CN118088634A - Eleven-speed planetary automatic transmission - Google Patents

Abstract

The invention belongs to the technical field of vehicle transmission, and relates to an eleven-gear planetary automatic transmission, which comprises planetary rows, input members, output members, connecting members, brakes and clutches, wherein the input members and the output members are arranged at two ends of the planetary rows and are respectively connected with an input shaft and an output shaft, the number of the planetary rows is 4, the number of the connecting members is 5, and the number of the brakes is 4 and 2. The invention designs a novel transmission structure with eleven forward gears and one reverse gear through the coupling and arrangement of the planetary rows, the brake and the clutch, and the novel transmission structure has the characteristics of wider transmission ratio range, more compact space structure and lighter volume and weight.

Description

Eleven-speed planetary automatic transmission

Technical Field

The invention belongs to the technical field of vehicle transmission and relates to an eleven-speed planetary automatic transmission.

Background technique

The traction and speed range required by the vehicle during driving are relatively large, but the torque and speed range of the engine are relatively small. The use of the transmission can make the engine work within a reasonable and effective range. The engine can usually only rotate in one direction and cannot be started under load. Related problems can be solved by the use of the transmission. In addition, the situation where the vehicle needs to stop frequently for a long time also requires a transmission. The transmission can improve the performance of the vehicle in terms of economy and power. During the driving process, the vehicle uses the transmission to reasonably convert its gears, thereby changing the speed ratio between the vehicle's wheels and the engine, ensuring that the engine's working performance is always maintained in the best state. The power, comfort and economy of the entire vehicle are all affected by the performance of the transmission.

As a planetary automatic transmission for road vehicles, the power of the internal combustion engine is transmitted to the input shaft of the planetary automatic transmission through the torque converter. After the current gear is changed, the power is output from the output shaft and transmitted to the left and right drive wheels through the differential. Most of the transmissions are composed of multiple planetary gears, brakes and clutches. The traditional three-speed, four-speed, five-speed and even six-speed and seven-speed transmissions can no longer meet the growing needs of automotive automatic transmissions. Eight-speed and nine-speed transmissions have begun to enter the field of vision and are slowly developing in the mainstream direction. At present, the planetary gear transmission mechanism with three planetary gears can no longer meet the inherent needs of the increase in the number of gears, so the development of four planetary gear rows or even more planetary gear rows is imperative. For this reason, it is necessary to find a planetary automatic transmission with better performance than the current planetary automatic transmission.

Summary of the invention

In view of this, the object of the present invention is to provide an eleven-speed planetary automatic transmission, which utilizes four planetary rows, two clutches and four brakes to achieve eleven forward gears and one reverse gear, has a large transmission ratio range, and has uniform transmission ratios, which can meet the use requirements of heavy vehicles.

In order to achieve the above object, the present invention provides the following technical solutions:

An eleven-speed planetary automatic transmission, comprising a planetary row, an input member and an output member installed at both ends and connected to an input shaft and an output shaft respectively, a connecting member, a brake and a clutch, wherein the planetary row is four, namely a first planetary row PGS1, a second planetary row PGS2, a third planetary row PGS3 and a fourth planetary row PGS4, and the planetary row comprises a sun gear, a planet carrier and a ring gear, the connecting members are five, namely a first connecting member, a second connecting member, a third connecting member, a fourth connecting member and a fifth connecting member, the brakes are four, namely a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4, and the clutches are two, namely a first clutch C1 and a second clutch C2;

The sun gear S1, the planet carrier CA1 and the ring gear R1 of the first planetary gear set PGS1 are connected to the first connecting member, the second connecting member and the fifth connecting member respectively;

The sun gear S2, the planet carrier CA2 and the ring gear R2 of the second planetary gear set PGS2 are connected to the input member, the third connecting member and the second connecting member respectively;

The sun gear S3, the planet carrier CA3 and the ring gear R3 of the third planetary gear PGS3 are connected to the input member, the fourth connecting member and the fifth connecting member respectively;

The sun gear S4, the planet carrier CA4 and the ring gear R4 of the fourth planetary gear PGS4 are connected to the second connecting member, the fourth connecting member and the output member respectively;

The first connecting member is also connected to the inner hub of the first brake B1;

The second connecting member is also connected to the inner hub of the second brake B2;

The third connecting member also connects the inner hub of the first clutch C1 and the inner hub of the third brake B3;

The fourth connecting member also connects the outer hub of the second clutch C2 and the inner hub of the fourth brake B4;

The fifth connecting member is also connected to the inner hub of the first clutch C1;

The input member is also connected to the inner hub of the second clutch C2.

Furthermore, the first planet row PGS1, the second planet row PGS2, the third planet row PGS3 and the fourth planet row PGS4 are all single planet rows.

Furthermore, the input shaft is a turbine shaft of a torque converter.

Furthermore, the brake and clutch are multi-plate friction operating parts.

The beneficial effects of the present invention are:

The present invention provides an eleven-speed planetary automatic transmission, which adopts four planetary gears, four brakes and two clutches to realize eleven forward gears and one reverse gear. The transmission ratio range of the forward gear can reach 18.286, thereby obtaining a wider transmission ratio range and realizing high-efficiency transmission, thereby improving the vehicle's dynamic performance and economic performance.

Other advantages, objectives and features of the present invention will be described in the following description to some extent, and to some extent, will be obvious to those skilled in the art based on the following examination and study, or can be taught from the practice of the present invention. The objectives and other advantages of the present invention can be realized and obtained through the following description.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to make the purpose, technical solutions and advantages of the present invention more clear, the present invention will be described in detail below in conjunction with the accompanying drawings, wherein:

FIG1 is a schematic structural diagram of an eleven-speed planetary automatic transmission according to the present invention.

Reference numerals: 1 - input member, 2 - output member, 3 - first connecting member, 4 - second connecting member, 5 - third connecting member, 6 - fourth connecting member, 7 - fifth connecting member;

PGS1~PGS4 are four planetary rows, S1~S4 are four sun gears, CA1~CA4 are four planetary carriers, R1~R4 are four ring gears, B1~B4 are four brakes, and C1~C2 are two clutches.

Detailed ways

The following describes the embodiments of the present invention by specific examples, and those skilled in the art can easily understand other advantages and effects of the present invention from the contents disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed in various ways based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the illustrations provided in the following embodiments only illustrate the basic concept of the present invention in a schematic manner, and the following embodiments and the features in the embodiments can be combined with each other without conflict.

Among them, the drawings are only used for illustrative explanations, and they only represent schematic diagrams rather than actual pictures, and should not be understood as limitations on the present invention. In order to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of actual products. For those skilled in the art, it is understandable that some well-known structures and their descriptions in the drawings may be omitted.

The same or similar numbers in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if the terms "upper", "lower", "left", "right", "front", "back" and the like indicate directions or positional relationships, they are based on the directions or positional relationships shown in the drawings, which are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and cannot be understood as limiting the present invention. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

Please refer to FIG1 . The eleven-speed planetary automatic transmission provided by the present invention is suitable for a vehicle transmission system, wherein each single planetary gear is arranged in sequence, and each planetary gear is connected by a connecting member. The input shaft is connected to the input member 1, which is generally a turbine shaft of a hydraulic torque converter, and is used to transmit the power of the engine to the planetary automatic transmission through the hydraulic torque converter. The output shaft is connected to the output member 2, and transmits the power to the front and rear axles or the left and right drive wheels through a transfer case or a differential. The planetary automatic transmission is completely symmetrical with respect to the rotation center. The lower half of the rotation center is omitted in FIG1 , and will not be described in the following description.

The eleven-speed planetary automatic transmission includes a planetary gear, an input member 1 and an output member 2, a connecting member, a brake and a clutch, which are installed at both ends and are connected to the input shaft and the output shaft respectively. There are four planetary gears, namely the first planetary gear PGS1, the second planetary gear PGS2, the third planetary gear PGS3 and the fourth planetary gear PGS4; there are five connecting members, namely the first connecting member 3, the second connecting member 4, the third connecting member 5, the fourth connecting member 6 and the fifth connecting member 7; there are four brakes, namely the first brake B1, the second brake B2, the third brake B3 and the fourth brake B4; there are two clutches, namely the first clutch C1 and the second clutch C2;

Each of the planetary gears comprises a sun gear, a planet carrier and a ring gear. The sun gear S1, the planet carrier CA1 and the ring gear R1 of the first planetary gear PGS1 are connected to the first connecting member 3, the second connecting member 4 and the fifth connecting member 7 respectively;

The sun gear S2, the planet carrier CA2 and the ring gear R2 of the second planetary gear set PGS2 are connected to the input member 1, the third connecting member 5 and the second connecting member 4 respectively;

The sun gear S3, the planet carrier CA3 and the ring gear R3 of the third planetary gear PGS3 are connected to the input member 1, the fourth connecting member 6 and the fifth connecting member 7 respectively;

The sun gear S4, the planet carrier CA4 and the ring gear R4 of the fourth planetary gear PGS4 are respectively connected to the second connecting member 4, the fourth connecting member 6 and the output member 2;

The input member 1 is connected to the sun gear S2 of the second planetary gear PGS2, the sun gear S3 of the third planetary gear PGS3 and the inner hub of the second clutch C2;

The output member 2 is connected to the ring gear R4 of the fourth planetary gear PGS4;

The first connecting member 3 connects the sun gear S1 of the first planetary gear PGS1 and the inner hub of the first brake B1;

The second connecting member 4 connects the planet carrier CA1 of the first planetary gear set PGS1, the ring gear R2 of the second planetary gear set PGS2, the sun gear S4 of the fourth planetary gear set PGS4 and the inner hub of the second brake B2;

The third connecting member 5 connects the planet carrier CA2 of the second planetary gear PGS2, the inner hub of the first clutch C1 and the inner hub of the third brake B3;

The fourth connecting member 6 connects the planet carrier CA4 of the fourth planetary gear PGS4, the outer hub of the second clutch C2 and the inner hub of the fourth brake B4;

The fifth connecting member 7 connects the ring gear R1 of the first planetary gear set PGS1, the ring gear R3 of the third planetary gear set PGS3 and the outer hub of the first clutch C1;

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

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

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

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

The first clutch C1 connects the third connecting member 5 and the fifth connecting member 7;

The second clutch C2 connects the input member 1 and the fourth connecting member 6 .

The first planetary gear PGS1, the second planetary gear PGS2, the third planetary gear PGS3 and the fourth planetary gear PGS4 are all single planetary gears. The first brake B1, the second brake B1, the third brake B1, the fourth brake B4, the first clutch C1 and C2 are generally multi-plate friction operating parts, and the hydraulic oil drives the piston for pressurization. The operating scheme of each gear is shown in Table 1.

Table 1 Schematic diagram of the implementation methods and corresponding transmission ratios of the eight-speed planetary automatic transmission

The following is a detailed description of an example of the present invention in conjunction with FIG. 1 and Table 1. It should be noted that the transmission ratio described herein refers to the ratio of the input shaft speed to the output shaft speed, the planetary gear k value refers to the ratio of the number of teeth of the planetary gear ring to the number of teeth of the sun gear, 1 represents the input member, 2 represents the output member, 8 and 9 are virtual members, representing the first clutch C1 and the second clutch C2 respectively, and the active and passive ends of 8 are 5 (third connecting member 5) and 7 (fifth connecting member 7), and the active and passive ends of 9 are 1 (input member 1) and 6 (fourth connecting member 6);

When the first brake B1 and the fourth brake B4 are combined, the first connecting member 3 and the fourth connecting member 6 are braked at the same time to achieve the first gear “1st”;

When the third brake B3 and the fourth brake B4 are combined, the third connecting member 5 and the fourth connecting member 6 are braked at the same time to achieve the second gear “2nd”;

When the first brake B1 and the second brake B2 are combined, the first connecting member 3 and the second connecting member 4 are braked at the same time, realizing the third gear "3rd";

When the first clutch C1 and the fourth brake B4 are engaged, the third connecting member 5 and the fifth connecting member 7 rotate integrally, and the fourth connecting member 6 is braked, thereby realizing the fourth gear “4th”;

When the first clutch C1 and the third brake B3 are engaged, the third connecting member 5 and the fifth connecting member 7 rotate integrally, and the third connecting member 5 is braked to achieve the fifth gear “5th”;

When the first clutch C1 and the second brake B2 are engaged, the third connecting member 5 and the fifth connecting member 7 rotate integrally, and the second connecting member 4 is braked, thus realizing the sixth gear “6th”;

When the first clutch C1 and the first brake B1 are engaged, the third connecting member 5 and the fifth connecting member 7 rotate integrally, and the first connecting member 3 is braked, thereby realizing the seventh gear “7th”;

When the first clutch C1 and the second clutch C2 are engaged, the third connecting member 5 and the fifth connecting member 7 rotate integrally, and the input member 1 and the fourth connecting member 6 rotate integrally, realizing the eighth gear "8th";

When the second clutch C2 and the first brake B1 are engaged, the input member 1 and the fourth connecting member 6 rotate integrally, and the first connecting member 3 is braked, thus achieving the ninth gear “9th”;

When the second clutch C2 and the second brake B2 are engaged, the input member 1 and the fourth connecting member 6 rotate integrally, and the second connecting member 4 is braked, realizing the tenth gear "10th";

When the second clutch C2 and the third brake B3 are engaged, the input member 1 and the fourth connecting member 6 rotate integrally, and the third connecting member 5 is braked, realizing the tenth gear "11en";

When the first brake B1 and the third brake B3 are combined, the first connecting member 3 and the third connecting member 5 are braked at the same time, realizing the reverse gear "R";

The transmission ratio of each gear is determined by the k value of the four planetary gears. For example, when k1=3.113, k2=2.920, k3=4.384, and k4=1.812, the transmission ratios of each gear shown in Table 1 can be obtained. The total transmission ratio range of the forward gear (10.496/0.574) reaches 18.286, and a wider transmission ratio range is obtained. At the same time, the k values of the three planetary gears are in the range of 1.8 to 3.2, which is convenient for realizing a compact structure and reducing the volume and weight of the automatic transmission. When the input speed is 1 and the torque is 1, the relative speeds of the components and the planetary gears at different gears are shown in Table 2, the relative torques of the components and the planetary gears are shown in Table 3, and the transmission efficiency of different gears is shown in Table 4.

Table 2. Relative speed of each component and planetary gear in different gears

Table 3. Relative torque of each component and planetary gear in different gears

Table 4. Transmission efficiency of different gears

Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solution of the present invention can be modified or replaced by equivalents without departing from the purpose and scope of the technical solution, which should be included in the scope of the claims of the present invention.

Claims (4)

1. An eleven-speed planetary automatic transmission, comprising a planetary gear, an input member (1) and an output member (2) mounted at both ends and connected to an input shaft and an output shaft respectively, a connecting member, a brake and a clutch, wherein: the number of the planetary gears is four, namely a first planetary gear PGS1, a second planetary gear PGS2, a third planetary gear PGS3 and a fourth planetary gear PGS4, and the planetary gears include a sun gear, a planet carrier and a ring gear, the number of the connecting members is five, namely a first connecting member (3), a second connecting member (4), a third connecting member (5), a fourth connecting member (6) and a fifth connecting member (7), the number of the brakes is four, namely a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4, and the number of the clutches is two, namely a first clutch C1 and a second clutch C2; The sun gear S1, the planet carrier CA1 and the ring gear R1 of the first planetary gear set PGS1 are respectively connected to the first connecting member (3), the second connecting member (4) and the fifth connecting member (7); The sun gear S2, the planet carrier CA2 and the ring gear R2 of the second planetary gear set PGS2 are respectively connected to the input member (1), the third connecting member (5) and the second connecting member (4); The sun gear S3, the planet carrier CA3 and the ring gear R3 of the third planetary gear PGS3 are respectively connected to the input member (1), the fourth connecting member (6) and the fifth connecting member (7); The sun gear S4, the planet carrier CA4 and the ring gear R4 of the fourth planetary gear PGS4 are respectively connected to the second connecting member (4), the fourth connecting member (6) and the output member (2); The first connecting member (3) is also connected to the inner hub of the first brake B1; The second connecting member (4) is also connected to the inner hub of the second brake B2; The third connecting member (5) further connects the inner hub of the first clutch C1 and the inner hub of the third brake B3; The fourth connecting member (6) further connects the outer hub of the second clutch C2 and the inner hub of the fourth brake B4; The fifth connecting member (7) is also connected to the inner hub of the first clutch C1; The input member (1) is also connected to the inner hub of the second clutch C2. 2 . The eleven-speed planetary transmission according to claim 1 , wherein the first planet row PGS1 , the second planet row PGS2 , the third planet row PGS3 and the fourth planet row PGS4 are all single planet rows. 3 . The eleven-speed planetary transmission according to claim 1 , wherein the input shaft is a turbine shaft of a torque converter. 4. The eleven-speed planetary transmission according to claim 1 is characterized in that the brake and the clutch are multi-plate friction operating parts.