14. Each first planetary gear 12 does not rotate.

gears

In the forward 6th speed, no shift is performed as described above.

[Third Embodiment]
FIG. 26 is a schematic view of a planetary gear type transmission according to the third embodiment. As shown in FIG. 26, the planetary gear type transmission 100 shifts and outputs the rotational speed of power from an engine (not shown) or the like. Note that power from the engine or the like may be input to the planetary gear type transmission 100 via a torque converter.

The third clutch 53 is configured to connect the third ring gear 33 and the third carrier 34. Specifically, the third clutch 53 connects the third ring gear 33 and the third carrier 34 so that they can be disconnected. The third clutch 53 is, for example, a hydraulic clutch mechanism, and can be composed of a plurality of disks.

When the third clutch 53 is on, the third clutch 53 connects the third ring gear 33 and the third carrier 34. Therefore, the third ring gear 33 and the third carrier 34 rotate integrally.

When the third clutch 53 is in the off state, the third clutch 53 disconnects the connection between the third ring gear 33 and the third carrier 34. Therefore, the third ring gear 33 and the third carrier 34 can rotate relative to each other.

The third clutch 53 is disposed between the third planetary gear mechanism 3 and the fourth planetary gear mechanism 4 in the rotation axis direction. A space S is formed between the third clutch 53 and the casing 9 in the radial direction of the rotation shaft.

The operation of the planetary gear type transmission 100 configured as described above will be described. The planetary gear type transmission 100 has nine speed stages in the forward direction and two speed stages in the reverse direction. FIG. 27 is a table showing each clutch or each braking mechanism that is turned on at each speed stage. In FIG. 27, the ◯ marks indicate clutches or braking mechanisms that are turned on.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the first forward speed (F1), the first braking mechanism 61 is turned on and the fourth braking mechanism 64 is turned on. To. The second braking mechanism 62, the third braking mechanism 63, and the first to third clutches 51 to 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the second forward speed (F2), the first clutch 51 is turned on and the fourth braking mechanism 64 is turned on. To do. That is, in switching between the first speed (F1) and the second speed (F2), the fourth braking mechanism 64 is kept on. Note that the second clutch 52, the third clutch 53, and the first to third braking mechanisms 61 to 63 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the third forward speed (F3), the first clutch 51 is turned on and the first braking mechanism 61 is turned on. To do. That is, in switching between the second speed (F2) and the third speed (F3), the first clutch 51 remains on. The second to fourth braking mechanisms 62 to 64, the second clutch 52, and the third clutch 53 are in the off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the fourth forward speed (F4), the first clutch 51 is turned on and the second braking mechanism 62 is turned on. To do. That is, in switching between the third speed (F3) and the fourth speed (F4), the first clutch 51 remains on. The first braking mechanism 61, the third braking mechanism 63, the fourth braking mechanism 64, the second clutch 52, and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the fifth forward speed (F5), the first clutch 51 is turned on and the third braking mechanism 63 is turned on. To do. That is, in switching between the fourth speed (F4) and the fifth speed (F5), the first clutch 51 remains on. The first braking mechanism 61, the second braking mechanism 62, the fourth braking mechanism 64, the second clutch 52, and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the sixth forward speed (F6), the first clutch 51 is turned on and the second clutch 52 is turned on. . That is, in switching between the fifth speed (F5) and the sixth speed (F6), the first clutch 51 remains on. Note that the first to fourth braking mechanisms 61 to 64 and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the seventh forward speed (F7), the second clutch 52 is turned on and the third braking mechanism 63 is turned on. To do. That is, in switching between the sixth speed (F6) and the seventh speed (F7), the second clutch 52 remains on. The first braking mechanism 61, the second braking mechanism 62, the fourth braking mechanism 64, the first clutch 51, and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the eighth forward speed (F8), the second clutch 52 is turned on and the second braking mechanism 62 is turned on. To do. That is, in switching between the seventh speed (F7) and the eighth speed (F8), the second clutch 52 remains on. The first braking mechanism 61, the third braking mechanism 63, the fourth braking mechanism 64, the first clutch 51, and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the ninth forward speed (F9), the second clutch 52 is turned on and the first braking mechanism 61 is turned on. To do. That is, in switching between the eighth speed (F8) and the ninth speed (F9), the second clutch 52 remains on. The second to fourth braking mechanisms 62 to 64, the first clutch 51, and the third clutch 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the reverse first speed (R1), the third braking mechanism 63 is turned on and the fourth braking mechanism 64 is turned on. To. The first braking mechanism 61, the second braking mechanism 62, and the first to third clutches 51 to 53 are in an off state.

As shown in FIG. 27, when the speed stage of the planetary gear type transmission 100 is set to the second reverse speed (R2), the third clutch 53 is turned on and the first braking mechanism 61 is turned on. To do. The second to fourth braking mechanisms 62 to 64, the first clutch 51, and the second clutch 52 are in an off state.

Since the third clutch 53 is turned on, the third carrier 34 rotates integrally with the third ring gear 33. In addition, since the first braking mechanism 61 is turned on, the first carrier 14 cannot be rotated.

In this state, the planetary gear type transmission 100 transmits power through a route shown by a thick line in FIG. First, the first sun gear 11 rotates integrally with the input shaft 7. Then, each first planetary gear 12 rotates and the first ring gear 13 rotates. In addition, since the 1st carrier 14 cannot rotate, each 1st planetary gear 12 does not revolve.

The second carrier 24 rotates integrally with the first ring gear 13. The third ring gear 33 rotates integrally with the second carrier 24. The third carrier 34 rotates integrally with the third ring gear 33. For this reason, each 3rd planetary gear 32 revolves without rotating. Then, the third sun gear 31 rotates. That is, the third sun gear 31, the third ring gear 33, and the third carrier 34 rotate integrally with each other.

The fourth sun gear 41 rotates integrally with the third sun gear 31. The fourth ring gear 43 rotates integrally with the third carrier 34. Due to the rotation of the fourth sun gear 41 and the fourth ring gear 43, each fourth planetary gear 42 revolves without rotating. Then, the fourth carrier 44 rotates. That is, the first sun gear 41, the fourth ring gear 43, and the fourth carrier 44 rotate integrally with each other. As a result, the fourth carrier 44 outputs power having a shifted rotational speed.

gears

In the forward 6th speed, no shift is performed as described above.

In the second reverse speed, the rotation speed ratio N _r1 of the first ring gear 13 is obtained by the first relational expression. The rotation speed ratio N _s1 of the first sun gear 11 is 1, and the rotation speed ratio N _c1 of the first carrier 14 is 0.

The rotation speed ratio N _c4 of the fourth carrier 44 is the same as the rotation speed ratio N _r1 of the first ring gear 13. As a result, the reduction ratio in the second reverse speed is obtained.

As described above, the planetary gear type transmission according to each embodiment can have two speed stages in reverse.

[Modification]
As mentioned above, although each embodiment of this invention was described, this invention is not limited to these, A various change is possible unless it deviates from the meaning of this invention. For example, in the above embodiment, the second clutch 52 is configured to connect the input shaft 7 and the third carrier 34 via the second intermediate shaft, but is not particularly limited thereto. That is, the second clutch 52 may be configured to directly connect the input shaft 7 and the third carrier 34.

In each of the above embodiments, the second braking mechanism 62 is configured to brake the rotation of the first ring gear 13, but the second braking mechanism 62 includes the first ring gear 13, the second carrier 24, And what is necessary is just to be comprised so that at least 1 rotation of the 3rd ring gear 33 may be braked. For example, as shown in FIG. 39, the second braking mechanism 62 may be configured to brake the rotation of the third ring gear 33. In addition, the 1st ring gear 13, the 2nd carrier 24, and the 3rd ring gear 33 rotate integrally. Therefore, in each embodiment, even if the second braking mechanism 62 is configured to brake the rotation of the second carrier 24 or the third ring gear 33, the operation of the planetary gear type transmission, that is, each speed stage is set. The ON / OFF state of each clutch and each braking mechanism, the power transmission path, and the like are the same as those described in the above embodiments.

DESCRIPTION OF SYMBOLS 1 1st planetary gear mechanism 11 1st sun gear 12 1st planetary gear 13 1st ring gear 14 1st carrier 2 2nd planetary gear mechanism 21 2nd sun gear 22 2nd planetary gear 23 2nd ring gear 24 2nd carrier 3 2nd carrier 3 planetary gear mechanism 31 3rd sun gear 32 3rd planetary gear 33 3rd ring gear 34 3rd carrier 4 4th planetary gear mechanism 41 4th sun gear 42 4th planetary gear 43 4th ring gear 44 4th carrier 51 1st clutch 52 Second clutch 53 Third clutch 61 First braking mechanism 62 Second braking mechanism 63 Third braking mechanism 7 Input shaft 81 First intermediate shaft 82 Second intermediate shaft 9 Casing 100 Planetary gear type transmission

Claims

An input shaft configured to rotate about a rotation axis;
A first intermediate shaft configured to rotate about the rotational shaft;
A first planetary gear mechanism having a first sun gear, a first planetary gear, a first ring gear, and a first carrier configured to rotate integrally with the input shaft;
A second sun gear configured to rotate integrally with the input shaft, a second planetary gear, a second ring gear, and a second carrier configured to rotate integrally with the first ring gear; A second planetary gear mechanism having;
A third sun gear configured to rotate integrally with the first intermediate shaft, a third planetary gear, a third ring gear configured to rotate integrally with the second carrier, and a third carrier; A third planetary gear mechanism having
A fourth sun gear configured to rotate integrally with the first intermediate shaft, a fourth planetary gear, a fourth ring gear configured to rotate integrally with the third carrier, and output power A fourth planetary gear mechanism having a fourth carrier configured as follows:
A first clutch configured to connect the input shaft and the first intermediate shaft;
A second clutch configured to connect the input shaft and the third carrier;
A third clutch configured to connect the input shaft and the first carrier;
A first braking mechanism configured to brake rotation of the first carrier;
A second braking mechanism configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear;
A third braking mechanism configured to brake rotation of the second ring gear;
A fourth braking mechanism configured to brake rotation of the fourth ring gear;
A planetary gear type transmission comprising:
An input shaft configured to rotate about a rotation axis;
A first intermediate shaft configured to rotate about the rotational shaft;
A first planetary gear mechanism having a first sun gear, a first planetary gear, a first ring gear, and a first carrier configured to rotate integrally with the input shaft;
A second sun gear configured to rotate integrally with the input shaft, a second planetary gear, a second ring gear, and a second carrier configured to rotate integrally with the first ring gear; A second planetary gear mechanism having;
A third sun gear configured to rotate integrally with the first intermediate shaft, a third planetary gear, a third ring gear configured to rotate integrally with the second carrier, and a third carrier; A third planetary gear mechanism having
A fourth sun gear configured to rotate integrally with the first intermediate shaft, a fourth planetary gear, a fourth ring gear configured to rotate integrally with the third carrier, and output power A fourth planetary gear mechanism having a fourth carrier configured as follows:
A first clutch configured to connect the input shaft and the first intermediate shaft;
A second clutch configured to connect the input shaft and the third carrier;
A third clutch configured to connect the first carrier and the first ring gear;
A first braking mechanism configured to brake rotation of the first carrier;
A second braking mechanism configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear;
A third braking mechanism configured to brake rotation of the second ring gear;
A fourth braking mechanism configured to brake rotation of the fourth ring gear;
A planetary gear type transmission comprising:
An input shaft configured to rotate about a rotation axis;
A first intermediate shaft configured to rotate about the rotational shaft;
A first planetary gear mechanism having a first sun gear, a first planetary gear, a first ring gear, and a first carrier configured to rotate integrally with the input shaft;
A second sun gear configured to rotate integrally with the input shaft, a second planetary gear, a second ring gear, and a second carrier configured to rotate integrally with the first ring gear; A second planetary gear mechanism having;
A third sun gear configured to rotate integrally with the first intermediate shaft, a third planetary gear, a third ring gear configured to rotate integrally with the second carrier, and a third carrier; A third planetary gear mechanism having
A fourth sun gear configured to rotate integrally with the first intermediate shaft, a fourth planetary gear, a fourth ring gear configured to rotate integrally with the third carrier, and output power A fourth planetary gear mechanism having a fourth carrier configured as follows:
A first clutch configured to connect the input shaft and the first intermediate shaft;
A second clutch configured to connect the input shaft and the third carrier;
A third clutch configured to connect the third ring gear and the third carrier;
A first braking mechanism configured to brake rotation of the first carrier;
A second braking mechanism configured to brake at least one rotation of the first ring gear, the second carrier, and the third ring gear;
A third braking mechanism configured to brake rotation of the second ring gear;
A fourth braking mechanism configured to brake rotation of the fourth ring gear;
A planetary gear type transmission comprising:
The input shaft is hollow,
The first intermediate shaft is disposed within the input shaft;
The planetary gear type transmission according to any one of claims 1 to 3.
A second intermediate shaft disposed between the input shaft and the first intermediate shaft and configured to rotate integrally with the third carrier;
The planetary gear type transmission according to claim 4.
An output shaft configured to rotate integrally with the fourth carrier;
The planetary gear transmission according to any one of claims 1 to 5.
The first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism are arranged in this order along the rotation axis direction.
The planetary gear type transmission according to any one of claims 1 to 6.
A casing that accommodates each planetary gear mechanism;
In the radial direction of the rotating shaft, a space is formed between the third clutch and the casing.
The planetary gear transmission according to any one of claims 1 to 7.
The second braking mechanism is disposed on the radially outer side of the first ring gear,
The first braking mechanism is disposed on the input side in the rotation axis direction with respect to the second braking mechanism,
The third clutch is disposed between the first braking mechanism and the second braking mechanism in the rotation axis direction.
The planetary gear transmission according to claim 8.
The third clutch is disposed between the third planetary gear mechanism and the fourth planetary gear mechanism in the rotation axis direction.
The planetary gear type converter according to claim 8.