阅读说明：本技术 一种七挡行星自动变速器 (Seven-gear planetary automatic transmission ) 是由 王明成 王佳婧 毛润 刘振杰 李慧渊 李晋 宋振川 王叶 钟超杰 高子茵 邹武俊 于 2020-03-30 设计创作，主要内容包括：本发明提供了一种车辆驱动系统的七挡行星自动变速器,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、连接构件有六个、制动器有四个、离合器有三个。与现有技术相比,本发明的自动变速器采用四个行星排、四个制动器和三个离合器的方案,实现七个前进挡和六个倒挡,倒挡的挡位多、传动比范围宽。本发明便于实现简单换挡控制和紧凑结构,减少了控制难度和自动变速器的体积和重量。(The invention provides a seven-gear planetary automatic transmission of a vehicle driving system, and belongs to the technical field of vehicle transmission. The transmission comprises a planet row, 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 the planet row and are respectively connected with an input shaft and an output shaft, and the planet row comprises four connecting members, six connecting members, four brakes and three clutches. Compared with the prior art, the automatic transmission adopts the scheme of four planet rows, four brakes and three clutches, seven forward gears and six reverse gears are realized, the reverse gears have more gears, and the transmission ratio range is wide. The invention is convenient for realizing simple gear shift control and compact structure, and reduces the control difficulty and the volume and weight of the automatic transmission.)

1. The utility model provides a seven 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 six, namely a connecting component (3), a connecting component (4), a connecting component (5), a connecting component (6), a connecting component (7) and a connecting component (8); the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; the number of the clutches is three, namely a clutch C1, a clutch C2 and a clutch C3;

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

the sun gear S2, the carrier CA2 and the ring gear R2 of the planetary row PGS2 are connected with the connecting member (4), the connecting member (5) and the connecting member (8), respectively;

the sun gear S3, the carrier CA3 and the ring gear R3 of the planetary row PGS3 are connected with the connecting member (7), the connecting member (8) and the connecting member (5), respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the planetary row PGS4 are connected to the connecting member (8), connecting member (6) and output member (2), 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 R4 of the planet row PGS4 with the outer hub of the clutch C3;

the connecting member (3) connects the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;

the connecting member (4) 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 B2;

the connecting member (5) connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B3 and the inner hub of clutch C2;

the connecting member (6) connects the carrier CA4 of the planetary row PGS4 and the inner hub of the brake B4;

the connecting member (7) connects the sun gear S3 of the planetary row PGS3 and the outer hub of the clutch C1;

the connecting member (8) connects the ring gear R2 of the row PGS2, the carrier CA3 of the row PGS3, the sun gear S4 of the row PGS4 and the inner hub of the clutch C3;

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 (5);

the clutch C3 connects the output member (2) and the connecting member (8).

2. The seven speed planetary automatic transmission according to claim 1, wherein: the planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are all single planet rows.

Technical Field

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

Background

As a planetary automatic transmission for a vehicle, 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 drive wheels through a differential, and the planetary automatic transmission is mostly composed of a plurality of planetary rows, brakes and clutches. At present, a mainstream seven-gear planetary automatic transmission for a vehicle is obtained by adding a planetary row on the basis of an original six-gear planetary automatic transmission, and has fewer reverse gears and a narrow transmission ratio range; for this reason, a seven-speed planetary automatic transmission having more reverse gears than the current planetary automatic transmission is sought.

Disclosure of Invention

The invention aims to provide a seven-gear planetary automatic transmission for a vehicle, which realizes seven forward gears and six reverse gears by utilizing four planetary rows, four brakes and three clutches, has more reverse gears and wide transmission ratio range, and can meet the use requirements of the vehicle.

The invention provides a seven-gear planetary automatic transmission, which comprises a planetary row, an input component 1, an output component 2, a connecting component, a brake and a clutch, wherein the input component 1 and the output component 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; six connecting members are respectively a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6, a connecting member 7 and a connecting member 8; the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; there are three clutches, clutch C1, clutch C2, and clutch C3.

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

the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 4, connecting member 5 and connecting member 8, respectively;

the sun gear S3, carrier CA3 and ring gear R3 of the planetary row PGS3 are connected with the connecting member 7, connecting member 8 and connecting member 5, respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the row PGS4 are connected to the connecting member 8, connecting member 6 and output member 2, 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 R4 of the planet row PGS4 with the outer hub of the clutch C3;

the connecting member 3 connects the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;

the connecting member 4 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 B2;

the connecting member 5 connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B3 and the inner hub of clutch C2;

the connecting member 6 connects the carrier CA4 of the planetary row PGS4 and the inner hub of the brake B4;

the connecting member 7 connects the sun gear S3 of the planet row PGS3 with the outer hub of the clutch C1;

the connecting member 8 connects the ring gear R2 of row PGS2, the carrier CA3 of row PGS3, the sun gear S4 of row PGS4 and the inner hub of clutch C3;

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 5;

the clutch C3 connects the output member 2 with the connecting member 8.

Has the advantages that:

the seven-gear planetary automatic transmission adopts the scheme of four planetary rows, four brakes and three clutches to realize seven forward gears and six reverse gears, and the reverse gear transmission ratio range can reach 5.531. K values of the four planet rows are within a range of 1.5-2.6, so that a compact structure is convenient to realize, and the volume and the weight of the automatic transmission are reduced.

Drawings

FIG. 1 is a schematic diagram of the connection of the components of a seven-speed planetary automatic transmission.

In the figure, 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 gear rings, B1-B4 are four brakes, C1-C3 are three clutches, 1 is an input member, 2 is an output member, and 3-8 are connecting members.

Detailed Description

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

The seven-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 seven-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 coupling 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; six connecting members are respectively a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6, a connecting member 7 and a connecting member 8; the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; there are three clutches, clutch C1, clutch C2, and clutch C3.

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

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

the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 4, connecting member 5 and connecting member 8, respectively;

the sun gear S3, carrier CA3 and ring gear R3 of the planetary row PGS3 are connected with the connecting member 7, connecting member 8 and connecting member 5, respectively;

the sun gear S4, carrier CA4 and ring gear R4 of the row PGS4 are connected to the connecting member 8, connecting member 6 and output member 2, 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 R4 of the planet row PGS4 with the outer hub of the clutch C3;

the connecting member 3 connects the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;

the connecting member 4 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 B2;

the connecting member 5 connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B3 and the inner hub of clutch C2;

the connecting member 6 connects the carrier CA4 of the planetary row PGS4 and the inner hub of the brake B4;

the connecting member 7 connects the sun gear S3 of the planet row PGS3 with the outer hub of the clutch C1;

the connecting member 8 connects the ring gear R2 of row PGS2, the carrier CA3 of row PGS3, the sun gear S4 of row PGS4 and the inner hub of clutch C3;

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 5;

the clutch C3 connects the output member 2 with the connecting member 8.

The planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are all single planet rows.

The brakes B1-B4 and the clutches C1-C3 are multi-plate friction control pieces, and hydraulic oil is used for driving pistons to pressurize; it may also be a sliding sleeve or coupling or dog clutch or other controllable selective disengagement and engagement means. 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 seven-gear planetary automatic transmission

In the table ". smallcircle" indicates the handling member engagement

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 brake B1, the brake B3, and the brake B4 are combined, the linking member 3, the linking member 5, and the linking member 6 are braked simultaneously, achieving the first gear "1 st".

When clutch C1, clutch C3, and brake B3 are engaged, coupling member 7 and input member 1 rotate integrally, output member 2 and coupling member 8 rotate integrally, and coupling member 5 brakes, achieving two gears "2 nd".

When clutch C1, clutch C3, and brake B2 are engaged, connecting member 7 and input member 1 rotate integrally, output member 2 and connecting member 8 rotate integrally, and connecting member 4 brakes, achieving third gear "3 rd".

When clutch C1, clutch C3, and brake B1 are engaged, connecting member 7 and input member 1 rotate integrally, output member 2 and connecting member 8 rotate integrally, and connecting member 3 brakes, achieving fourth gear "4 th".

When the clutch C1, the clutch C2, and the clutch C3 are engaged, the coupling member 7 and the input member 1 rotate integrally, the input member 1 and the coupling member 5 rotate integrally, and the output member 2 and the coupling member 8 rotate integrally, realizing five "5 th".

When clutch C2, clutch C3, and brake B1 are engaged, input member 1 and coupling member 5 rotate integrally, output member 2 and coupling member 8 rotate integrally, and coupling member 3 brakes to achieve six "6 th".

When clutch C2, clutch C3, and brake B2 are engaged, input member 1 and coupling member 5 rotate integrally, output member 2 and coupling member 8 rotate integrally, and coupling member 4 brakes to achieve seven "7 th".

When clutch C1, brake B3 and brake B4 are engaged, connecting member 7 and input member 1 rotate as a unit, and connecting member 5 and connecting member 6 brake simultaneously, achieving reverse gear "Rev 1".

When clutch C1, brake B2 and brake B4 are engaged, connecting member 7 and input member 1 rotate as a unit, and connecting member 4 and connecting member 6 brake simultaneously, achieving reverse gear "Rev 2".

When clutch C1, brake B1 and brake B4 are engaged, connecting member 7 and input member 1 rotate as a unit, and connecting member 3 and connecting member 6 brake simultaneously, achieving reverse three gear "Rev 3".

When clutch C1, clutch C2, and brake B4 are engaged, connecting member 7 and input member 1 rotate integrally, input member 1 and connecting member 5 rotate integrally, and connecting member 6 brakes, achieving reverse four gear "Rev 4".

When clutch C2, brake B1, and brake B4 are engaged, input member 1 and connecting member 5 rotate as a unit, and connecting member 3 and connecting member 6 brake simultaneously, achieving reverse five gear "Rev 5".

When clutch C2, brake B2 and brake B4 are engaged, input member 1 and connecting member 5 rotate as a unit, and connecting member 4 and connecting member 6 brake simultaneously, achieving reverse six gear "Rev 6".

The gear ratios of the gears are determined by the k values of the four planetary rows. For example, when k1 ≈ 1.712, k2 ≈ 1.738, k3 ≈ 2.510, and k4 ≈ 1.519, the gear ratios of the respective gears shown in table 1 can be obtained, and the total gear ratio range (5.332/0.964) of six reverse gears reaches 5.531, so that a wide reverse gear ratio range is obtained. The k values of the PGS 1-PGS 4 of the planet rows are within the range of 1.5-2.6, so that the radial sizes of the four planet rows PGS 1-PGS 4 are small, and the compact structure is convenient to realize. Meanwhile, as can be seen from the operating schemes of the gears in table 1, except for 1 gear and 2 gears, only one operating member needs to be switched for each gear shifting, so that simple gear shifting control is facilitated, and the control difficulty is 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.