CN114791034A - Transmission system, electric drive assembly and vehicle - Google Patents
Transmission system, electric drive assembly and vehicle Download PDFInfo
- Publication number
- CN114791034A CN114791034A CN202210349430.9A CN202210349430A CN114791034A CN 114791034 A CN114791034 A CN 114791034A CN 202210349430 A CN202210349430 A CN 202210349430A CN 114791034 A CN114791034 A CN 114791034A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 68
- 230000007246 mechanism Effects 0.000 claims abstract description 16
- 230000008859 change Effects 0.000 claims abstract description 14
- 230000009977 dual effect Effects 0.000 claims 1
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Structure Of Transmissions (AREA)
Abstract
A transmission system, an electric drive assembly and a vehicle are provided. The transmission system includes: the planetary transmission mechanism is provided with an input part and two output parts, the input part is arranged to be in transmission connection with the motor, and the two output parts are both arranged to be in transmission connection with the wheels; the transmission system has a straight running working mode and a turning working mode; under the straight-ahead working mode, the rotating speeds output by the two output parts are the same; under the turning working mode, the change rates of the rotating speeds output by the two output parts are mutually opposite numbers. The transmission system is applied to a vehicle, and under a straight-going working mode, the rotating speeds output by the two output parts are the same, so that the rotating speed requirements of wheels on two sides of the vehicle in straight-going are met; under the turning working mode, the change rates of the rotating speeds output by the two output parts are opposite numbers, so that the differential function is realized, and the rotating speed requirements of the wheels at two sides of the vehicle during turning are met; in addition, the speed change function is realized by changing the rotating speed of the input part; moreover, the planetary transmission mechanism has the advantages of small volume, light weight and the like.
Description
Technical Field
The present disclosure relates to vehicle technology, in particular to a transmission system, an electric drive assembly and a vehicle.
Background
At present, the design of pure electric vehicles transmission system is mostly parallel shaft layout, carries out power take off through traditional bevel gear differential mechanism. Such a transmission system is bulky and heavy.
Disclosure of Invention
In order to solve at least one of the technical problems, the application provides a transmission system which is small in size and light in weight, solves the problems of large size and large weight of the traditional transmission system, and an electric driving assembly formed by assembling the transmission system and a motor has differential speed and speed change functions.
The present application further provides a vehicle.
The transmission system provided by the embodiment of the invention comprises: the planetary transmission mechanism is provided with an input part and two output parts, the input part is arranged to be in transmission connection with the motor, and the two output parts are both arranged to be in transmission connection with the wheels; wherein the transmission system has a straight-driving mode of operation and a turning mode of operation; in the straight-moving working mode, the rotating speeds output by the two output parts are the same; under the turning working mode, the change rates of the rotating speeds output by the two output parts are mutually opposite numbers.
In an exemplary embodiment, the planetary transmission mechanism includes: a simple planetary row with a sun gear, a first planet carrier and a first ring gear, the input being located on the sun gear and the output being located on the first planet carrier; the second gear ring is fixedly arranged and is positioned on one side of the simple planet row; the second planet gear is meshed with the second gear ring; a third gear ring positioned at one side of the second gear ring, and the other output part is positioned on the third gear ring; the third planet wheel is fixedly connected with the second planet wheel and meshed with the third gear ring; and one end of the second planet carrier is fixedly connected with the first gear ring, and the other end of the second planet carrier is in transmission connection with the second planet gear.
In an exemplary embodiment, the second gear ring is located between the first gear ring and the third gear ring.
In an exemplary embodiment, the transmission ratio i is 1+ i 1 /[1-(i 2 /i 3 )]And satisfy i 1 *i 2 ＝(i 1 *i 3 -i 2 +i 3 ) 2; wherein i 1 ＝Z R1 /Z S1 ，i 2 ＝Z P2 /Z R2 ，i 3 ＝Z P3 /Z R3 The sun gear is represented by S1, the first ring gear is represented by R1, the second planet gear is represented by P2, the second ring gear is represented by R2, the third planet gear is represented by P3, the third ring gear is represented by R3, and Z represents the number of teeth.
In an exemplary embodiment, the output portion at the first carrier extends through the sun gear.
In an exemplary embodiment, the first carrier and the third ring gear are located between the two output portions.
In an exemplary embodiment, the second gear ring is an outer gear ring or an inner gear ring, and the third gear ring is an outer gear ring or an inner gear ring.
In an exemplary embodiment, the second planet wheel and the third planet wheel are a double planet wheel of an integrated structure.
The electric drive assembly provided by the embodiment of the invention comprises a motor and the transmission system of any one of the embodiments, wherein the motor is in transmission connection with the input part.
The vehicle provided by the embodiment of the invention comprises wheels and the transmission system of any embodiment, wherein the wheels are in transmission connection with the output part.
In an exemplary embodiment, the vehicle is an electric vehicle.
The transmission system is applied to vehicles, and in a straight-going working mode, the rotating speeds output by the two output parts are the same, so that the rotating speed requirements of wheels on two sides of the vehicles in straight-going are met; under the turning working mode, the change rates of the rotating speeds output by the two output parts are opposite numbers, so that the differential function is realized, and the rotating speed requirements of the wheels at two sides of the vehicle during turning are met; in addition, the speed change function is realized by changing the rotating speed of the input part; moreover, the planetary transmission mechanism has the advantages of small size, light weight and the like, and the electric drive assembly assembled by the planetary transmission mechanism and the motor has integrated design on a speed reduction structure and a differential structure, and has the advantages of compact structure, high transmission efficiency, large transmission ratio and the like.
Additional features and advantages of the application will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by the practice of the application. Other advantages of the present application can be realized and attained by the instrumentalities and combinations particularly pointed out in the specification and the drawings.
Drawings
The accompanying drawings are included to provide an understanding of the present disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the examples serve to explain the principles of the disclosure and not to limit the disclosure.
FIG. 1 is a schematic structural diagram of an electric drive assembly according to an embodiment of the present invention;
FIG. 2 is a graph of rotational speed of various components of the electric drive assembly of FIG. 1 in a straight-ahead mode of operation;
FIG. 3 is a graph of the rotational speed of components of the electric drive assembly of FIG. 1 in a right turn mode of operation versus the rotational speed of components in a straight mode of operation;
FIG. 4 is a graph illustrating the rotational speed of the various components of the electric drive assembly of FIG. 1 in a left turn mode of operation versus a straight mode of operation.
Wherein, the corresponding relation between the reference numbers and the part names in fig. 1 is:
100 machines, 210 sun, 211 input, 220 first planet wheels, 230 first planet carrier, 231 first output, 240 first ring gear, 250 second ring gear, 260 second planet wheels, 270 third ring gear, 271 second output, 280 third planet wheels, 290 second planet carrier, 300 double planet wheels.
Detailed Description
The present embodiments are described herein, but are by way of illustration rather than limitation, and the objects, aspects and advantages of the present invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings. In the case of no conflict, the present application shall be defined
The embodiments and features of the embodiments can be combined with each other in any desired manner.
Embodiments of the present invention provide a vehicle (not shown) including a wheel and an electric drive assembly. As shown in fig. 1, an electric drive assembly includes an electric machine 100 and a drive train. The transmission system includes: the planetary transmission mechanism is provided with an input part 211 and two output parts, wherein the input part 211 is in transmission connection with the motor 100, and the two output parts are in transmission connection with a group of wheels correspondingly; the transmission system has a straight running working mode and a turning working mode; under the straight-ahead working mode, the rotating speeds output by the two output parts are the same; in the turning working mode, the change rates of the rotating speeds output by the two output parts are opposite numbers, namely the output rotating speed of one output part is increased, and the output rotating speed of the other output part is decreased.
In the vehicle, under the straight-ahead operation mode, the rotating speeds output by the two output parts are the same, so that the rotating speed requirements of wheels on two sides of the vehicle in straight-ahead operation are met; under the turning working mode, the change rates of the rotating speeds output by the two output parts are opposite numbers, so that the differential function is realized, and the rotating speed requirements of the wheels at two sides of the vehicle during turning are met; in addition, by changing the rotation speed of the input portion 211, a speed change function is realized; moreover, the planetary transmission mechanism has the advantages of small size, light weight and the like, and the electric drive assembly assembled by the planetary transmission mechanism and the motor 100 integrates the speed reduction structure and the differential structure, so that the planetary transmission mechanism has the advantages of compact structure, high transmission efficiency, large transmission ratio and the like.
In an exemplary embodiment, as shown in fig. 1, the planetary gear mechanism includes: a simple planetary row with a sun gear 210, a first planet gear 220, a first carrier 230 and a first ring gear 240, the input 211 being located on the sun gear 210, and an output (i.e. a first output 231) being located on the first carrier 230; a second fixed gear ring 250 (e.g., the second gear ring 250 is fixed to a stationary member such as a housing) positioned on one side of the simple planetary row; a second planetary gear 260 meshed with the second ring gear 250; a third ring gear 270 located on a side of the second ring gear 250 facing away from the first ring gear 240 (i.e., the second ring gear 250 is located between the first ring gear 240 and the third ring gear 270), another output portion (i.e., the second output portion 271) is located on the third ring gear 270 (i.e., the third ring gear 270 has a bottom wall, and the second output portion 271 is located on a side of the bottom wall facing away from the sun gear 210 and is fixedly connected to the bottom wall), and the first carrier 230 and the third ring gear 270 are located between the two output portions; a third planet gear 280 fixedly connected with the second planet gear 260 and meshed with the third gear ring 270; and a second planet carrier 290, one end of which is fixedly connected with the first gear ring 240 and the other end of which is in transmission connection with the second planet gear 260.
The input portion 211 drives the sun gear 210 to rotate. The sun gear 210 drives the first planet gear 220 to rotate, the first planet gear 220 drives the first ring gear 240 to rotate, the first planet gear 220 also drives the first planet carrier 230 to rotate, and the first planet carrier 230 drives the first output part 231 to rotate together for power output. The first gear ring 240 drives the second planet carrier 290 to rotate, the second planet carrier 290 drives the second planet gear 260 and the third planet gear 280 to rotate together, the second gear ring 250 is fixed, the third planet gear 280 drives the third gear ring 270 to rotate, and the third gear ring 270 drives the second output part 271 to rotate together to output power.
In the planetary gear train, the sun gear 210 is denoted as S1, the first ring gear 240 is denoted as R1, the second planet gears 260 are denoted as P2, the second ring gear 250 is denoted as R2, the third planet gears 280 are denoted as P3, the third ring gear 270 is denoted as R3, C1 represents the rotation speed of the first carrier 230, C2 represents the rotation speed of the second carrier 290, and Z represents the number of teeth. Transmission ratio i of transmission system is 1+ i 1 /[1-(i 2 /i 3 )]And satisfy i 1 *i 2 ＝(i 1 *i 3 -i 2 +i 3 ) 2; wherein i 1 ＝Z R1 /Z S1 ，i 2 ＝Z P2 /Z R2 ，i 3 ＝Z P3 /Z R3 。i 1 Is the gear ratio of the first ring gear 240 to the sun gear 210, i 2 Is the gear ratio, i, of the second planet gear 260 to the second annulus 250 3 The gear ratio of the third planetary gear 280 to the third ring gear 270. In fig. 2 to 4, a is a curve of the rotation speed in the right-turn operation mode, b is a curve of the rotation speed in the left-turn operation mode, and c is a curve of the rotation speed in the straight-line operation mode.
As shown in fig. 2, in the direct driving operation mode, the motor 100 inputs power to the sun gear 210, and the first output part 231 and the second output part 271 output the same rotation speed, so as to ensure the same rotation speed of the wheels on both sides and achieve the same rotation speed and torque output. As shown in fig. 3, in the right-hand turning operation mode, the right-hand wheels (which rotate faster than the left-hand wheels) drive the rotation speeds of the second output portion 271 and the third ring gear 270 to increase by a set value, the rotation speeds of the second planet carrier 290 and the first ring gear 240 increase by a corresponding value, and the rotation speeds of the first planet carrier 230 and the first output portion 231 decrease by a set value (i.e., the increased rotation speed value of the second output portion 271 is equal to the decreased rotation speed value of the first output portion 231), so as to realize the differential function. As shown in fig. 4, in the left-hand turning operation mode, the left-hand wheels (which rotate faster than the right-hand wheels) drive the first carrier 230 and the first output portion 231 to increase by a set value, the rotation speeds of the second carrier 290 and the first ring gear 240 decrease by a corresponding value, and the rotation speeds of the second output portion 271 and the third ring gear 270 decrease by a set value (i.e., the increased rotation speed value of the first output portion 231 is equal to the decreased rotation speed value of the second output portion 271), so as to realize the differential function. The speed change function is realized by changing the output rotation speed of the motor 100.
In one example, as shown in fig. 1, the first carrier 230 is partially located on a side of the first planetary gear 220 facing the second ring gear 250 (i.e., the first carrier 230 is partially located on a right side of the first planetary gear 220, and is located at the first output portion 231 and passes through the sun gear 210), and the electric machine 100 is a ring-shaped electric machine 100. The input part 211 is a hollow shaft, and the first output part 231 penetrates through the input part 211 and the motor 100 leftwards and then is fixedly connected with the wheels, so that the planetary transmission mechanism can be arranged to be located in the same shell, only one set of forced lubrication system needs to be equipped at the moment, and the structure is simpler and more reasonable.
It may be that, as shown in fig. 1, the second gear ring 250 is an outer gear ring; alternatively, the second ring gear 250 may be a ring gear; it may be that, as shown in fig. 1, the third ring gear 270 is an outer ring gear; alternatively, the third gear 270 may be an inner gear; the objectives of the present application can be achieved without departing from the design concept of the present invention, and therefore, the present application shall not be repeated herein and shall fall within the protection scope of the present application.
As shown in fig. 1, the second planet gear 260 and the third planet gear 280 may be a duplex planet gear 300 of an integrated structure; or the second planet gear 260 and the third planet gear 280 may be separate structures and fixedly connected by a spline or the like; the above objectives can be achieved without departing from the design concept of the present invention, and therefore, the details are not repeated herein and all of the objectives should fall within the protection scope of the present application.
In one example, the vehicle is an electric vehicle, and the electric vehicle is a pure electric vehicle.
In summary, the transmission system provided by the application is applied to a vehicle, and in a straight-ahead operation mode, the rotating speeds output by the two output parts are the same, so that the rotating speed requirements of wheels on two sides of the vehicle when the vehicle runs straight are met; in a turning working mode, the change rates of the rotating speeds output by the two output parts are opposite numbers, so that a differential function is realized, and the rotating speed requirements of wheels at two sides during turning of the vehicle are met; in addition, the speed change function is realized by changing the rotating speed of the input part; moreover, the planetary transmission mechanism has the advantages of small size, light weight and the like, and the electric drive assembly assembled by the planetary transmission mechanism and the motor has integrated design on a speed reduction structure and a differential structure, and has the advantages of compact structure, high transmission efficiency, large transmission ratio and the like.
In the description of the present invention, it should be noted that the terms "upper", "lower", "one side", "the other side", "one end", "the other end", "side", "opposite", "four corners", "periphery", "mouth" structure ", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the structures referred to have specific orientations, are configured and operated in specific orientations, and thus, are not to be construed as limiting the present invention.
In the description of the embodiments of the present invention, unless otherwise explicitly specified or limited, the terms "connected," "directly connected," "indirectly connected," "fixedly connected," "mounted," and "mounted" are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; the terms "mounted," "connected," and "fixedly connected" may refer to a direct connection, an indirect connection through intervening media, and a connection between two elements. The specific meanings of the above terms in the present invention can be understood in a specific case to those of ordinary skill in the art.
Although the embodiments of the present invention have been described above, the above description is only for the convenience of understanding the present invention, and is not intended to limit the present invention. It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (10)
1. A transmission system, comprising:
the planetary transmission mechanism is provided with an input part and two output parts, the input part is arranged to be in transmission connection with the motor, and the two output parts are both arranged to be in transmission connection with the wheels;
wherein the transmission system has a straight-travel mode of operation and a cornering mode of operation; in the straight-moving working mode, the rotating speeds output by the two output parts are the same; under the turning working mode, the change rates of the rotating speeds output by the two output parts are mutually opposite numbers.
2. The transmission system of claim 1, wherein the planetary transmission comprises:
a simple planetary row with a sun gear, a first planet carrier and a first ring gear, the input being located on the sun gear and the output being located on the first planet carrier;
the second gear ring is fixedly arranged and is positioned on one side of the simple planet row;
the second planet gear is meshed with the second gear ring;
a third gear ring, which is positioned at one side of the second gear ring, and the other output part is positioned on the third gear ring;
the third planet wheel is fixedly connected with the second planet wheel and meshed with the third gear ring; and
and one end of the second planet carrier is fixedly connected with the first gear ring, and the other end of the second planet carrier is in transmission connection with the second planet gear.
3. A transmission system according to claim 2, characterised in that the transmission ratio i-1 + i of the transmission system 1 /[1-(i 2 /i 3 )]And satisfy i 1 *i 2 ＝(i 1 *i 3 -i 2 +i 3 )/2；
Wherein i 1 ＝Z R1 /Z S1 ，i 2 ＝Z P2 /Z R2 ，i 3 ＝Z P3 /Z R3 The sun gear is represented by S1, the first gear ring is represented by R1, the second planet gear is represented by P2, the second ring gear is represented by R2, the third planet gear is represented by P3, the third gear ring is represented by R3, and Z represents the number of teeth.
4. The transmission system of claim 2, wherein the second ring gear is located between the first ring gear and the third ring gear, the output at the first carrier extending through the sun gear.
5. The transmission system of claim 2, wherein the first carrier and the third ring gear are located between the two outputs.
6. The transmission system of claim 2, wherein the second gear ring is an outer gear ring or an inner gear ring and the third gear ring is an outer gear ring or an inner gear ring.
7. The transmission system of claim 2, wherein the second planet gears and the third planet gears are dual planet gears of a unitary structure.
8. An electric drive assembly comprising an electric machine and a drive system as claimed in any one of claims 1 to 7, the electric machine being in driving connection with the input.
9. A vehicle comprising a wheel and the transmission system of claim 8, the wheel being in driving connection with the output.
10. The vehicle of claim 9, characterized in that the vehicle is an electric automobile.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210349430.9A CN114791034A (en) | 2022-04-01 | 2022-04-01 | Transmission system, electric drive assembly and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210349430.9A CN114791034A (en) | 2022-04-01 | 2022-04-01 | Transmission system, electric drive assembly and vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114791034A true CN114791034A (en) | 2022-07-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210349430.9A Pending CN114791034A (en) | 2022-04-01 | 2022-04-01 | Transmission system, electric drive assembly and vehicle |
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| Country | Link |
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| CN (1) | CN114791034A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024044904A1 (en) * | 2022-08-29 | 2024-03-07 | 宁德时代(上海)智能科技有限公司 | Differential device and electric device |
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| JP2003048442A (en) * | 2001-08-02 | 2003-02-18 | Honda Motor Co Ltd | Four-wheel drive device for vehicle |
| CN101861477A (en) * | 2007-12-20 | 2010-10-13 | 腓特烈斯港齿轮工厂股份公司 | Transmission device comprising at least two output shafts |
| CN109895619A (en) * | 2017-12-11 | 2019-06-18 | 郑州宇通客车股份有限公司 | A kind of Direct wheel drives system and the vehicle with the Direct wheel drives system |
| CN111434952A (en) * | 2019-01-15 | 2020-07-21 | 通用汽车环球科技运作有限责任公司 | Planetary differential drive system |
| DE102019203212A1 (en) * | 2019-03-08 | 2020-09-10 | Zf Friedrichshafen Ag | Differential gear assembly and drive train with differential gear assembly |
-
2022
- 2022-04-01 CN CN202210349430.9A patent/CN114791034A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003048442A (en) * | 2001-08-02 | 2003-02-18 | Honda Motor Co Ltd | Four-wheel drive device for vehicle |
| CN101861477A (en) * | 2007-12-20 | 2010-10-13 | 腓特烈斯港齿轮工厂股份公司 | Transmission device comprising at least two output shafts |
| CN109895619A (en) * | 2017-12-11 | 2019-06-18 | 郑州宇通客车股份有限公司 | A kind of Direct wheel drives system and the vehicle with the Direct wheel drives system |
| CN111434952A (en) * | 2019-01-15 | 2020-07-21 | 通用汽车环球科技运作有限责任公司 | Planetary differential drive system |
| DE102019203212A1 (en) * | 2019-03-08 | 2020-09-10 | Zf Friedrichshafen Ag | Differential gear assembly and drive train with differential gear assembly |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024044904A1 (en) * | 2022-08-29 | 2024-03-07 | 宁德时代(上海)智能科技有限公司 | Differential device and electric device |
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Effective date of registration: 20240613 Address after: No. 98 Beihui Road, Huishan Industrial Transformation and Agglomeration Zone, Wuxi City, Jiangsu Province, China Applicant after: Wuxi Xingqu Power Technology Co.,Ltd. Country or region after: China Applicant after: Wuxi Xingqu Technology Co.,Ltd. Address before: 310051 No. 1760, Jiangling Road, Hangzhou, Zhejiang, Binjiang District Applicant before: ZHEJIANG GEELY HOLDING GROUP Co.,Ltd. Country or region before: China Applicant before: Wuxi Xingqu Technology Co.,Ltd. Applicant before: Wuxi Xingqu Power Technology Co.,Ltd. |