WO2022255011A1

WO2022255011A1 - Multi-speed transmission

Info

Publication number: WO2022255011A1
Application number: PCT/JP2022/019086
Authority: WO
Inventors: 拓松尾; 伸人安田; 正樹塩原; 倫弘相田
Original assignee: 株式会社小松製作所
Priority date: 2021-06-01
Filing date: 2022-04-27
Publication date: 2022-12-08
Also published as: JP2022184479A

Abstract

The present invention achieves an increase in the number of speed positions, a reduction in the number of parts, and an increase in an overall step ratio. A multi-speed transmission (100) comprises an input member (7), an output member (10), first to third planetary gear sets (1-3), first to fourth clutches (51-54), and first and second brakes (61, 62). Each of the planetary gear sets (1-3) includes a sun gear, a planetary carrier, and a ring gear. At least one of the first to fourth clutches (51-54) and the first and second brakes (61, 62) is operably coupled to each of the planetary gear sets (1-3) and can be selectively engaged therewith so as to generate a set of different gear ratios including at least the gear ratios of 10 forward positions and at least the gear ratio of one reverse position between the input member (7) and the output member (10). The first clutch (51) selectively couples a first sun gear (11) of the first planetary gear set (1) and a second ring gear (23) of the second planetary gear set (2) to each other.

Description

multi-speed transmission

The present disclosure relates to a multi-speed transmission.

A work vehicle such as a dump truck is equipped with a multi-speed transmission with multiple planetary gear sets. A planetary gear type multi-speed transmission can obtain a desired reduction ratio by appropriately combining the rotating elements of each planetary gear set. A conventional planetary gear transmission is disclosed, for example, in US Pat. No. 9,188,200.

U.S. Pat. No. 9,188,200

In multi-speed transmissions, there is a demand for an increase in the number of speed stages in order to improve fuel efficiency and driving performance, and a reduction in the number of parts to reduce weight and size. In order to improve the maximum vehicle speed, there is a demand for an increase in the total inter-stage ratio.

This disclosure proposes a multi-speed transmission that can increase the number of speed stages, reduce the number of parts, and increase the total inter-stage ratio.

A multi-speed transmission according to one aspect of the present disclosure includes an input member and an output member. A multi-speed transmission has no more than three planetary gear sets. Each planetary gear set includes a sun gear, a planet carrier and a ring gear. A multi-speed transmission has six or fewer control elements. At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between the input and output members. The set of different gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio. One control element of the six or less control elements is the sun gear of one planetary gear set of the three or less planetary gear sets and the other one of the three or less planetary gear sets. and a ring gear of one planetary gear set.

According to the multi-stage transmission of the present disclosure, it is possible to increase the number of speed stages, reduce the number of parts, and increase the total inter-stage ratio.

1 is a schematic diagram of a multi-stage transmission according to a first embodiment; FIG. 4 is a table showing each clutch or each brake that is turned on in each speed stage of the multi-stage transmission according to the first embodiment; 4 is a table showing gear ratios in each planetary gear set of the multi-stage transmission according to the first embodiment; It is a schematic diagram of a multi-stage transmission according to a second embodiment. 9 is a table showing each clutch or each brake that is turned on in each speed stage of the multi-stage transmission according to the second embodiment; 9 is a table showing gear ratios in each planetary gear set of the multi-stage transmission according to the second embodiment;

Each embodiment of the multi-stage transmission 100 will be described below with reference to the drawings. In the following description, the rotation axis direction indicates the direction in which the rotation axis O extends. The radial direction indicates the radial direction of a circle centered on the rotation axis O. As shown in FIG. In FIG. 1, the rotation axis direction is the horizontal direction in the drawing, and the radial direction is the vertical direction in the drawing. A rotation axis O indicates the centerline of the input member 7 and the output member 10 . The input side indicates the side to which multi-speed transmission 100 inputs power. The output side indicates the side to which multi-speed transmission 100 outputs power. In FIG. 1, the input side is on the left side of the drawing and the output side is on the right side of the drawing.

[First embodiment]
FIG. 1 is a schematic diagram of a multi-stage transmission 100 according to the first embodiment. Multi-speed transmission 100 changes the rotation speed of power input from an arbitrary drive source (not shown) such as an internal combustion engine typified by a diesel engine and an electric motor, and outputs the power. Power from the drive source may be input to multi-speed transmission 100 via a torque converter.

The multi-speed transmission 100 includes a plurality of planetary gear sets 1-3, a plurality of clutches 51-54, a plurality of brakes 61-62, an input member 7, a first intermediate coupling member 81, a second intermediate coupling member 82, an output member 10 , and housing 9 . Each planetary gear set 1-3, each clutch 51-54, each brake 61-62, input member 7, first intermediate coupling member 81, second intermediate coupling member 82, and output member 10 are accommodated in housing 9. there is

The plurality of planetary gear sets includes a first planetary gear set 1, a second planetary gear set 2, and a third planetary gear set 3. The multiple clutches include a first clutch 51 , a second clutch 52 , a third clutch 53 and a fourth clutch 54 . The multiple brakes include a first brake 61 and a second brake 62 . Each of the clutches 51-54 and each of the brakes 61-62 corresponds to the control element of the embodiment. The six control elements include first clutch 51 , second clutch 52 , third clutch 53 , fourth clutch 54 , first brake 61 and second brake 62 .

The first planetary gear set 1, the second planetary gear set 2, and the third planetary gear set 3 are rotatably supported around the rotation axis O. The first planetary gear set 1, the second planetary gear set 2, and the third planetary gear set 3 are arranged in this order along the rotation axis direction. Specifically, the first planetary gear set 1, the second planetary gear set 2, and the third planetary gear set 3 are arranged in this order from the input side to the output side.

The input member 7 is configured to rotate around the rotation axis O. The rotation axis O is the centerline of the input member 7 . Power from an engine or the like is input to the input member 7 .

The first intermediate coupling member 81 is configured to rotate around the rotation axis O. The first intermediate coupling member 81 extends in the rotation axis direction. The centerline of the first intermediate coupling member 81 and the centerline of the input member 7 are substantially the same.

The second intermediate coupling member 82 is configured to rotate around the rotation axis O. The second intermediate coupling member 82 is hollow. The first intermediate coupling member 81 is arranged radially inside the second intermediate coupling member 82 . The centerline of the second intermediate coupling member 82 and the centerline of the input member 7 are substantially the same.

The first planetary gear set 1 is a single pinion planetary gear mechanism. The first planetary gear set 1 has a first sun gear 11, a plurality of first planetary gears 12, a first ring gear 13, and a first planetary carrier 14 as rotating elements.

The first sun gear 11 is rotatably arranged around the rotation axis O. The first sun gear 11 is arranged radially outside the input member 7 . Specifically, the first sun gear 11 is annular, and the input member 7 penetrates the first sun gear 11 . The first sun gear 11 and the input member 7 are relatively rotatable.

Each first planetary gear 12 is configured to mesh with the first sun gear 11 . Each first planetary gear 12 is arranged radially outside the first sun gear 11 . Specifically, the first planetary gears 12 are spaced apart in the circumferential direction.

Each first planetary gear 12 is configured to revolve around the first sun gear 11 . Each first planetary gear 12 is configured to rotate around the rotation axis O. As shown in FIG. Each first planetary gear 12 is configured to rotate.

The first ring gear 13 meshes with each first planetary gear 12 . The first ring gear 13 is configured to rotate about the rotation axis O. As shown in FIG.

The first ring gear 13 is configured to rotate integrally with the first intermediate coupling member 81 . Specifically, the first ring gear 13 is fixed to the first intermediate coupling member 81 . The first ring gear 13 and the first intermediate coupling member 81 may be formed by one member.

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

The first planetary carrier 14 is configured to rotate integrally with the input member 7 . Specifically, the first planetary carrier 14 is fixed to the input member 7 . The input member 7 is continuously connected to the first planetary carrier 14 of the first planetary gearset 1 . The first planetary carrier 14 and the input member 7 may be formed by one member.

The second planetary gear set 2 is a single pinion planetary gear mechanism. The second planetary gear set 2 has a second sun gear 21, a plurality of second planetary gears 22, a second ring gear 23, and a second planetary carrier 24 as rotating elements.

The second sun gear 21 is configured to rotate around the rotation axis O. The second sun gear 21 is arranged radially outside the first intermediate coupling member 81 . Specifically, the second sun gear 21 is annular, and the first intermediate coupling member 81 penetrates the second sun gear 21 . The second sun gear 21 and the first intermediate coupling member 81 are relatively rotatable.

The second sun gear 21 is configured to rotate integrally with the second intermediate coupling member 82 . Specifically, the second sun gear 21 is fixed to the second intermediate coupling member 82 . The second sun gear 21 and the second intermediate coupling member 82 may be formed by one member.

Each second planetary gear 22 is configured to mesh with the second sun gear 21 . Each second planetary gear 22 is arranged radially outside the second sun gear 21 . Specifically, the second planetary gears 22 are spaced apart in the circumferential direction.

Each second planetary gear 22 is configured to revolve around the second sun gear 21 . Each second planetary gear 22 is configured to rotate around the rotation axis O. As shown in FIG. 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. As shown in FIG.

The second planetary carrier 24 supports each second planetary gear 22 . Each second planetary gear 22 is rotatable while being supported by the second planetary carrier 24 . The second planetary carrier 24 is configured to rotate around the rotation axis O. As shown in FIG.

The third planetary gear set 3 is a single pinion planetary gear mechanism. The third planetary gear set 3 has a third sun gear 31, a plurality of third planetary gears 32, a third ring gear 33, and a third planetary carrier 34 as rotating elements.

The third sun gear 31 is configured to rotate together with the first intermediate coupling member 81 . Specifically, the third sun gear 31 is fixed to the first intermediate coupling member 81 . The third sun gear 31 and the first intermediate coupling member 81 may be formed by one member. The first intermediate coupling member 81 is continuously connected to the first ring gear 13 of the first planetary gear set 1 and the third sun gear 31 of the third planetary gear set 3 . The first ring gear 13 and the third sun gear 31 are configured to rotate integrally with each other.

Each third planetary gear 32 is configured to mesh with the third sun gear 31 . Each third planetary gear 32 is arranged radially outside the third sun gear 31 . Specifically, the third planetary gears 32 are spaced apart in the circumferential direction.

Each third planetary gear 32 is configured to revolve around the third sun gear 31 . Each third planetary gear 32 is configured to rotate about the rotation axis O. As shown in FIG. Each third planetary gear 32 is configured to rotate.

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

The third ring gear 33 is configured to rotate integrally with the second intermediate coupling member 82 . Specifically, the third ring gear 33 is fixed to the second intermediate coupling member 82 . The third ring gear 33 and the second intermediate coupling member 82 may be formed by one member. The second intermediate coupling member 82 is continuously connected to the second sun gear 21 of the second planetary gear set 2 and the third ring gear 33 of the third planetary gear set 3 . The second sun gear 21 and the third ring gear 33 are configured to rotate integrally with each other.

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

The third planetary carrier 34 is configured to rotate integrally with the output member 10 . A third planetary carrier 34 is fixed to the output member 10 . The output member 10 is continuously connected to the third planetary carrier 34 of the third planetary gearset 3 . The third planetary carrier 34 and the output member 10 may be formed by one member. The output member 10 outputs power. Specifically, the output member 10 outputs power having a rotation speed changed by the multi-speed transmission 100 .

The first clutch 51 is configured to selectively connect the first sun gear 11 of the first planetary gear set 1 and the second ring gear 23 of the second planetary gear set 2 . The first clutch 51 is, for example, a hydraulic clutch mechanism and can be composed of a plurality of discs.

The first clutch 51 connects the first sun gear 11 and the second ring gear 23 when in the ON state. Therefore, the first sun gear 11 and the second ring gear 23 rotate integrally. The first clutch 51 releases the connection between the first sun gear 11 and the second ring gear 23 when in the OFF state. Therefore, the first sun gear 11 and the second ring gear 23 are rotatable relative to each other.

The second clutch 52 is configured to selectively connect the first planetary carrier 14 of the first planetary gearset 1 and the second ring gear 23 of the second planetary gearset 2 . The second clutch 52 is, for example, a hydraulic clutch mechanism and can be composed of a plurality of discs.

The second clutch 52 connects the first planetary carrier 14 and the second ring gear 23 when in the ON state. Therefore, the first planetary carrier 14 and the second ring gear 23 rotate integrally. The second clutch 52 releases the connection between the first planetary carrier 14 and the second ring gear 23 when in the OFF state. Therefore, the first planetary carrier 14 and the second ring gear 23 are rotatable relative to each other.

The third clutch 53 is configured to selectively connect the second planetary carrier 24 of the second planetary gear set 2 and the first intermediate coupling member 81 . The third clutch 53 is configured to selectively couple the second planetary carrier 24 with the first ring gear 13 of the first planetary gearset 1 and the third sun gear 31 of the third planetary gearset 3. . The third clutch 53 is, for example, a hydraulic clutch mechanism and can be composed of a plurality of discs.

The third clutch 53 connects the second planetary carrier 24 and the first intermediate coupling member 81 when in the ON state. The third clutch 53 connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 via the first intermediate coupling member 81 when in the ON state. Therefore, the second planetary carrier 24, the first ring gear 13, and the third sun gear 31 rotate integrally. The third clutch 53 releases the connection between the second planetary carrier 24 and the first intermediate coupling member 81 when in the OFF state. Therefore, the second planetary carrier 24 is rotatable relative to the first ring gear 13 and the third sun gear 31 .

The fourth clutch 54 is configured to selectively couple the second planetary carrier 24 of the second planetary gearset 2 and the third planetary carrier 34 of the third planetary gearset 3 . The fourth clutch 54 is, for example, a hydraulic clutch mechanism and can be composed of a plurality of discs.

The fourth clutch 54 connects the second planetary carrier 24 and the third planetary carrier 34 when in the ON state. Therefore, the second planetary carrier 24 and the third planetary carrier 34 rotate integrally. The fourth clutch 54 releases the connection between the second planetary carrier 24 and the third planetary carrier 34 when in the OFF state. Therefore, the second planetary carrier 24 and the third planetary carrier 34 are rotatable relative to each other.

The first brake 61 is configured to selectively connect the first sun gear 11 of the first planetary gear set 1 and the housing 9 .

The first brake 61 connects the first sun gear 11 and the housing 9 when in the ON state. The ON-state first brake 61 brakes the rotation of the first sun gear 11, and the first sun gear 11 cannot rotate. The first brake 61 releases the connection between the first sun gear 11 and the housing 9 when in the OFF state. The first brake 61 in the OFF state does not brake the rotation of the first sun gear 11, and the first sun gear 11 is rotatable.

The second brake 62 is configured to selectively connect the second sun gear 21 of the second planetary gear set 2 and the third ring gear 33 of the third planetary gear set 3 with the housing 9 .

The second brake 62 connects the second sun gear 21 and the housing 9 and connects the third ring gear 33 and the housing 9 when in the ON state. The second brake 62 in the ON state brakes the rotation of the second sun gear 21 and the third ring gear 33 so that the second sun gear 21 and the third ring gear 33 cannot rotate. The second brake 62 releases the connection between the second sun gear 21 and the housing 9 and the connection between the third ring gear 33 and the housing 9 when in the OFF state. The second brake 62 in the OFF state does not brake the rotation of the second sun gear 21 and the third ring gear 33, and the second sun gear 21 and the third ring gear 33 are rotatable.

In the multi-stage transmission 100 configured as described above, the first to fourth clutches 51 to 54 and the first to second brakes 61 to 62 are operable in the first to third planetary gear sets 1 to 3. Combined. By selectively engaging the first to fourth clutches 51 to 54 and the first to second brakes 61 to 62 to restrict the rotation of the rotating elements of the first to third planetary gear sets 1 to 3 , a set of different gear ratios between the input member 7 and the output member 10 is produced. The set of different gear ratios includes at least ten forward gear ratios and one reverse gear ratio.

FIG. 2 is a table showing the clutches 51-54 or the brakes 61-62 that are turned on at each speed stage of the multi-stage transmission 100 according to the first embodiment. FIG. 2 shows operating states of the first to fourth clutches 51 to 54 and the first to second brakes 61 to 62 corresponding to each speed stage. When the columns of the first to fourth clutches 51 to 54 and the first to second brakes 61 to 62 are crossed, they are in the on (engaged) state. (engaged) state.

When the speed stage of the multi-speed transmission 100 is set to forward first speed (F1), the second clutch 52, the third clutch 53 and the second brake 62 are turned on, and the first clutch 51, the fourth clutch 54 and the second clutch 54 are turned on. The first brake 61 is turned off. The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When setting the speed stage of the multi-speed transmission 100 to the forward second speed (F2), the first clutch 51, the third clutch 53 and the second brake 62 are turned on, and the second clutch 52 and the fourth clutch 54 are turned on. and the first brake 61 is turned off. The first clutch 51 in the ON state connects the first sun gear 11 and the second ring gear 23 . The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When setting the speed stage of the multi-speed transmission 100 to the forward third speed (F3), the first clutch 51, the second clutch 52 and the second brake 62 are turned on, and the third clutch 53 and the fourth clutch 54 are turned on. and the first brake 61 is turned off. The first clutch 51 in the ON state connects the first sun gear 11 and the second ring gear 23 . The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When the speed stage of the multi-speed transmission 100 is set to the forward fourth speed (F4), the first clutch 51, the fourth clutch 54 and the second brake 62 are turned on, and the second clutch 52 and the third clutch 53 are turned on. and the first brake 61 is turned off. The first clutch 51 in the ON state connects the first sun gear 11 and the second ring gear 23 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When setting the speed stage of the multi-speed transmission 100 to the forward fifth speed (F5), the fourth clutch 54, the first brake 61 and the second brake 62 are turned on, and the first clutch 51 and the second clutch 52 are turned on. and the third clutch 53 are turned off. The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When the speed stage of the multi-speed transmission 100 is set to the forward sixth speed (F6), the second clutch 52, the fourth clutch 54 and the second brake 62 are turned on, and the first clutch 51 and the third clutch 53 are turned on. and the first brake 61 is turned off. The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The on-state second brake 62 brakes the rotation of the second sun gear 21 and the third ring gear 33 .

When setting the speed stage of the multi-speed transmission 100 to the forward seventh speed (F7), the second clutch 52, the fourth clutch 54 and the first brake 61 are turned on, and the first clutch 51 and the third clutch 53 are turned on. and the second brake 62 is turned off. The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 .

When the speed stage of the multi-speed transmission 100 is set to the forward eighth speed (F8), the second clutch 52, the third clutch 53 and the fourth clutch 54 are turned on, and the first clutch 51 and the first brake 61 are turned on. and the second brake 62 is turned off. The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 .

When setting the speed stage of the multi-speed transmission 100 to the forward ninth speed (F9), the third clutch 53, the fourth clutch 54 and the first brake 61 are turned on, and the first clutch 51 and the second clutch 52 are turned on. and the second brake 62 is turned off. The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 .

When setting the speed stage of the multi-speed transmission 100 to forward tenth speed (F10), the second clutch 52, the third clutch 53 and the first brake 61 are turned on, and the first clutch 51 and the fourth clutch 54 are turned on. and the second brake 62 is turned off. The second clutch 52 in the ON state connects the first planetary carrier 14 and the second ring gear 23 . The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 .

When the speed stage of the multi-speed transmission 100 is set to the reverse first speed (R1), the first clutch 51, the fourth clutch 54 and the first brake 61 are turned on, and the second clutch 52 and the third clutch 53 are turned on. and the second brake 62 is turned off. The first clutch 51 in the ON state connects the first sun gear 11 and the second ring gear 23 . The fourth clutch 54 in the ON state connects the second planetary carrier 24 and the third planetary carrier 34 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 .

When the speed stage of the multi-speed transmission 100 is set to the forward 11th speed (F11), which is an additional speed stage, the first clutch 51, the third clutch 53 and the first brake 61 are turned on, and the second clutch is turned on. 52, the fourth clutch 54 and the second brake 62 are turned off. The first clutch 51 in the ON state connects the first sun gear 11 and the second ring gear 23 . The third clutch in the ON state connects the second planetary carrier 24 with the first ring gear 13 and the third sun gear 31 . The ON-state first brake 61 brakes the rotation of the first sun gear 11 .

Here, for each planetary gear set 1 to 3, the number of teeth of the sun gear is a, the number of teeth of the ring gear is b, the rotation speed ratio of the sun gear is Na, the rotation speed ratio of the ring gear is Nb, and the rotation speed ratio of the planetary carrier is Nc. Then, the following relational expression holds. The rotation speed ratio of each gear means the ratio of the rotation speed of each gear to the rotation speed of the input member 7 .

a·Na+b·Nb=(a+b)·Nc
The ratio of the number of teeth of the ring gear to the number of teeth of the sun gear (tooth ratio) in each of the planetary gear sets 1 to 3 is as shown in FIG. FIG. 3 is a table showing gear ratios of the planetary gear sets 1 to 3 of the multi-stage transmission 100 according to the first embodiment.

The speed reduction ratio in each speed stage described above, shown in FIG. 2, can be obtained using the above relational expression and the gear ratio shown in FIG.

It should be noted that the interstage ratio shown in FIG. 2 represents the ratio of the speed reduction ratios of the respective speed stages. Specifically, regarding the speed reduction ratios of adjacent speed stages, a value obtained by dividing the speed reduction ratio of the low speed stage by the speed reduction ratio of the high speed stage is called the interstage ratio. The total interstage ratio is a value obtained by dividing the reduction ratio of the lowest speed stage by the reduction ratio of the highest speed stage. The multi-speed transmission 100 of this embodiment has ten forward speed stages. The total interstage ratio of the multi-speed transmission 100 of the present embodiment is a value obtained by dividing the speed reduction ratio of the 1st forward speed by the speed reduction ratio of the 10th forward speed.

The multi-stage transmission 100 of the present embodiment has ten forward speed stages and one reverse speed stage, and the number of speed stages of the multi-stage transmission 100 is increased. As a result, it is possible to improve the fuel consumption of the vehicle equipped with the multi-speed transmission 100, and improve the running performance of the vehicle equipped with the multi-speed transmission 100.

In this embodiment, in order to realize 10 forward speeds and 1 reverse speed, the multi-speed transmission 100 includes three planetary gear sets 1-3 and a total of six control elements (first to fourth clutches 51-54). and first and second brakes 61-62), and the number of parts is reduced. As a result, weight reduction and compactness of the multi-speed transmission 100 can be achieved.

In the multi-stage transmission 100 of the present embodiment, the total inter-stage ratio shown in FIG. 2 is 8.23, and the total inter-stage ratio is expanded. As a result, the maximum tractive force of the vehicle equipped with the multi-speed transmission 100 can be improved, and the maximum vehicle speed can also be improved.

[Second embodiment]
FIG. 4 is a schematic diagram of a multi-stage transmission 100 according to the second embodiment. FIG. 5 is a table showing the clutches 51-54 or the brakes 61-62 that are turned on at each speed stage of the multi-stage transmission 100 according to the second embodiment. FIG. 6 is a table showing the gear ratios of the planetary gear sets 1 to 3 of the multi-stage transmission 100 according to the second embodiment.

As shown in FIG. 6, the multi-speed transmission 100 according to the second embodiment is different from the first embodiment in that the three or less planetary gear sets 1 to 3 include at least one double-pinion planetary gear mechanism. different from the form. Specifically, in the multi-stage transmission 100 according to the second embodiment, the second planetary gear set 2 is configured as a double pinion planetary gear mechanism.

The second planetary gear 22 of the second planetary gear set 2 has an inner pinion gear and an outer pinion gear. The inner pinion gear meshes with the second sun gear 21 . The outer pinion gear meshes with the second ring gear 23 . The inner pinion gear and the outer pinion gear are also meshed with each other. The inner pinion gear is spaced radially inward from the second ring gear 23 , and the outer pinion gear is spaced radially outward from the second sun gear 21 . The second planetary carrier 24 rotatably supports both the inner pinion gear and the outer pinion gear.

As shown in FIG. 4, the first clutch 51 is configured to selectively couple the first sun gear 11 of the first planetary gearset 1 and the second planetary carrier 24 of the second planetary gearset 2. It is The first clutch 51 is configured to selectively connect the first sun gear 11 and the second planetary carrier 24 when in the ON state. Therefore, the first sun gear 11 and the second planetary carrier 24 rotate integrally. The first clutch 51 releases the connection between the first sun gear 11 and the second planetary carrier 24 when in the OFF state. Therefore, the first sun gear 11 and the second planetary carrier 24 are rotatable relative to each other.

The second clutch 52 is configured to selectively couple the first planetary carrier 14 of the first planetary gearset 1 and the second planetary carrier 24 of the second planetary gearset 2 . The second clutch 52 connects the first planetary carrier 14 and the second planetary carrier 24 when in the ON state. Therefore, the first planetary carrier 14 and the second planetary carrier 24 rotate integrally. The second clutch 52 releases the connection between the first planetary carrier 14 and the second planetary carrier 24 when in the OFF state. Therefore, the first planetary carrier 14 and the second planetary carrier 24 are rotatable relative to each other.

The third clutch 53 is configured to selectively connect the second ring gear 23 of the second planetary gear set 2 and the first intermediate coupling member 81 . The third clutch 53 is configured to selectively connect the second ring gear 23 with the first ring gear 13 of the first planetary gear set 1 and the third sun gear 31 of the third planetary gear set 3 .

The third clutch 53 connects the second ring gear 23 and the first intermediate coupling member 81 when in the ON state. The third clutch 53 connects the second ring gear 23 and the first ring gear 13 and connects the second ring gear 23 and the third sun gear 31 via the first intermediate connecting member 81 when in the ON state. Therefore, the second ring gear 23, the first ring gear 13, and the third sun gear 31 rotate integrally. The third clutch 53 releases the connection between the second ring gear 23 and the first intermediate coupling member 81 when in the OFF state. Therefore, the second ring gear 23 is relatively rotatable with respect to the first ring gear 13 and the third sun gear 31 .

The fourth clutch 54 is configured to selectively connect the second ring gear 23 of the second planetary gearset 2 and the third planetary carrier 34 of the third planetary gearset 3 . The fourth clutch 54 connects the second ring gear 23 and the third planetary carrier 34 when in the ON state. Therefore, the second ring gear 23 and the third planetary carrier 34 rotate integrally. The fourth clutch 54 releases the connection between the second ring gear 23 and the third planetary carrier 34 when in the OFF state. Therefore, the second ring gear 23 and the third planetary carrier 34 are rotatable relative to each other.

In the multi-stage transmission 100 of the second embodiment configured as described above, the first to fourth clutches 51 to 54 and the first to second brakes 61 to 62 are selectively engaged as shown in FIG. Together, by restricting the rotation of the rotating elements of the first to third planetary gear sets 1 to 3, a gear ratio of 10 forward speeds and 1 reverse speed can be realized. Also in the multi-stage transmission 100 of the second embodiment, it is possible to increase the number of speed stages of the multi-stage transmission 100, reduce the number of parts, and increase the total inter-stage ratio, as in the first embodiment. .

The multi-speed transmission 100 of the above-described embodiment can be used for any machine equipped with a multi-speed transmission, but is particularly applicable to construction and mining machines such as dump trucks.

The embodiments disclosed this time should be considered illustrative in all respects and not restrictive. The scope of the present invention is indicated by the scope of the claims rather than the above description, and is intended to include all changes within the scope and meaning equivalent to the scope of the claims.

1 first planetary gear set, 2 second planetary gear set, 3 third planetary gear set, 7 input member, 9 housing, 10 output member, 11 first sun gear, 12 first planetary gear, 13 first ring gear, 14 first Planet carrier, 21 Second sun gear, 22 Second planetary gear, 23 Second ring gear, 24 Second planet carrier, 31 Third sun gear, 32 Third planetary gear, 33 Third ring gear, 34 Third planet carrier, 51 First clutch, 52 Second clutch, 53 Third clutch, 54 Fourth clutch, 61 First brake, 62 Second brake, 81 First intermediate coupling member, 82 Second intermediate coupling member, 100 Multi-speed transmission, O Rotation axis.

Claims

an input member;
an output member;
no more than three planetary gear sets, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
One control element of the six or less control elements is the sun gear of one planetary gear set of the three or less planetary gear sets and the other of the three or less planetary gear sets. and the ring gear of one planetary gear set.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission further comprising an intermediate coupling member continuously connected to the sun gear of the second planetary gear set and the ring gear of the third planetary gear set.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission, wherein one control element of said six or fewer control elements selectively couples said sun gear of said first planetary gearset and said ring gear of said second planetary gearset.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission wherein one control element of said six or fewer control elements selectively couples said planetary carrier of said second planetary gearset and said planetary carrier of said third planetary gearset.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission, wherein one control element of the six or fewer control elements selectively couples the planetary carrier of the first planetary gearset and the planetary carrier of the second planetary gearset.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission, wherein one control element of said six or fewer control elements selectively couples said ring gear of said first planetary gearset and said ring gear of said second planetary gearset.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission, wherein one control element of said six or fewer control elements selectively couples said ring gear of said second planetary gearset and said sun gear of said third planetary gearset.
an input member;
an output member;
a first planetary gear set connected to said input member, a second planetary gear set connected to said input member, a third planetary gear set connected to said output member, each including a sun gear, a planet carrier and a ring gear;
6 or less control elements,
At least one control element is operably coupled to each planetary gear set and is selectively engageable to produce different sets of gear ratios between said input member and said output member; the set of gear ratios includes at least ten forward gear ratios and at least one reverse gear ratio;
A multi-speed transmission wherein one control element of said six or fewer control elements selectively couples said ring gear of said second planetary gearset and said planetary carrier of said third planetary gearset.
9. The multi-speed transmission of any one of claims 3 to 8, further comprising an intermediate coupling member continuously connected to the ring gear of the first planetary gearset and the sun gear of the third planetary gearset. machine.
The multi-speed transmission according to any one of claims 2 to 9, wherein said input member is continuously connected to said planet carrier of said first planetary gear set.
The multi-speed transmission according to any one of claims 2 to 10, wherein said output member is continuously connected to said planet carrier of said third planetary gear set.
The first planetary gear set and the third planetary gear set are single pinion planetary gear mechanisms,
12. A multi-speed transmission according to any one of claims 2 to 11, wherein the second planetary gear set is a single pinion or double pinion planetary gear mechanism.