CN111536211A

CN111536211A - Multi-gear planetary gear speed change device

Info

Publication number: CN111536211A
Application number: CN202010576423.3A
Authority: CN
Inventors: 董鹏; 徐向阳; 刘艳芳; 王书翰; 郭伟
Original assignee: Beihang University
Current assignee: Beihang University
Priority date: 2020-06-23
Filing date: 2020-06-23
Publication date: 2020-08-14
Anticipated expiration: 2040-06-23
Also published as: CN111536211B

Abstract

The invention discloses a multi-gear planetary gear speed change device, which comprises 8 rotating shafts, 5 brakes, 2 clutches and 5 planetary rows, wherein the multi-gear planetary gear speed change device adopts 5 simple minus planetary rows and 7 gear shift elements (comprising 5 brakes and 2 clutches), and the 2 clutches are arranged at the front end of a speed changer but not in the middle of the speed changer, so that oil supply is very convenient; the hydraulic brake comprises 5 brakes, the number of the brakes is large, the brakes can be arranged in an embedded planetary row, pressure oil can be directly supplied to the brakes from a box body, and the structural layout is more compact; and 2 shifting elements are closed in each gear, so that 12 forward gears and 1 reverse gear can be realized, the gear number is more, and the transmission ratio range is wider.

Description

Multi-gear planetary gear speed change device

Technical Field

The invention belongs to the technical field of automobile transmissions, and particularly relates to a multi-gear planetary gear speed change device.

Background

The requirements on fuel economy and dynamic performance of automobiles promote the number of gears of the AT automatic transmission of the automobile to be more and more, and the transmission ratio range to be larger and larger. The prior art provides an 8-gear planetary gear automatic transmission, which comprises 4 planetary rows and 5 gear shifting elements (3 clutches and 2 brakes), wherein each gear shifting element is closed to realize 8 forward gears and 1 reverse gear, only 8 forward gears can be realized, 3 clutches in the 5 gear shifting elements are arranged in the middle of the transmission, oil supply to the clutches is difficult, oil supply channels are complex, and the processing and manufacturing cost is increased. Another technique has proposed a 9-speed planetary gear automatic transmission including 4 planetary rows, 6 shift elements (3 clutches and 3 brakes), and 3 shift elements are engaged to realize 9 forward gears and 1 reverse gear per gear, and only 9 forward gears can be realized, and there are 3 clutches and 3 brakes in the 6 shift elements, and 1 clutch in the 3 clutches is disposed in the middle of the transmission, and it is difficult to supply oil. The four-wheel four-.

Disclosure of Invention

In order to solve the defects of the prior art, the invention provides a longitudinal 12-gear speed changing device for a front-engine rear-drive vehicle, which has the following specific technical scheme:

a multi-speed planetary transmission comprising:

a box body;

the eight rotating shafts are respectively a first rotating shaft, a second rotating shaft, a third rotating shaft, a fourth rotating shaft, a fifth rotating shaft, a sixth rotating shaft, a seventh rotating shaft and an eighth rotating shaft;

the gear shifting element comprises five brakes, namely a B1 brake, a B2 brake, a B3 brake, a B4 brake and a B5 brake; two clutches, a C1 clutch and a C2 clutch;

five planet rows, PG1 planet row, PG2 planet row, PG3 planet row, PG4 planet row and PG5 planet row respectively;

wherein the C1 clutch connects the first rotating shaft and the fourth rotating shaft; the C2 clutch connects the first rotating shaft and the fifth rotating shaft;

the B1 brake is connected with the seventh rotating shaft and the box body, the B2 brake is connected with the sixth rotating shaft and the box body, the B3 brake is connected with the fifth rotating shaft and the box body, the B4 brake is connected with the third rotating shaft and the box body, and the B5 brake is connected with the eighth rotating shaft and the box body;

the sun gear of the PG1 planet row is positioned on the first rotating shaft, the planet carrier is positioned on the eighth rotating shaft, and the gear ring is positioned on the seventh rotating shaft; the sun gear of the PG2 planet row is positioned on the first rotating shaft, the planet carrier is positioned on the sixth rotating shaft, and the gear ring is positioned on the seventh rotating shaft; the sun gear of the PG3 planet row is positioned on the seventh rotating shaft, the planet carrier is positioned on the sixth rotating shaft, and the ring gear is positioned on the third rotating shaft; the sun gear of the PG4 planet row is positioned on the fourth rotating shaft, the planet carrier is positioned on the fifth rotating shaft, and the ring gear is positioned on the sixth rotating shaft; the sun gear of the PG5 planet row is positioned on the fourth rotating shaft, the planet carrier is positioned on the second rotating shaft, and the gear ring is positioned on the fifth rotating shaft;

the first rotating shaft is an input shaft, and the second rotating shaft is an output shaft; the shifting elements can be selectively operated, so that twelve forward gears and one reverse gear can be realized by different transmission ratios between the first rotating shaft and the second rotating shaft, and each gear only needs to be closed by two shifting elements.

Further, the PG1, PG2, PG3, PG4, and PG5 planetary rows are simple minus planetary rows.

Further, the PG1, PG2, PG3, PG4, and PG5 planet rows each include a sun gear, a planet carrier, and a ring gear.

Further, a multi-gear planetary gear speed changing device,

reverse gear is achieved by the B1 brake and the B3 brake being closed,

a first forward gear is achieved by the B3 brake and the B5 brake being closed,

a second forward gear is achieved by the B3 brake and the B4 brake being closed,

a third forward gear is achieved by the C1 clutch and the B3 brake being closed,

a fourth forward gear is achieved by the C1 clutch and the B4 brake being closed,

a fifth forward gear is achieved by the C1 clutch and the B5 brake being closed,

a sixth forward gear is achieved by the C1 clutch and the B2 brake being closed,

a seventh forward gear is achieved by the C1 clutch and the B1 brake being closed,

an eighth forward gear is achieved by the C1 clutch and the C2 clutch being closed,

a ninth forward gear is achieved by the C2 clutch and the B1 brake being closed,

a tenth forward gear is achieved by the C2 clutch and the B2 brake being closed,

an eleventh forward gear is achieved by the C2 clutch and the B5 brake being closed,

a twelfth forward gear is achieved with the C2 clutch and the B4 brake closed.

The invention has the beneficial effects that:

1. according to the invention, each gear is closed by 2 shifting elements, 12 forward gears and 1 reverse gear can be realized, the number of gears is more, and the transmission ratio range is wider.

2. The invention can realize 1 large 1-gear speed ratio, has wider speed ratio range and is beneficial to the low-speed running operation of the commercial vehicle.

3. The invention adopts 5 simple minus planetary rows, 7 gear shifting elements (comprising 5 brakes and 2 clutches), and 2 clutches are arranged at the front end of the transmission instead of the middle part of the transmission, so that oil supply is very convenient; contain 5 brakes, the stopper quantity is many, can inlay the planet row and arrange, and pressure oil can be directly supplied to the brake from the box, and structural layout is more compact.

Drawings

In order to illustrate embodiments of the present invention or technical solutions in the prior art more clearly, the drawings which are needed in the embodiments will be briefly described below, so that the features and advantages of the present invention can be understood more clearly by referring to the drawings, which are schematic and should not be construed as limiting the present invention in any way, and for a person skilled in the art, other drawings can be obtained on the basis of these drawings without any inventive effort. Wherein:

FIG. 1 is a block diagram of the present invention.

The reference numbers illustrate:

1-a first rotating shaft, 2-a second rotating shaft, 3-a third rotating shaft, 4-a fourth rotating shaft, 5-a fifth rotating shaft, 6-a sixth rotating shaft, 7-a seventh rotating shaft and 8-an eighth rotating shaft.

Detailed Description

In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments of the present invention and features of the embodiments may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

As shown in fig. 1, a multi-speed planetary gear transmission device includes:

a case (not shown);

the eight rotating shafts are respectively a first rotating shaft 1, a second rotating shaft 2, a third rotating shaft 3, a fourth rotating shaft 4, a fifth rotating shaft 5, a sixth rotating shaft 6, a seventh rotating shaft 7 and an eighth rotating shaft 8;

the C1 clutch is connected with the first rotating shaft 1 and the fourth rotating shaft 4; the C2 clutch connects the first rotating shaft 1 and the fifth rotating shaft 5;

the B1 brake is connected with the seventh rotating shaft 7 and the box body, the B2 brake is connected with the sixth rotating shaft 6 and the box body, the B3 brake is connected with the fifth rotating shaft 5 and the box body, the B4 brake is connected with the third rotating shaft 3 and the box body, and the B5 brake is connected with the eighth rotating shaft 8 and the box body;

the sun gear of the PG1 planet row is positioned on the first rotating shaft 1, the planet carrier is positioned on the eighth rotating shaft 8, and the gear ring is positioned on the seventh rotating shaft 7; the sun gear of the PG2 planet row is positioned on the first rotating shaft 1, the planet carrier is positioned on the sixth rotating shaft 6, and the ring gear is positioned on the seventh rotating shaft 7; the sun gear of the PG3 planet row is positioned on the seventh rotating shaft 7, the planet carrier is positioned on the sixth rotating shaft 6, and the ring gear is positioned on the third rotating shaft 3; the sun gear of the PG4 planet row is positioned on the fourth rotating shaft 4, the planet carrier is positioned on the fifth rotating shaft 5, and the ring gear is positioned on the sixth rotating shaft 6; the sun gear of the PG5 planet row is positioned on the fourth rotating shaft 4, the planet carrier is positioned on the second rotating shaft 2, and the ring gear is positioned on the fifth rotating shaft 5;

the first rotating shaft 1 is an input shaft, and the second rotating shaft 2 is an output shaft; the shifting elements can be selectively actuated, so that twelve forward gears and one reverse gear can be achieved by means of different transmission ratios between the first rotary shaft 1 and the second rotary shaft 2, each gear only requiring two shifting elements to be engaged.

The transmission adopts 5 simple negative planetary rows and 7 shifting elements (comprising 5 brakes and 2 clutches), and the 2 clutches are arranged at the front end of the transmission instead of the middle part of the transmission, so that oil supply is very convenient; contain 5 brakes, the stopper quantity is many, can inlay the planet row and arrange, and pressure oil can be directly supplied to the brake from the box, and structural layout is more compact.

The PG1 planet row, the PG2 planet row, the PG3 planet row, the PG4 planet row, and the PG5 planet row are simple minus planet rows.

The PG1, PG2, PG3, PG4, and PG5 planet rows each comprise a sun, a planet carrier, and a ring gear.

A multi-gear planetary gear speed change device, reverse gear is realized by a closed B1 brake and a B3 brake, a first forward gear is realized by a closed B3 brake and a B5 brake, a second forward gear is realized by a closed B3 brake and a B4 brake, a third forward gear is realized by a closed C1 clutch and a B3 brake, a fourth forward gear is realized by a closed C1 clutch and a B4 brake, a fifth forward gear is realized by a closed C1 clutch and a B5 brake, a sixth forward gear is realized by a closed C1 clutch and a B2 brake, a seventh forward gear is realized by a closed C1 clutch and a B1 brake, an eighth forward gear is realized by a closed C1 clutch and a C2 clutch, a ninth forward gear is realized by a closed C2 clutch and a B1 brake, a tenth forward gear is realized by a closed C2 clutch and a B2 brake, and an eleventh forward gear is realized by a closed C5 brake and a B2 brake, the twelfth forward gear is achieved with the C2 clutch and the B4 brake closed.

And 2 shifting elements are closed in each gear, so that 12 forward gears and 1 reverse gear can be realized, the gear number is more, and the transmission ratio range is wider.

The brake and the clutch are wet multi-plate friction operating pieces.

Table 1 shows the shift logic of the present solution and the possible gear ratios of the gears, where the adjacent gears are simply shifted, ● indicates the shifting element is closed, and x indicates the shifting element is open. 1 great 1-gear speed ratio can be realized, and the low-speed running operation of the commercial vehicle is facilitated.

TABLE 1 Shift logic and one possible Gear ratio

Gear position

C1

C2

B1

B2

B3

B4

B5

Transmission ratio

Reverse gear

×

●

×

●

×

-6.065

1 gear

×

●

×

●

17.184

2 keeps off

×

●

×

5.771

3 grade

●

×

●

×

3.4

4-gear

●

×

●

×

2.526

5-gear

●

×

●

2.029

6-gear

●

×

●

×

1.846

7 shift

●

×

●

×

1.469

8 keep off

●

×

1

9 gear

×

●

×

0.725

10 keeps off

×

●

×

●

×

0.648

11 grade

×

●

×

●

0.624

12 gear

×

●

×

●

×

0.582

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

In the present invention, the terms "first", "second", "third", and "fourth" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. The term "plurality" means two or more unless expressly limited otherwise.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. 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.

Claims

1. A multi-speed planetary transmission comprising:

a box body;

the eight rotating shafts are respectively a first rotating shaft (1), a second rotating shaft (2), a third rotating shaft (3), a fourth rotating shaft (4), a fifth rotating shaft (5), a sixth rotating shaft (6), a seventh rotating shaft (7) and an eighth rotating shaft (8);

wherein the C1 clutch connects the first rotating shaft (1) and the fourth rotating shaft (4); the C2 clutch connects the first rotating shaft (1) and the fifth rotating shaft (5);

the B1 brake is connected with the seventh rotating shaft (7) and the box body, the B2 brake is connected with the sixth rotating shaft (6) and the box body, the B3 brake is connected with the fifth rotating shaft (5) and the box body, the B4 brake is connected with the third rotating shaft (3) and the box body, and the B5 brake is connected with the eighth rotating shaft (8) and the box body;

the sun gear of the PG1 planet row is positioned on the first rotating shaft (1), the planet carrier is positioned on the eighth rotating shaft (8), and the gear ring is positioned on the seventh rotating shaft (7); the sun gear of the PG2 planet row is positioned on the first rotating shaft (1), the planet carrier is positioned on the sixth rotating shaft (6), and the gear ring is positioned on the seventh rotating shaft (7); the sun gear of the PG3 planet row is positioned on the seventh rotating shaft (7), the planet carrier is positioned on the sixth rotating shaft (6), and the gear ring is positioned on the third rotating shaft (3); the sun gear of the PG4 planet row is positioned on the fourth rotating shaft (4), the planet carrier is positioned on the fifth rotating shaft (5), and the ring gear is positioned on the sixth rotating shaft (6); the sun gear of the PG5 planet row is positioned on the fourth rotating shaft (4), the planet carrier is positioned on the second rotating shaft (2), and the gear ring is positioned on the fifth rotating shaft (5);

the first rotating shaft (1) is an input shaft, and the second rotating shaft (2) is an output shaft; the shifting elements can be selectively operated, so that twelve forward gears and one reverse gear can be realized through different transmission ratios between the first rotating shaft (1) and the second rotating shaft (2), and each gear only needs to be closed by two shifting elements.

2. The multi-speed planetary gear transmission as claimed in claim 1, wherein the PG1, PG2, PG3, PG4 and PG5 planetary rows are simple minus planetary rows.

3. The multi-speed planetary gear set as in claim 1, wherein the PG1, PG2, PG3, PG4, and PG5 planetary rows each comprise a sun, a planet carrier, and a ring gear.

4. A multi-speed planetary gear transmission according to any of claims 1 to 3,

reverse gear is achieved by the B1 brake and the B3 brake being closed,

a first forward gear is achieved by the B3 brake and the B5 brake being closed,

a twelfth forward gear is achieved with the C2 clutch and the B4 brake closed.