CN115071337B - Automobile and electric drive transmission mechanism thereof - Google Patents

Automobile and electric drive transmission mechanism thereof Download PDF

Info

Publication number
CN115071337B
CN115071337B CN202210744852.6A CN202210744852A CN115071337B CN 115071337 B CN115071337 B CN 115071337B CN 202210744852 A CN202210744852 A CN 202210744852A CN 115071337 B CN115071337 B CN 115071337B
Authority
CN
China
Prior art keywords
gear
shaft
sun gear
planetary
planetary gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202210744852.6A
Other languages
Chinese (zh)
Other versions
CN115071337A (en
Inventor
马飞龙
赵玉婷
林霄喆
于海生
施悠笛
孔子豪
章金乐
孙峰
于闯
谭艳军
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wuxi Xingqu Power Technology Co ltd
Wuxi Xingqu Technology Co ltd
Original Assignee
Wuxi Xingqu Power Technology Co ltd
Wuxi Xingqu Technology Co ltd
Zhejiang Geely Holding Group Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wuxi Xingqu Power Technology Co ltd, Wuxi Xingqu Technology Co ltd, Zhejiang Geely Holding Group Co Ltd filed Critical Wuxi Xingqu Power Technology Co ltd
Priority to CN202210744852.6A priority Critical patent/CN115071337B/en
Publication of CN115071337A publication Critical patent/CN115071337A/en
Application granted granted Critical
Publication of CN115071337B publication Critical patent/CN115071337B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/121—Power-transmission from drive shaft to hub
    • B60B35/122—Power-transmission from drive shaft to hub using gearings
    • B60B35/125—Power-transmission from drive shaft to hub using gearings of the planetary type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/14—Torque-transmitting axles composite or split, e.g. half- axles; Couplings between axle parts or sections
    • 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
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • 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
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)

Abstract

An automobile and an electric drive transmission mechanism thereof, wherein the electric drive transmission mechanism comprises a first half shaft; the input shaft is constructed as a hollow shaft and is sleeved on the first half shaft; the second half shaft is coaxially arranged with the first half shaft and the input shaft; the first sun gear is fixedly connected with the input shaft; the second sun gear is fixedly connected with the first half shaft; the third sun gear is fixedly connected with the second half shaft; the planet carrier can rotate around the axis of the input shaft; a first planetary gear meshed with the first sun gear; the second planetary gear is coaxially arranged with the first planetary gear, connected with the first planetary gear and meshed with the second sun gear; a third planetary gear meshed with the third sun gear; the inner gear ring is coaxially arranged with the first half shaft and can not move. The electric drive transmission mechanism can realize speed change and differential speed functions simultaneously, reduces the volume and the mass of transmission parts, and greatly improves the power density of the transmission.

Description

Automobile and electric drive transmission mechanism thereof
Technical Field
The present disclosure relates to the field of automobiles, and more particularly, to an automobile and an electric drive mechanism thereof.
Background
Currently, with the development of the new energy automobile industry, electric automobiles have become a development trend. Because the electric vehicle needs a larger battery to increase the endurance mileage, the mass of the pure electric vehicle sold in the current market is far higher than that of the traditional fuel vehicle. Under the trend of increasing sales of pure electric vehicles, the development of light weight of electric vehicles is imperative, and the importance of the electric vehicles on the reduction of various parts in the vehicles is higher and higher.
The current electric vehicle transmission design is mostly in parallel shaft layout, and meanwhile, a traditional bevel gear differential is used for power output. This design is bulky and heavy.
Disclosure of Invention
For solving the technical problem, the application provides an electric drive transmission mechanism, which comprises:
a first half shaft;
the input shaft is constructed as a hollow shaft and sleeved on the first half shaft;
the second half shaft is coaxially arranged with the first half shaft and the input shaft;
the first sun gear is fixedly connected with the input shaft;
the second sun gear is fixedly connected with the first half shaft;
the third sun gear is fixedly connected with the second half shaft;
a planet carrier rotatable about an axis of the input shaft;
the first planet gear is rotationally connected with the planet carrier and meshed with the first sun gear;
the second planetary gear is rotationally connected with the planet carrier, coaxially arranged with the first planetary gear, connected with the first planetary gear and meshed with the second sun gear;
the third planetary gear is rotationally connected with the planet carrier and meshed with the third sun gear;
an inner gear ring coaxially arranged with the first half shaft and not movable; and
the fourth planetary gear is rotationally connected with the planet carrier and meshed with the annular gear and the third planetary gear;
the first sun gear, the second sun gear and the third sun gear are all coaxially arranged with the input shaft, and the axes of the first planet gear, the second planet gear, the third planet gear and the fourth planet gear are all parallel to the axis of the first half shaft.
In one exemplary embodiment, the gear ratio of the electrically driven transmission, the number of teeth of the first planetary gear, the number of teeth of the second planetary gear, the number of teeth of the first sun gear, the number of teeth of the second sun gear, the number of teeth of the third sun gear, the number of teeth of the ring gear satisfy the following relationship:
wherein i is the gear ratio of the electric drive transmission mechanism, Z 31 For the number of teeth of the first planetary gear, Z 32 For the number of teeth of the second planetary gear, Z 41 For the number of teeth of the first sun gear, Z 42 For the number of teeth of the second sun gear, Z 43 Z is the number of teeth of the third sun gear 60 Is the number of teeth of the inner gear ring.
In one illustrative embodiment, the first sun gear, the second sun gear, the third sun gear, the first planet gear, the second planet gear, the third planet gear, and the fourth planet gear are all cylindrical gears.
In an exemplary embodiment, a fourth planetary gear is located between the ring gear and the third planetary gear, and the third planetary gear is located between the third sun gear and the fourth planetary gear.
In an exemplary embodiment, a plurality of first planetary gears and a plurality of second planetary gears are provided, the plurality of first planetary gears are coaxially arranged with the plurality of second planetary gears, respectively, and each of the first planetary gears is connected with the coaxial second planetary gears;
a plurality of the first planetary gears are uniformly distributed around the first sun gear;
the plurality of second planetary gears are uniformly distributed around the second sun gear.
In an exemplary embodiment, a plurality of the third planetary gears and the fourth planetary gears are provided, and a plurality of the third planetary gears are respectively meshed with a plurality of the fourth planetary gears;
the plurality of third planetary gears are uniformly distributed around the third sun gear, and the plurality of third rotating shafts are uniformly distributed on the inner peripheral wall of the ring gear.
In an exemplary embodiment, the pitch diameter of the first planetary gear is greater than the pitch diameter of the second planetary gear;
the pitch diameter of the first sun gear is smaller than that of the second sun gear.
In an exemplary embodiment, the electro-drive transmission further includes an electric motor having a rotor coupled to the input shaft.
In an exemplary embodiment, the planet carrier is rotatably coupled to the input shaft and the second axle shaft, respectively.
In an exemplary embodiment, the planet carrier comprises
The first connecting part is provided with a first shaft hole, and the input shaft penetrates through the first shaft hole;
the second connecting part is provided with a second shaft hole, and the second half shaft penetrates through the second shaft hole;
the mounting part comprises a connecting frame, a first rotating shaft, a second rotating shaft and a third rotating shaft, wherein the first rotating shaft, the second rotating shaft and the third rotating shaft are parallel to the input shaft, the opposite ends of the first rotating shaft are respectively connected with the first connecting part and the connecting frame, the opposite ends of the second rotating shaft are respectively connected with the second connecting part and the connecting frame, and the opposite ends of the third rotating shaft are respectively connected with the second connecting part and the connecting frame;
the input shaft and the first shaft hole are provided with a first bearing, the second half shaft and the second shaft hole are provided with a second bearing, the first planetary gear and the second planetary gear are sleeved on the first rotating shaft, and the third planetary gear and the fourth planetary gear are sleeved on the second rotating shaft and the third rotating shaft respectively.
The application also provides an automobile which comprises the electric drive transmission mechanism.
The electric drive transmission mechanism can realize speed change and differential speed functions simultaneously, reduces the volume and the mass of transmission parts, and greatly improves the power density of the transmission. Compared with the traditional parallel shaft and bevel gear differential mechanism, the parallel shaft and bevel gear differential mechanism reduces the number of required parts, has more compact structure and lighter weight.
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 practice of the application. Other advantages of the present application may be realized and attained by the structure particularly pointed out in the written description and drawings.
Drawings
The accompanying drawings are included to provide an understanding of the technical aspects of the present application, and are incorporated in and constitute a part of this specification, illustrate the technical aspects of the present application and together with the examples of the present application, and not constitute a limitation of the technical aspects of the present application.
Fig. 1 is a schematic structural diagram of an electric drive mechanism according to an embodiment of the present application;
FIG. 2 is a schematic diagram of an embodiment of the present application when the rotational speeds of the first and second axle shafts are the same;
FIG. 3 is a schematic diagram of an embodiment of the present application in which the rotational speed of the first half shaft is greater than the rotational speed of the second half shaft;
FIG. 4 is a schematic diagram of an embodiment of the present application in which the rotational speed of the first half shaft is less than the rotational speed of the second half shaft.
Detailed Description
As shown in fig. 1, fig. 1 shows an electrically driven transmission mechanism in the present embodiment. The electric drive mechanism includes a motor 10, a first half shaft 22, a second half shaft 23, an input shaft 21, a first sun gear 41, a second sun gear 42, a third sun gear 43, a carrier 50, a first planetary gear 31, a second planetary gear 32, a third planetary gear 33, a fourth planetary gear 34, and an annular gear 60.
The motor 10 includes a stator and a rotor 11, the rotor 11 being rotatable relative to the stator.
The input shaft 21 is configured as a hollow shaft. The input shaft 21 is cylindrical. The input shaft 21 may be arranged horizontally. The input shaft 21 is connected to the rotor 11 of the motor 10. The motor 10 can drive the input shaft 21 to rotate about its own axis.
The first sun gear 41 may be a cylindrical gear. The first sun gear 41 may be arranged at an end of the input shaft 21 facing away from the rotor 11 of the motor 10. The first sun gear 41 is sleeved on the input shaft 21 and is fixedly connected with the input shaft 21. The first sun gear 41 may be an interference fit or a keyed connection, such as a flat key connection or a spline connection, with the input shaft 21.
The first half shaft 22 and the second half shaft 23 may be straight strips. The first half shaft 22 is disposed through the input shaft 21 and coaxially with the input shaft 21. The first half shaft 22 has both ends extending beyond the input shaft 21. The first half shaft 22 and the second half shaft 23 are coaxially arranged. There is a gap between the first half shaft 22 and the second half shaft 23. The first half shaft 22 and the second half shaft 23 are spaced apart from each other.
The second sun gear 42 and the third sun gear 43 may be cylindrical gears. The second sun gear 42 is sleeved on the first half shaft 22 and is fixedly connected with the first half shaft 22. A keyed connection may be used between the second sun gear 42 and the first half shaft 22. The third sun gear 43 is sleeved on the second half shaft 23 and fixedly connected with the second half shaft. A keyed connection may be used between the third sun gear 43 and the second half shaft 23. The second sun gear 42 and the third sun gear 43 are disposed at the ends of the first half shaft 22 and the second half shaft 23, respectively, that are adjacent to each other. The first sun gear 41, the second sun gear 42 and the third sun gear 43 are coaxial, and the second sun gear 42 is located between the first sun gear 41 and the third sun gear 43.
The carrier 50 includes a first connection portion 51, a second connection portion 52, and a mounting portion 53. The mounting portion 53 is provided between the first connection portion 51 and the second connection portion 52, and both ends of the mounting portion 53 are connected to the first connection portion 51 and the second connection portion 52, respectively. The first connecting portion 51 is provided with a first shaft hole 511. The input shaft 21 passes through the first shaft hole 511 of the first connecting portion 51, and the input shaft 21 is disposed coaxially with the first shaft hole 511. A first bearing (not shown) is disposed in the first shaft hole 511, an inner ring of the first bearing is sleeved on the input shaft 21, the first shaft hole 511 is sleeved on an outer ring of the first bearing, and the input shaft 21 and the first connecting portion 51 are rotatably connected together through the first bearing. The second connection portion 52 is provided with a second shaft hole 521. The second half shaft 23 passes through the second shaft hole 521 of the second connection portion 52, and the second half shaft 23 is disposed coaxially with the second shaft hole 521. A second bearing (not shown) is disposed in the second shaft hole 521, the inner ring of the second bearing is sleeved on the second half shaft 23, the second shaft hole 521 is sleeved on the outer ring of the second bearing, and the second half shaft 23 and the second connecting portion 52 are rotatably connected together through the second bearing. Thereby, the carrier 50 can rotate about the axis of the input shaft 21.
The mounting portion 53 includes a first rotation shaft 531, a second rotation shaft 532, and a third rotation shaft 533. The first rotation axis 531, the second rotation axis 532, and the third rotation axis 533 are all parallel to the input shaft 21. The first rotation shaft 531 is located outside the first sun gear 41 and the second sun gear 42. The second rotation shaft 532 is located outside the third sun gear 43.
Ring gear 60 cannot rotate. The inner gear ring 60 may be fixed on the housing of the electric drive mechanism or may be fixed on the mounting base of the electric drive mechanism. The ring gear 60 is disposed coaxially with the input shaft 21. The third rotation shaft 533 of the mounting part 53 is located inside the ring gear 60.
The first, second, third and fourth planetary gears 31, 32, 33 and 34 may be cylindrical gears. The first planetary gear 31 and the second planetary gear 32 are both sleeved on the first rotating shaft 531, the first planetary gear 31 and the second planetary gear 32 are both in clearance fit with the first rotating shaft 531, and the first planetary gear 31 and the second planetary gear 32 can both rotate around the first rotating shaft 531. One ends of the first planetary gear 31 and the second planetary gear 32, which are close to each other, are connected to each other. The first planetary gears 31 intermesh with the first sun gear 41. The second planetary gears 32 intermesh with the second sun gear 42.
The third planetary gear 33 is sleeved on the second rotating shaft 532 and is in clearance fit with the second rotating shaft 532, and the third planetary gear 33 can rotate around the second rotating shaft 532. The third planetary gears 33 mesh with the third sun gear 43. The fourth planetary gear 34 is sleeved on the third rotating shaft 533 and is in clearance fit with the third rotating shaft 533, and the fourth planetary gear 34 can rotate around the third rotating shaft 533. The third planetary gear 33 meshes with the fourth planetary gear 34. The fourth planetary gears 34 mesh with the ring gear 60.
In the present embodiment, when the motor 10 drives the input shaft 21 to rotate, torque is input from the input shaft 21 of the electric drive transmission mechanism into the electric drive transmission mechanism, and then the electric drive transmission mechanism is output through the first half shaft 22 and the second half shaft 23. The first axle 22 and the second axle 23 may circumscribe two wheels, respectively, such that the first axle 22 and the second axle 23 may drive the two wheels to rotate, respectively.
The torque transfer path from the input shaft 21 to the first half shaft 22 is: from the input shaft 21 to the first sun gear 41, from the first sun gear 41 to the first planet gears 31, from the first planet gears 31 to the second planet gears 32, from the second planet gears 32 to the second sun gear 42, and from the second sun gear 42 to the first half shaft 22.
The torque transfer path from the input shaft 21 to the second half shaft 23 is: from the input shaft 21 to the first sun gear 41, from the first sun gear 41 to the planet carrier 50, from the planet carrier 50 to the ring gear 60, from the ring gear 60 to the fourth planet gears 34, from the fourth planet gears 34 to the third planet gears 33, from the third planet gears 33 to the third sun gear 43, and from the third sun gear 43 to the second half shaft 23.
The electric drive transmission mechanism can also realize a shift by changing the gear ratio of the electric drive transmission mechanism by configuring different numbers of teeth of the first planetary gear 31, the second planetary gear 32, the first sun gear 41, the second sun gear 42, the third sun gear 43, and the internal gear.
When the automobile runs on a flat road surface and runs along a straight line, the first half shaft 22 and the second half shaft 23 can respectively drive the two wheels to rotate at the same rotating speed so as to ensure that the automobile keeps straight line motion. When the automobile runs on uneven road or turns, the first half shaft 22 and the second half shaft 23 can respectively drive the two wheels to rotate at different rotation speeds so as to ensure that the two wheels do pure rolling motion on the ground.
Fig. 2 shows the relationship among the rotational speed of the first sun gear S1, the rotational speed of the second sun gear S2, the rotational speed of the third sun gear S3, the rotational speed of the carrier PC, and the rotational speed of the ring gear R in a specific embodiment of the vehicle on a flat road surface and in a straight running condition, in which the rotational speed of the second sun gear S2 and the rotational speed of the third sun gear S3 are identical, whereby the rotational speeds of the first half shaft 22 and the second half shaft 23 are identical.
Fig. 3 shows the relationship among the rotational speed of the first sun gear S1, the rotational speed a of the second sun gear S2, the rotational speed B of the third sun gear S3, the rotational speed of the carrier PC, and the rotational speed of the ring gear R when the vehicle is traveling on an uneven road or when the vehicle is in a cornering situation, the rotational speed of the first half shaft 22 needs to be higher than the rotational speed of the second half shaft 23, and the rotational speed a of the second sun gear S2 is higher than the rotational speed B of the third sun gear S3, whereby the rotational speed of the first half shaft 22 is higher than the rotational speed of the second half shaft 23.
Fig. 4 shows the relationship among the rotational speed of the first sun gear S1, the rotational speed D of the second sun gear S2, the rotational speed C of the third sun gear S3, the rotational speed of the carrier PC, and the rotational speed of the ring gear R when the vehicle is traveling on an uneven road or when the vehicle is in a cornering situation, the rotational speed of the first axle 22 needs to be lower than the rotational speed of the second axle 23, and the rotational speed D of the second sun gear S2 is lower than the rotational speed C of the third sun gear S3, whereby the rotational speed of the first axle 22 is lower than the rotational speed of the second axle 23.
In conclusion, the electric drive transmission mechanism can realize speed change and differential speed functions simultaneously, reduces the volume and the mass of transmission parts, and greatly improves the power density of the transmission. Compared with the traditional parallel shaft and bevel gear differential mechanism, the parallel shaft and bevel gear differential mechanism reduces the number of required parts, has more compact structure and lighter weight.
In one exemplary embodiment, when the gear ratio of the electric drive mechanism, the number of teeth of the first planetary gear 31, the number of teeth of the second planetary gear 32, the number of teeth of the first sun gear 41, the number of teeth of the second sun gear 42, the number of teeth of the third sun gear 43, and the number of teeth of the ring gear 60 have the following relationship, the torque output from the first half shaft 22 and the second half shaft 23 when the vehicle travels on a flat road surface and travels in a straight line is equal, and the rotational speeds of the first half shaft 22 and the second half shaft 23 are the same.
Wherein i is the gear ratio of the electric drive transmission mechanism, Z 31 For the number of teeth, Z, of the first planetary gear 31 32 Z is the number of teeth of the second planetary gear 32 41 Z is the number of teeth of the first sun gear 41 42 Z is the number of teeth of the second sun gear 42 43 Z is the number of teeth of the third sun gear 43 60 Is the number of teeth of the ring gear 60.
In one exemplary embodiment, the ring gear 60 is axially aligned with the third sun gear 43. The mounting portion 53 further includes a connection frame 534. Both ends of the first rotation shaft 531 are connected to the first connection part 51 and the connection frame 534, respectively. Both ends of the second rotation shaft 532 are connected to the second connection part 52 and the connection frame 534, respectively. Both ends of the third rotation shaft 533 are connected to the second connection part 52 and the connection frame 534, respectively. The second rotation shaft 532 is located inside the third rotation shaft 533. The third planetary gear 33 is located between the third sun gear 43 and the fourth planetary gear 34.
Thus, the fourth planetary gear 34 is located between the ring gear 60 and the third planetary gear 33, and the third planetary gear 33 is located between the third sun gear 43 and the fourth planetary gear 34. The fourth planetary gear 34 and the third planetary gear 33 are more balanced and reasonable in stress.
In an exemplary embodiment, the first planetary gears 31, the second planetary gears 32, and the first rotation shafts 531 are all provided in plurality and the same number. The first planetary gears 31 are arranged in one-to-one correspondence with the first rotating shafts 531, and the first planetary gears 31 are sleeved on the corresponding first rotating shafts 531. The second planetary gears 32 are arranged in one-to-one correspondence with the first rotating shafts 531, and the second planetary gears 32 are sleeved on the corresponding first rotating shafts 531. One ends of the first planetary gear 31 and the second planetary gear 32 located on the same rotation shaft, which are close to each other, are connected to each other, and the first planetary gear 31 and the second planetary gear 32 may be integrally formed.
The first rotation shafts 531 are uniformly distributed in the circumferential direction of the first sun gear 41 and the second sun gear 42, so that the plurality of first planetary gears 31 can be uniformly distributed around the first sun gear 41 and the plurality of second planetary gears 32 can be uniformly distributed around the second sun gear 42. The stress of the first sun gear 41, the second sun gear 42, and the carrier 50 is more uniform.
In the first exemplary embodiment, the third planetary gear 33, the fourth planetary gear 34, the second rotation shaft 532, and the third rotation shaft 533 are provided in plurality. The number of the third planetary gears 33 is the same as that of the second rotating shafts 532, and the third planetary gears 33 are sleeved on the second rotating shafts 532 in a one-to-one correspondence. The plurality of second rotating shafts 532 are uniformly distributed around the third sun gear 43, and the plurality of third planetary gears 33 are uniformly distributed around the third sun gear 43.
The number of the fourth planetary gears 34 is the same as that of the third rotating shafts 533, and the fourth planetary gears 34 are sleeved on the third rotating shafts 533 in a one-to-one correspondence. The plurality of third rotating shafts 533 are evenly distributed inside the ring gear 60. The plurality of fourth planetary gears 34 are uniformly distributed on the inner peripheral wall of the ring gear 60. The plurality of third planetary gears 33 are respectively meshed with the plurality of fourth planetary gears 34.
In this way, the stress of the ring gear 60, the third sun gear 43, and the carrier 50 is more uniform.
Further, the number of the third planetary gears 33, the fourth planetary gears 34, the second rotating shafts 532 and the third rotating shafts 533 are the same, one third rotating shaft 533 is arranged on the outer side of each second rotating shaft 532, and one fourth planetary gear 34 is arranged on the outer side of each third planetary gear 33.
In one illustrative embodiment, the pitch diameter of the first planet gears 31 is greater than the pitch diameter of the second planet gears 32, and the pitch diameter of the first sun gear 41 is less than the pitch diameter of the second sun gear 42.
In this way, the electric drive transmission mechanism can output the torque input from the input shaft 21 to the first half shaft 22 at a reduced speed and increased torque.
The embodiment also provides an automobile, which comprises the electric drive transmission mechanism.
The present application describes a number of embodiments, but the description is illustrative and not limiting and it will be apparent to those of ordinary skill in the art that many more embodiments and implementations are possible within the scope of the embodiments described herein. Although many possible combinations of features are shown in the drawings and discussed in the detailed description, many other combinations of the disclosed features are possible. Any feature or element of any embodiment may be used in combination with or in place of any other feature or element of any other embodiment unless specifically limited.
The present application includes and contemplates combinations of features and elements known to those of ordinary skill in the art. The embodiments, features and elements of the present disclosure may also be combined with any conventional features or elements to form a unique inventive arrangement as defined in the claims. Any feature or element of any embodiment may also be combined with features or elements from other inventive arrangements to form another unique inventive arrangement as defined in the claims. Thus, it should be understood that any of the features shown and/or discussed in this application may be implemented alone or in any suitable combination. Accordingly, the embodiments are not to be restricted except in light of the attached claims and their equivalents. Further, various modifications and changes may be made within the scope of the appended claims.
Furthermore, in describing representative embodiments, the specification may have presented the method and/or process as a particular sequence of steps. However, to the extent that the method or process does not rely on the particular order of steps set forth herein, the method or process should not be limited to the particular sequence of steps described. Other sequences of steps are possible as will be appreciated by those of ordinary skill in the art. Accordingly, the particular order of the steps set forth in the specification should not be construed as limitations on the claims. Furthermore, the claims directed to the method and/or process should not be limited to the performance of their steps in the order written, and one skilled in the art can readily appreciate that the sequences may be varied and still remain within the spirit and scope of the embodiments of the present application.

Claims (9)

1. An electrically driven transmission, comprising:
a first half shaft;
the input shaft is constructed as a hollow shaft and sleeved on the first half shaft;
the second half shaft is coaxially arranged with the first half shaft and the input shaft;
the first sun gear is fixedly connected with the input shaft;
the second sun gear is fixedly connected with the first half shaft;
the third sun gear is fixedly connected with the second half shaft;
a planet carrier rotatable about an axis of the input shaft;
the first planet gear is rotationally connected with the planet carrier and meshed with the first sun gear;
the second planetary gear is rotationally connected with the planet carrier, coaxially arranged with the first planetary gear, connected with the first planetary gear and meshed with the second sun gear;
the third planetary gear is rotationally connected with the planet carrier and meshed with the third sun gear;
an inner gear ring coaxially arranged with the first half shaft and not movable; and
the fourth planetary gear is rotationally connected with the planet carrier and meshed with the annular gear and the third planetary gear;
the first sun gear, the second sun gear and the third sun gear are all coaxially arranged with the input shaft, and the axes of the first planet gear, the second planet gear, the third planet gear and the fourth planet gear are all parallel to the axis of the first half shaft;
the first sun gear, the second sun gear, the third sun gear, the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear are all cylindrical gears;
the electric drive transmission mechanism further comprises a motor, and a rotor of the motor is connected to the input shaft.
2. The electrically driven transmission mechanism according to claim 1, wherein the gear ratio of the electrically driven transmission mechanism, the number of teeth of the first planetary gear, the number of teeth of the second planetary gear, the number of teeth of the first sun gear, the number of teeth of the second sun gear, the number of teeth of the third sun gear, the number of teeth of the ring gear satisfy the following relationship:
wherein i is the gear ratio of the electric drive transmission mechanism,for the number of teeth of the first planetary gear, +.>For the number of teeth of the second planetary gear, +.>For the number of teeth of the first sun gear, +.>For the number of teeth of the second sun gear, +.>For the number of teeth of the third sun gear +.>Is the number of teeth of the inner gear ring.
3. The electrically driven transmission of claim 1, wherein a fourth planetary gear is located between the ring gear and the third planetary gear, the third planetary gear being located between the third sun gear and the fourth planetary gear.
4. An electrically driven transmission according to any one of claims 1 to 3, wherein a plurality of said first planetary gears and said second planetary gears are each provided, a plurality of said first planetary gears being provided coaxially with a plurality of said second planetary gears, respectively, each of said first planetary gears being connected with a second planetary gear coaxial therewith;
a plurality of the first planetary gears are uniformly distributed around the first sun gear;
the plurality of second planetary gears are uniformly distributed around the second sun gear.
5. An electric drive transmission according to any one of claims 1 to 3, wherein a plurality of third planetary gears and a plurality of fourth planetary gears are provided, the plurality of third planetary gears being respectively engaged with the plurality of fourth planetary gears;
the plurality of third planetary gears are uniformly distributed around the third sun gear, and the plurality of fourth planetary gears are uniformly distributed on the inner peripheral wall of the ring gear.
6. An electro-drive transmission as claimed in any one of claims 1 to 3, wherein the pitch diameter of the first planet gears is greater than the pitch diameter of the second planet gears;
the pitch diameter of the first sun gear is smaller than that of the second sun gear.
7. An electric drive transmission according to any one of claims 1 to 3, wherein the planet carrier is in rotational connection with the input shaft and the second half shaft, respectively.
8. The electric drive of claim 7, wherein the planet carrier comprises
The first connecting part is provided with a first shaft hole, and the input shaft penetrates through the first shaft hole;
the second connecting part is provided with a second shaft hole, and the second half shaft penetrates through the second shaft hole;
the mounting part comprises a connecting frame, a first rotating shaft, a second rotating shaft and a third rotating shaft, wherein the first rotating shaft, the second rotating shaft and the third rotating shaft are parallel to the input shaft, the opposite ends of the first rotating shaft are respectively connected with the first connecting part and the connecting frame, the opposite ends of the second rotating shaft are respectively connected with the second connecting part and the connecting frame, and the opposite ends of the third rotating shaft are respectively connected with the second connecting part and the connecting frame;
the input shaft and the first shaft hole are provided with a first bearing, the second half shaft and the second shaft hole are provided with a second bearing, the first planetary gear and the second planetary gear are sleeved on the first rotating shaft, and the third planetary gear and the fourth planetary gear are sleeved on the second rotating shaft and the third rotating shaft respectively.
9. An automobile comprising an electrically driven transmission according to any one of claims 1 to 8.
CN202210744852.6A 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof Active CN115071337B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210744852.6A CN115071337B (en) 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210744852.6A CN115071337B (en) 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof

Publications (2)

Publication Number Publication Date
CN115071337A CN115071337A (en) 2022-09-20
CN115071337B true CN115071337B (en) 2024-04-05

Family

ID=83254690

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210744852.6A Active CN115071337B (en) 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof

Country Status (1)

Country Link
CN (1) CN115071337B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115042560B (en) * 2022-06-27 2024-04-12 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof
CN115320295B (en) * 2022-08-19 2024-04-12 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014029203A (en) * 2012-07-03 2014-02-13 Origin Electric Co Ltd Speed reducer of high change gear ratio using planetary gear mechanism
WO2020001588A1 (en) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, power drive system, and vehicle
DE102019214670A1 (en) * 2019-09-25 2021-03-25 Zf Friedrichshafen Ag Arrangement and method for driving a vehicle axle
CN115042560A (en) * 2022-06-27 2022-09-13 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof
CN115320295A (en) * 2022-08-19 2022-11-11 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10399437B2 (en) * 2016-09-06 2019-09-03 Joy Global Underground Mining Llc Coupled compound planetary transmission for a wheel unit
CN107013654B (en) * 2017-04-21 2023-04-07 吉林大学 Electric differential mechanism with torque directional distribution function
CN107420516B (en) * 2017-04-21 2023-04-21 吉林大学 Electric differential mechanism with torque directional distribution function
CN108266512B (en) * 2018-03-19 2023-03-28 吉林大学 Centralized full-time electric four-wheel drive system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014029203A (en) * 2012-07-03 2014-02-13 Origin Electric Co Ltd Speed reducer of high change gear ratio using planetary gear mechanism
WO2020001588A1 (en) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, power drive system, and vehicle
DE102019214670A1 (en) * 2019-09-25 2021-03-25 Zf Friedrichshafen Ag Arrangement and method for driving a vehicle axle
CN115042560A (en) * 2022-06-27 2022-09-13 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof
CN115320295A (en) * 2022-08-19 2022-11-11 浙江吉利控股集团有限公司 Automobile and electric drive transmission mechanism thereof

Also Published As

Publication number Publication date
CN115071337A (en) 2022-09-20

Similar Documents

Publication Publication Date Title
CN115071337B (en) Automobile and electric drive transmission mechanism thereof
CN115320295B (en) Automobile and electric drive transmission mechanism thereof
CN115042560B (en) Automobile and electric drive transmission mechanism thereof
CN101067438B (en) Drive unit for motor vehicle
CN108372778A (en) Three sets of axle construction hybrid power assemblies of double planet wheel rows of mixing
CN115972896A (en) Efficient multi-gear electric drive bridge transmission system
CN112721619A (en) Two-gear speed change bridge driving system without power interruption
WO2019213802A1 (en) Electrical bridge driving system and vehicle
CN108001216B (en) Electric automobile power assembly based on continuously variable transmission
CN208793532U (en) A kind of planet gear type differential mechanism
CN214380504U (en) Integrated differential driving motor
CN114396467A (en) Planet row type transmission and vehicle
CN112046275A (en) Axially aligned coaxially driven axle
CN112046276A (en) Motor-driven coaxial axle
CN219214726U (en) Dual electro-mechanical drive assembly and vehicle
CN217944878U (en) Coaxial drive arrangement and vehicle
CN213108871U (en) Axially-arranged coaxial drive axle
CN213619341U (en) Motor-driven coaxial axle
CN220850585U (en) Planetary gear speed change device and hub motor
CN111327155A (en) Split shaft type hub motor
CN216951528U (en) Planet row type transmission and vehicle
CN220134537U (en) Speed reducer, electric drive axle and new energy automobile
CN219172185U (en) Driving axle and vehicle with same
CN219382202U (en) Coaxial electric drive assembly and vehicle
CN220452686U (en) Speed reducer, speed reduction box and vehicle

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant
TR01 Transfer of patent right

Effective date of registration: 20240613

Address after: No. 98 Beihui Road, Huishan Industrial Transformation and Agglomeration Zone, Wuxi City, Jiangsu Province, China

Patentee after: Wuxi Xingqu Power Technology Co.,Ltd.

Country or region after: China

Patentee after: Wuxi Xingqu Technology Co.,Ltd.

Address before: 310051 No. 1760, Jiangling Road, Hangzhou, Zhejiang, Binjiang District

Patentee before: ZHEJIANG GEELY HOLDING GROUP Co.,Ltd.

Country or region before: China

Patentee before: Wuxi Xingqu Technology Co.,Ltd.

Patentee before: Wuxi Xingqu Power Technology Co.,Ltd.