阅读说明：本技术 一种九挡行星自动变速器 (Nine-gear planetary automatic transmission ) 是由 王明成 朱礼安 徐宜 陈嘉杨 李明勇 乔丽 靳建波 柳泓蛰 魏然 程鑫 张海全 于 2020-04-10 设计创作，主要内容包括：本发明公开了一种车辆驱动系统的九挡行星自动变速器,属于车辆传动技术领域。该变速器包括行星排,安装在两端分别与输入轴、输出轴连接的输入构件和输出构件,连接构件、制动器和离合器,所述行星排有四个、连接构件有五个、制动器有四个、离合器有二个。与现有技术相比,本发明的自动变速器采用四个行星排、四个制动器和二个离合器的方案,实现九个前进挡,传动比间比均匀,可显著提高车辆的燃油经济性；便于实现紧凑结构,减少了自动变速器的体积和重量。(The invention discloses a nine-gear planetary automatic transmission of a vehicle driving system, and belongs to the technical field of vehicle transmission. The transmission comprises four planet rows, an input member, an output member, connecting members, brakes and clutches, wherein the input member and the output member are arranged at two ends of each planet row and are respectively connected with an input shaft and an output shaft, and the four planet rows, the five connecting members, the four brakes and the two clutches are arranged. Compared with the prior art, the automatic transmission adopts the scheme of four planet rows, four brakes and two clutches, realizes nine forward gears, has uniform transmission ratio, and can obviously improve the fuel economy of a vehicle; the compact structure is convenient to realize, and the volume and the weight of the automatic transmission are reduced.)

1. The utility model provides a nine keep off planet automatic gearbox, includes the planet row, installs input member (1), output member (2) with input shaft, output shaft respectively at both ends, connecting element, stopper and clutch, its characterized in that: the number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS 4; the number of the connecting components is five, and the connecting components are respectively a connecting component (3), a connecting component (4), a connecting component (5), a connecting component (6) and a connecting component (7); the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; the two clutches are a clutch C1 and a clutch C2 respectively;

the sun gear S1, carrier CA1 and ring gear R1 of the planetary row PGS1 are connected to the input member (1), connecting member (3) and connecting member (4), respectively;

the sun gear S2, the carrier CA2 and the ring gear R2 of the planetary row PGS2 are connected with the connecting member (3), the connecting member (4) and the connecting member (5), respectively;

the sun gear S3, the carrier CA3 and the ring gear R3 of the planetary row PGS3 are connected with the connecting member (4), the connecting member (6) and the output member (2), respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the planetary row PGS4 are connected to the connecting member (7), output member (2) and connecting member (6), respectively;

the input member (1) connects the sun gear S1 of the planetary row PGS1, the inner hub of clutch C1 and the outer hub of clutch C2;

the output member (2) connects the ring gear R3 of the row PGS3 with the carrier CA4 of the row PGS 4;

the connecting member (3) connects the carrier CA1 of the planetary row PGS1, the sun gear S2 of the planetary row PGS2 and the inner hub of the brake B1;

the connecting member (4) connects ring gear R1 of row PGS1, carrier CA2 of row PGS2, sun gear S3 of row PGS3 and the inner hub of brake B2;

the connecting member (5) connects the ring gear R2 of the planet row PGS2 and the inner hub of the brake B3;

the connecting member (6) connects carrier CA3 of row PGS3, ring gear R4 of row PGS4, the inner hub of brake B4 and the inner hub of clutch C2;

the connecting member (7) connects the sun gear S4 of the planetary row PGS4 and the outer hub of the clutch C1;

the brake B1 is used for braking the connecting component (3);

the brake B2 is used for braking the connecting component (4);

the brake B3 is used for braking the connecting component (5);

the brake B4 is used for braking the connecting component (6);

the clutch C1 connects the connecting member (7) and the input member (1);

the clutch C2 connects the input member (1) and the connecting member (6).

2. The nine-speed planetary automatic transmission according to claim 1, characterized in that: the planet row PGS1 is a double-star planet row, and the planet row PGS2, the planet row PGS3 and the planet row PGS4 are single-star planet rows.

Technical Field

The invention belongs to the technical field of vehicle transmission, and particularly relates to a nine-gear planetary automatic transmission for a road vehicle.

Background

As a planetary automatic transmission for road vehicles, power of an internal combustion engine or the like is transmitted to an input shaft of the planetary automatic transmission through a torque converter, and after shifting according to a current gear, the power is output from an output shaft and transmitted to left and right driving wheels through a differential, and most of the planetary automatic transmission is composed of a plurality of planetary rows, a brake and a clutch. At present, the ratio among the transmission ratios of the seven-gear planetary automatic transmission for the road vehicles is uneven, and the fuel economy of the vehicles is poor, so that a nine-gear planetary automatic transmission with better performance than the current planetary automatic transmission needs to be found.

Disclosure of Invention

The invention aims to provide a nine-gear planetary automatic transmission for a road vehicle, which realizes nine forward gears and one reverse gear by utilizing four planetary rows, four brakes and two clutches, has large transmission ratio range and uniform transmission ratio and can meet the requirement of fuel economy of the vehicle.

The invention provides a nine-gear planetary automatic transmission, which comprises a planetary row, an input member 1 and an output member 2, a connecting member, a brake and a clutch, wherein the input member 1 and the output member 2 are arranged at two ends of the planetary row and are respectively connected with an input shaft and an output shaft; the four planet rows are respectively a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS 4; five connecting members are respectively a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6 and a connecting member 7; the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; there are two clutches, clutch C1 and clutch C2.

The sun gear S1, carrier CA1 and ring gear R1 of the row PGS1 are connected with the input member 1, connecting member 3 and connecting member 4, respectively;

the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 3, connecting member 4 and connecting member 5, respectively;

the sun gear S3, carrier CA3 and ring gear R3 of the row PGS3 are connected to the connecting member 4, connecting member 6 and output member 2, respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the row PGS4 are connected to the connecting member 7, output member 2 and connecting member 6, respectively;

the input member 1 connects the sun gear S1 of the planetary row PGS1, the inner hub of clutch C1 and the outer hub of clutch C2;

the output member 2 connects the ring gear R3 of row PGS3 with the carrier CA4 of row PGS 4;

the connecting member 3 connects the carrier CA1 of the planetary row PGS1, the sun gear S2 of the planetary row PGS2 and the inner hub of the brake B1;

the connecting member 4 connects ring gear R1 of row PGS1, carrier CA2 of row PGS2, sun gear S3 of row PGS3 and the inner hub of brake B2;

the connecting member 5 connects the ring gear R2 of the planet row PGS2 and the inner hub of the brake B3;

the connecting member 6 connects carrier CA3 of row PGS3, ring gear R4 of row PGS4, the inner hub of brake B4 and the inner hub of clutch C2;

the connecting member 7 connects the sun gear S4 of the planet row PGS4 with the outer hub of the clutch C1;

the brake B1 is used for braking the connecting member 3;

the brake B2 is used for braking the connecting member 4;

the brake B3 is used for braking the connecting member 5;

the brake B4 is used for braking the connecting member 6;

the clutch C1 connects the connecting member 7 with the input member 1;

the clutch C2 connects the input member 1 with the connecting member 6.

Has the advantages that:

the nine-gear planetary automatic transmission adopts the scheme of adopting four planetary rows, four brakes and two clutches to realize nine forward gears, has uniform transmission ratio and can obviously improve the fuel economy of a vehicle. K values of the four planet rows are within the range of 1.64-3.10, so that a compact structure is convenient to realize, and the volume and the weight of the planetary automatic transmission are reduced.

Drawings

Fig. 1 is a schematic diagram showing the connection relationship of the components of a nine-speed planetary automatic transmission, in the diagram, PGS 1-PGS 4 are four planetary rows, S1-S4 are four sun gears, CA 1-CA 4 are four planetary carriers, R1-R4 are four ring gears, B1-B4 are four brakes, C1-C2 are two clutches, 1 is an input component, 2 is an output component, and 3-7 are five connecting components.

Detailed Description

The invention is described in detail below by way of example with reference to the accompanying drawings.

The nine-gear planetary automatic transmission is suitable for a vehicle transmission system. Wherein the planetary rows are arranged in a sequence, the planetary rows are connected by a connecting member, and the input shaft is connected to an input member 1, typically a turbine shaft of a torque converter, for transmitting power of an engine to the planetary automatic transmission through the torque converter. The output shaft is connected with the output member 2, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential. The planetary automatic transmission is completely symmetrical with respect to the rotation center, and the lower half of the rotation center is omitted in fig. 1, and will not be described below.

The nine-speed planetary automatic transmission shown in fig. 1 includes a planetary row, an input member 1 and an output member 2 mounted at both ends thereof to be connected to an input shaft and an output shaft, respectively, a connecting member, a brake, and a clutch. The number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS 4; five connecting members are respectively a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6 and a connecting member 7; the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; there are two clutches, clutch C1 and clutch C2.

Each planet row comprises a sun gear, a planet carrier and a ring gear.

The sun gear S1, carrier CA1 and ring gear R1 of the row PGS1 are connected with the input member 1, connecting member 3 and connecting member 4, respectively;

the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 3, connecting member 4 and connecting member 5, respectively;

the sun gear S3, carrier CA3 and ring gear R3 of the row PGS3 are connected to the connecting member 4, connecting member 6 and output member 2, respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the row PGS4 are connected to the connecting member 7, output member 2 and connecting member 6, respectively;

the input member 1 connects the sun gear S1 of the planetary row PGS1, the inner hub of clutch C1 and the outer hub of clutch C2;

the output member 2 connects the ring gear R3 of row PGS3 with the carrier CA4 of row PGS 4;

the connecting member 3 connects the carrier CA1 of the planetary row PGS1, the sun gear S2 of the planetary row PGS2 and the inner hub of the brake B1;

the connecting member 4 connects ring gear R1 of row PGS1, carrier CA2 of row PGS2, sun gear S3 of row PGS3 and the inner hub of brake B2;

the connecting member 5 connects the ring gear R2 of the planet row PGS2 and the inner hub of the brake B3;

the connecting member 6 connects carrier CA3 of row PGS3, ring gear R4 of row PGS4, the inner hub of brake B4 and the inner hub of clutch C2;

the connecting member 7 connects the sun gear S4 of the planet row PGS4 with the outer hub of the clutch C1;

the brake B1 is used for braking the connecting member 3;

the brake B2 is used for braking the connecting member 4;

the brake B3 is used for braking the connecting member 5;

the brake B4 is used for braking the connecting member 6;

the clutch C1 connects the connecting member 7 with the input member 1;

the clutch C2 connects the input member 1 with the connecting member 6.

The planet row PGS1 is a double-star planet row, and the planet row PGS2, the planet row PGS3 and the planet row PGS4 are single-star planet rows.

The brakes B1-B4, the clutches C1 and C2 are multi-plate friction operating pieces, and the pistons are driven by hydraulic oil to pressurize. The operating scheme for each gear is shown in table 1.

TABLE 1 schematic diagram of each gear implementation mode and corresponding transmission ratio and intermediate ratio of nine-gear planetary automatic transmission

Good in the table means the joint of the operating parts

Referring now to fig. 1 and table 1, an example of the present invention will be described in detail, wherein the transmission ratio is the ratio of the input shaft speed to the output shaft speed, and the k value of the planetary row is the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear of the planetary row.

When the clutch C1 and brake B3 are engaged, the coupling member 7 and the input member 1 rotate as a unit and the coupling member 5 brakes to achieve first gear "1 st".

When clutch C1 and brake B4 are engaged, connecting member 7 and input member 1 rotate as a unit and connecting member 6 brakes, achieving two gears "2 nd".

When brake B3 and brake B4 are engaged, connecting member 5 and connecting member 6 brake simultaneously, achieving third gear "3 rd".

When clutch C1 and brake B2 are engaged, connecting member 7 rotates integrally with the input member 1 and connecting member 4 brakes to achieve the fourth gear "4 th".

When clutch C1 and brake B1 are engaged, connecting member 7 rotates integrally with the input member 1 and connecting member 3 brakes to achieve the fifth gear "5 th".

When clutch C1 and clutch C2 are engaged, coupling member 7 and input member 1 rotate as a unit, and input member 1 and coupling member 6 rotate as a unit, thereby achieving six "6 th".

When clutch C2 and brake B1 are engaged, connecting member 1 and connecting member 6 rotate as a unit and connecting member 3 brakes to achieve seven "7 th".

When clutch C2 and brake B2 are engaged, the input member 1 and connecting member 6 rotate as a unit and connecting member 4 brakes to achieve eight gear "8 th".

When clutch C2 and brake B3 are engaged, the input member 1 and coupling member 6 rotate as a unit and coupling member 5 brakes to achieve the nine gear "9 th".

When brake B1 and brake B4 are engaged, connecting member 3 and connecting member 6 brake simultaneously, achieving reverse gear "Rev".

The gear ratios of the gears are determined by the k values of the four planetary rows. For example, when k1 ≈ 2.712, k2 ≈ 1.640, k3 ≈ 1.738, and k4 ≈ 3.100, the gear ratios of the respective stages shown in table 1 can be obtained, and the gear ratios of the respective stages are all smaller than 1.505, so that relatively uniform gear ratios are obtained. The k values of the four planet rows are within the range of 1.64-3.10, so that the radial size of the planet rows is small, the compact structure is convenient to realize, and the volume and the weight of the planetary automatic transmission are reduced.

In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.