CN115042560B - Automobile and electric drive transmission mechanism thereof - Google Patents

Automobile and electric drive transmission mechanism thereof Download PDF

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Publication number
CN115042560B
CN115042560B CN202210745318.7A CN202210745318A CN115042560B CN 115042560 B CN115042560 B CN 115042560B CN 202210745318 A CN202210745318 A CN 202210745318A CN 115042560 B CN115042560 B CN 115042560B
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CN
China
Prior art keywords
gear
planetary
sun gear
sun
sub
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CN202210745318.7A
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Chinese (zh)
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CN115042560A (en
Inventor
马飞龙
赵玉婷
于海生
孙峰
于闯
谭艳军
林霄喆
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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
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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 CN202210745318.7A priority Critical patent/CN115042560B/en
Publication of CN115042560A publication Critical patent/CN115042560A/en
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    • 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

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  • 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 annular gear, a first sun gear arranged in the first annular gear, a first planetary gear meshed with the first annular gear, a second planetary gear and a first planet carrier; the second planetary gear mechanism comprises a fixed second annular gear, a second sun gear arranged in the second annular gear and a second planet carrier; the third planetary gear mechanism comprises a fixed third annular gear, a third sun gear arranged in the third annular gear, a fourth planetary gear and a third planet carrier rotationally connected with the fourth planetary gear; the first half shaft is connected with the second planet carrier; the second half shaft is connected with the third planet carrier; 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:
the first planetary gear mechanism comprises a first annular gear, a first sun gear arranged in the first annular gear, a first planetary gear meshed with the first annular gear, a second planetary gear meshed with the first sun gear and the first planetary gear, and a first planet carrier rotationally connected with the first planetary gear and the second planetary gear;
the second planetary gear mechanism comprises a fixed second annular gear, a second sun gear arranged in the second annular gear, a third planetary gear meshed with the second annular gear and the second sun gear, and a second planet carrier rotationally connected with the third planetary gear;
the third planetary gear mechanism comprises a fixed third annular gear, a third sun gear arranged in the third annular gear, a fourth planetary gear meshed with the third annular gear and the third sun gear, and a third planet carrier rotationally connected with the fourth planetary gear;
the first half shaft is connected with the second planet carrier and is coaxially arranged with the second sun gear; and
the second half shaft is connected with the third planet carrier and is coaxially arranged with the third sun gear;
the first sun gear is in transmission connection with the second sun gear, and the first planet carrier is in transmission connection with the third sun gear.
In an exemplary embodiment, the first planetary gear mechanism is disposed between the second planetary gear mechanism and the third planetary gear mechanism, and the electrically driven transmission further includes
The two ends of the first rotating shaft are respectively connected with the first sun gear and the second sun gear; and
the two ends of the second rotating shaft are respectively connected with the first planet carrier and the third sun gear;
the first sun gear, the second sun gear, the third sun gear, the first annular gear, the second annular gear, the third annular gear, the first rotating shaft, the second rotating shaft, the first half shaft and the second half shaft are coaxially arranged, and the axes of the first planet gear, the second planet gear, the third planet gear and the fourth planet gear are parallel to the axis of the first sun gear.
In an exemplary 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, the electric drive transmission further includes a motor for driving the first ring gear to rotate.
In an exemplary embodiment, the motor includes a rotor configured as a ring-shaped structure that is fitted over the first ring gear and is rotatable about its own axis.
In one exemplary embodiment, the number of teeth of the first ring gear is twice the number of teeth of the first sun gear.
In an exemplary embodiment, a plurality of the first planetary gears and the second planetary gears are provided, and the plurality of first planetary gears are respectively meshed with the plurality of second planetary gears;
the plurality of first planet gears are uniformly distributed in the circumferential direction of the first ring gear, and the plurality of second planet gears are uniformly distributed in the circumferential direction of the first sun gear.
In an exemplary embodiment, the third planetary gear and the fourth planetary gear are each provided with a plurality of;
the plurality of third planetary gears are uniformly distributed in the circumferential direction of the second sun gear, and the plurality of fourth planetary gears are uniformly distributed in the circumferential direction of the third sun gear.
In an exemplary embodiment, the third planetary gear includes a first sub gear engaged with the second ring gear and a second sub gear engaged with the second sun gear;
the first sub-gear and the second sub-gear are coaxial and connected with each other, and the pitch circle diameter of the first sub-gear is smaller than that of the second sub-gear;
the fourth planetary gear includes a third sub-gear engaged with the third ring gear and a fourth sub-gear engaged with the third sun gear;
the third sub-gear and the fourth sub-gear are coaxial and are connected with each other, and the pitch circle diameter of the third sub-gear is smaller than that of the fourth sub-gear.
The application also proposes an automobile comprising any one of the electrically driven transmission mechanisms as described above.
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.
When the first planetary gear mechanism divides the torque into two paths and inputs the two paths to the second planetary gear mechanism and the third planetary gear mechanism respectively, the second planetary gear mechanism and the third planetary gear mechanism only bear half of the total torque, the structural strength requirements of the second planetary gear mechanism and the third planetary gear mechanism are reduced, and the design of the second planetary gear mechanism and the third planetary gear mechanism can be more compact and light.
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 a first embodiment of the present application;
fig. 2 is a schematic structural diagram of an electric drive mechanism according to a second embodiment of the present application.
Detailed Description
Example 1
As shown in fig. 1, fig. 1 shows an electric drive mechanism 100 in the present embodiment. The electric drive transmission mechanism 100 includes a motor 8, a first planetary gear mechanism 1, a second planetary gear mechanism 2, a third planetary gear mechanism 3, a first rotation shaft 4, a second rotation shaft 5, a first half shaft 6, and a second half shaft 7.
The first planetary gear mechanism 1 is disposed between the second planetary gear mechanism 2 and the third planetary gear mechanism 3. The first planetary gear mechanism 1 includes a first ring gear 11, a first sun gear 12, a first planetary gear 14, a second planetary gear 15, and a first carrier 13. The second planetary gear mechanism 2 includes a second ring gear 21, a second sun gear 22, a third planetary gear 24, and a second carrier 23. The third planetary gear mechanism 3 includes a third ring gear 31, a third sun gear 32, a fourth planetary gear 34, and a third carrier 33.
The motor 8 includes a stator and a rotor 81, the rotor 81 being rotatable relative to the stator. The rotor 81 may be constructed in a circular ring-shaped structure, and the rotor 81 may be rotatable about its own axis.
The first ring gear 11 is configured in a ring shape, and has a plurality of teeth provided on an inner wall thereof. The first ring gear 11 is connected to the rotor 81 and is disposed coaxially with the rotor 81. In the present embodiment, the first ring gear 11 is disposed inside the rotor 81, and the outer edge of the first ring gear 11 is connected to the inner peripheral wall of the rotor 81. The rotor 81 of the motor 8 can drive the first ring gear 11 to rotate.
The second ring gear 21 and the third ring gear 31 are each configured in a ring shape. A plurality of teeth are provided on the inner walls of the second ring gear 21 and the third ring gear 31. The second ring gear 21, the third ring gear 31, and the first ring gear 11 are coaxially disposed, and the second ring gear 21 and the third ring gear 31 are disposed on opposite sides of the first ring gear 11, respectively. The second ring gear 21 and the third ring gear 31 are each spaced apart from the first ring gear 11. Preferably, the distance between the second ring gear 21 and the first ring gear 11 is the same as the distance between the third ring gear 31 and the first ring gear 11. The second ring gear 21 and the third ring gear 31 are both fixedly arranged, and neither the second ring gear 21 nor the third ring gear 31 can move relative to the stator of the motor 8. The second ring gear 21 and the third ring gear 31 may be outer shells with outer edges connected to the electric drive mechanism 100, and the second ring gear 21 and the third ring gear 31 may also be mounting bases connected to the electric drive mechanism 100. The pitch diameters of the second ring gear 21 and the third ring gear 31 may be the same.
The first sun gear 12 is configured as a cylindrical gear. The first sun gear 12 is disposed within the first ring gear 11 and is coaxial with the first ring gear 11. An annular gap is formed between the outer peripheral wall of the first sun gear 12 and the inner peripheral wall of the first ring gear 11.
The first carrier 13 includes a first connection carrier 131, a first planetary shaft 132, and a second planetary shaft 133. The first coupling bracket 131 is provided at one side of the first sun gear 12. The first planetary shaft 132 and the second planetary shaft 133 are both connected to the first connecting frame 131. The first planetary shaft 132 and the second planetary shaft 133 are each parallel to the axial direction of the first sun gear 12. The first planetary shaft 132 and the second planetary shaft 133 each extend between the first sun gear 12 and the first ring gear 11. The first planetary shaft 132 is farther from the first sun gear 12 than the second planetary shaft 133. The first carrier 13 is constrained to rotate only about the axis of the first sun gear 12.
The first planetary gears 14 may be cylindrical gears. The first planetary gears 14 are sleeved on the first planetary shafts 132, and the axes of the first planetary gears 14 are parallel to the axes of the first sun gears 12. The first planetary gears 14 are rotatable about the axis of the first planetary shaft 132. The first planetary gears 14 are also meshed with the first ring gear 11.
The second planetary gear 15 may be a spur gear. The second planetary gear 15 is sleeved on the second planetary shaft 133, and the axis of the second planetary gear 15 is parallel to the axis of the first sun gear 12. The second planetary gears 15 are rotatable about the axis of the second planetary shafts 133. The second planetary gears 15 are meshed with the first sun gear 12, and the second planetary gears 15 are also meshed with the first planetary gears 14.
The first shaft 4 is configured in the shape of a straight bar. One end of the first shaft 4 is connected to the first sun gear 12.
The first shaft 4 and the first sun gear 12 may be keyed, such as flat keyed or splined.
The first shaft 4 is arranged coaxially with the first sun gear 12.
The second sun gear 22 is configured as a cylindrical gear. The second sun gear 22 is connected to the end of the first shaft 4 facing away from the first sun gear 12. The second sun gear 22 may be keyed, such as flat keyed or splined, to the first shaft 4. The second sun gear 22 is coaxially disposed with the first rotary shaft 4. The outer diameter of the second sun gear 22 is smaller than the inner diameter of the second ring gear 21, and the second sun gear 22 is located inside the second ring gear 21.
The second planet carrier 23 includes a second connection carrier 231 and a third planet axle 232. The second coupling frame 231 is arranged on the side of the second sun gear 22 facing away from the first rotation shaft 4. The third planetary shaft 232 is connected to the second coupling frame 231. The third planet axle 232 is parallel to the axis of the second sun gear 22. The third planetary shaft 232 extends between the second sun gear 22 and the second ring gear 21.
The third planetary gears 24 are configured as spur gears. The third planetary gear 24 is sleeved on the third planetary shaft 232 and can rotate around the third planetary shaft 232, and the axis of the third planetary gear 24 is parallel to the axis of the second sun gear 22. The third planetary gears 24 are meshed with the second ring gear 21 and the second sun gear 22.
The first half shaft 6 is configured in a straight strip shape. The first half shaft 6 is arranged on the side of the second planet carrier 23 facing away from the first sun gear 12. One end of the first half shaft 6 is connected to a second connection portion of the second carrier 23. The first half shaft 6 is arranged coaxially with the second sun gear 22.
The second rotation shaft 5 is configured in a straight bar shape. The second rotation shaft 5 is arranged at a side of the first connection part of the first planet carrier 13 facing away from the first sun gear. One end of the second rotating shaft 5 is connected to a first connection portion of the first planet carrier 13. The second rotation shaft 5 is disposed coaxially with the first sun gear 12. The second rotation shaft 5 is constrained to rotate only about its own axis.
The third sun gear 32 is configured as a cylindrical gear. The third sun gear 32 is connected to an end of the second rotation shaft 5 facing away from the first planet carrier 13. The third sun gear 32 may be keyed, such as flat keyed or splined, to the second shaft 5. The third sun gear 32 is coaxially disposed with the second rotating shaft 5. The outer diameter of the third sun gear 32 is smaller than the inner diameter of the third ring gear 31, and the third sun gear 32 is located inside the third ring gear 31.
The third carrier 33 includes a third connection carrier 331 and a fourth planetary shaft 332. The third connecting frame 331 is disposed on a side of the third sun gear 32 facing away from the second rotating shaft 5. The fourth planetary shaft 332 is connected to the third connection carrier 331. The fourth planet axle 332 is parallel to the axis of the third sun gear 32. The fourth planetary shaft 332 extends between the third sun gear 32 and the third ring gear 31.
The fourth planetary gear 34 is configured as a spur gear. The fourth planetary gear 34 is sleeved on the fourth planetary shaft 332, and can rotate around the fourth planetary shaft 332, and the axis of the fourth planetary gear 34 is parallel to the axis of the third sun gear 32. The fourth planetary gears 34 are engaged with the third ring gear 31 and the third sun gear 32.
The second half shaft 7 is configured in the shape of a straight bar. The second half shaft 7 is arranged on the side of the third planet carrier 33 facing away from the first sun gear 12. One end of the second half shaft 7 is connected to a third connection of the third planet carrier 33. The second half shaft 7 is arranged coaxially with the third sun gear 32.
In this embodiment, when the motor 8 drives the first ring gear 11 to rotate, torque is input from the first ring gear 11 of the electric drive transmission mechanism 100 to the electric drive transmission mechanism 100, and then the electric drive transmission mechanism 100 is output through the first half shaft 6 and the second half shaft 7. The first half shaft 6 and the second half shaft 7 can be respectively connected with two wheels in an external mode, and thus the first half shaft 6 and the second half shaft 7 can respectively drive the two wheels to rotate.
The path of torque transfer from the first ring gear 11 to the first half shaft 6 is: from the first ring gear 11 to the first planet gears 14, from the first planet gears 14 to the second planet gears 15, from the second planet gears 15 to the first sun gear 12, from the first sun gear 12 to the second sun gear 22, from the second sun gear 22 to the third planet gears 24, from the third planet gears 24 to the second planet carrier 23, and from the second planet carrier 23 to the first half shaft 6.
The torque is transferred from the first ring gear 11 to the second half shaft 7 by: from the first ring gear 11 to the first planet gears 14, from the first planet gears 14 to the second planet gears 15, and then through the first planet gears 14 and the second planet gears 15 acting together on the first planet carrier 13, from the first planet carrier 13 to the third sun gear 32, from the third sun gear 32 to the fourth planet gears 34, from the fourth planet gears 34 to the third planet carrier 33, and from the third planet carrier 33 to the second half shaft 7.
When the automobile runs on a flat road surface and runs along a straight line, the first half shaft 6 and the second half shaft 7 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 an uneven road or turns, the first half shaft 6 and the second half shaft 7 can respectively drive the two wheels to rotate at different rotating speeds so as to ensure that the two wheels do pure rolling motion on the ground.
At the same time, the torque is reduced and increased during the input from the motor 8 to the first planetary gear mechanism 1 and the transmission to the first half shaft 6 and the second half shaft 7 through the second planetary gear mechanism 2 and the third planetary gear mechanism 3, respectively, so that the transmission ratio of the electric drive transmission mechanism 100 is large.
In summary, the electric drive mechanism 100 can simultaneously realize speed change and differential functions, thereby reducing the volume and mass of the transmission components and greatly improving 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. When the first planetary gear mechanism 1 divides the torque into two paths and inputs the two paths to the second planetary gear mechanism 2 and the third planetary gear mechanism 3 respectively, the second planetary gear mechanism 2 and the third planetary gear mechanism 3 bear only half of the total torque, the structural strength requirements of the second planetary gear mechanism 2 and the third planetary gear mechanism 3 are reduced, and the design of the second planetary gear mechanism 2 and the third planetary gear mechanism 3 can be more compact and light.
In the present embodiment, the first planetary gear mechanism 1, the second planetary gear mechanism 2, the third planetary gear mechanism 3, the first rotating shaft 4, the second rotating shaft 5, the first half shaft 6, the second half shaft 7, and the rotor 81 of the motor 8 are configured as coaxial mechanisms, and the electric drive transmission mechanism 100 is symmetrically arranged about the axis of the first rotating shaft 4 as a whole, so that the structure of the electric drive transmission mechanism 100 is more compact.
The first sun gear 12, the second sun gear 22, the third sun gear 32, the first planetary gears 14, the second planetary gears 15, the third planetary gears 24 and the fourth planetary gears 34 are all cylindrical gears, and the axes are parallel to each other, so that the transmission efficiency of the electric drive mechanism 100 is greater than that of the conventional parallel shaft plus bevel gear differential.
In one exemplary embodiment, the number of teeth of the first ring gear 11 is twice the number of teeth of the first sun gear 12.
When the number of teeth of the first ring gear 11 is twice that of the first sun gear 12, the torque output by the first half shaft 6 and the second half shaft 7 is equal and the rotation speeds of the first half shaft 6 and the second half shaft 7 are the same when the automobile runs on a flat road surface and runs in a straight line.
In one exemplary embodiment, the first planetary gears 14, the second planetary gears 15, the first planetary shafts 132 and the second planetary shafts 133 are all provided in plurality and the same number. The number of the first planetary gears 14, the second planetary gears 15, the first planetary shafts 132, and the second planetary shafts 133 is preferably 3 or more. The plurality of first planetary gears 14 are respectively sleeved on the plurality of first planetary shafts 132. The plurality of second planetary gears 15 are respectively sleeved on the plurality of second planetary shafts 133. The plurality of first planetary gears 14 are respectively meshed with the plurality of second planetary gears 15.
The plurality of first planetary gears 14 are uniformly distributed in the circumferential direction of the first ring gear 11. The plurality of second planetary gears 15 are uniformly distributed in the circumferential direction of the first sun gear 12.
In this way, the stress of the first ring gear 11 and the first sun gear 12 is more uniform.
In the first exemplary embodiment, the third planetary gear 24, the fourth planetary gear 34, the third planetary shaft 232, and the fourth planetary shaft 332 are each provided in plurality. The number of the third planetary gears 24, the fourth planetary gears 34, the third planetary shafts 232, and the fourth planetary shafts 332 is preferably 3 or more.
The third planetary gears 24 and the third planetary shafts 232 are the same in number, and the third planetary gears 24 are sleeved on the third planetary shafts 232 in a one-to-one correspondence. The plurality of third planetary gears 24 are uniformly distributed in the circumferential direction of the second sun gear 22.
The number of the fourth planetary gears 34 is the same as that of the fourth planetary shafts 332, and the fourth planetary gears 34 are sleeved on the first planetary shafts in a one-to-one correspondence. The plurality of fourth planetary gears 34 are uniformly distributed in the circumferential direction of the third sun gear 32.
In this way, the forces of the second ring gear 21, the second sun gear 22, the third ring gear 31, and the third sun gear 32 are more uniform.
Example two
The main difference between the electric drive mechanism 100a in the second embodiment and the electric drive mechanism 100 in the first embodiment is that the third planetary gear and the fourth planetary gear are different in structure, and for avoiding redundancy, only the part of the electric drive mechanism 100a in the second embodiment that is different from the electric drive mechanism 100 in the first embodiment will be described.
As shown in fig. 2, the third planetary gear 24a includes a first sub-gear 241a and a second sub-gear 242a. The first sub gear 241a and the second sub gear 242a are both sleeved on the third planetary shaft 232 and are both rotatable around the third planetary shaft 232. The first and second sub gears 241a and 242a are coaxially disposed, and one ends of the first and second sub gears 241a and 242a, which are close to each other, are connected to each other. The first sub gear 241a is engaged with the second ring gear 21, and the second sub gear 242a is engaged with the second sun gear 22. The third planetary gear 24a may be an integrally formed structure. The third planetary gear 24a may be a double gear. The pitch diameter of the first sub-gear 241a is smaller than the pitch diameter of the second sub-gear 242a.
The fourth planetary gear 34a includes a third sub-gear 341a and a fourth sub-gear 342a. The third sub-gear 341a and the fourth sub-gear 342a are both sleeved on the fourth planetary shaft 332, and are both rotatable about the fourth planetary shaft 332. The third sub-gear 341a and the fourth sub-gear 342a are coaxially disposed, and one ends of the third sub-gear 341a and the fourth sub-gear 342a, which are close to each other, are connected to each other. The third sub gear 341a is engaged with the third ring gear 31, and the fourth sub gear 342a is engaged with the third sun gear 32. The fourth planetary gear 34a may be an integrally formed structure. The fourth planetary gear 34a may be a double gear. The pitch diameter of the third sub-gear 341a is smaller than the pitch diameter of the fourth sub-gear 342a.
In this way, the second planetary gear mechanism 2a and the third planetary gear mechanism 3a can further decelerate and increase torque of the electric drive transmission mechanism, so that the transmission ratio of the electric drive transmission mechanism 100a is larger.
Example III
The embodiment also provides an automobile, which comprises the electric drive transmission mechanism in the first embodiment or the second embodiment.
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 (7)

1. An electrically driven transmission, comprising:
the first planetary gear mechanism comprises a first annular gear, a first sun gear arranged in the first annular gear, a first planetary gear meshed with the first annular gear, a second planetary gear meshed with the first sun gear and the first planetary gear, and a first planet carrier rotationally connected with the first planetary gear and the second planetary gear;
the second planetary gear mechanism comprises a fixed second annular gear, a second sun gear arranged in the second annular gear, a third planetary gear meshed with the second annular gear and the second sun gear, and a second planet carrier rotationally connected with the third planetary gear;
the third planetary gear mechanism comprises a fixed third annular gear, a third sun gear arranged in the third annular gear, a fourth planetary gear meshed with the third annular gear and the third sun gear, and a third planet carrier rotationally connected with the fourth planetary gear;
the first half shaft is connected with the second planet carrier and is coaxially arranged with the second sun gear; and
the second half shaft is connected with the third planet carrier and is coaxially arranged with the third sun gear;
the first planet carrier is in transmission connection with the third sun gear;
the first planetary gear mechanism is arranged between the second planetary gear mechanism and the third planetary gear mechanism, and the electric drive transmission mechanism further comprises
The two ends of the first rotating shaft are respectively connected with the first sun gear and the second sun gear; and
the two ends of the second rotating shaft are respectively connected with the first planet carrier and the third sun gear;
the first sun gear, the second sun gear, the third sun gear, the first annular gear, the second annular gear, the third annular gear, the first rotating shaft, the second rotating shaft, the first half shaft and the second half shaft are coaxially arranged, and the axes of the first planet gear, the second planet gear, the third planet gear and the fourth planet gear are parallel to the axis of the first sun gear;
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 the motor is used for driving the first annular gear to rotate.
2. The electric drive transmission according to claim 1, wherein the motor includes a rotor configured as a ring-shaped structure fitted over the first ring gear and rotatable about its own axis.
3. The electric drive mechanism of claim 1, wherein the number of teeth of the first ring gear is twice the number of teeth of the first sun gear.
4. The electric drive transmission according to claim 1, wherein a plurality of the first planetary gears and the second planetary gears are provided, and a plurality of the first planetary gears are respectively meshed with a plurality of the second planetary gears;
the plurality of first planet gears are uniformly distributed in the circumferential direction of the first ring gear, and the plurality of second planet gears are uniformly distributed in the circumferential direction of the first sun gear.
5. The electric drive transmission of claim 1, wherein the third planetary gear and the fourth planetary gear are each provided with a plurality of;
the plurality of third planetary gears are uniformly distributed in the circumferential direction of the second sun gear, and the plurality of fourth planetary gears are uniformly distributed in the circumferential direction of the third sun gear.
6. The electric drive transmission of claim 1, wherein the third planetary gear includes a first sub-gear meshed with the second ring gear and a second sub-gear meshed with the second sun gear;
the first sub-gear and the second sub-gear are coaxial and connected with each other, and the pitch circle diameter of the first sub-gear is smaller than that of the second sub-gear;
the fourth planetary gear includes a third sub-gear engaged with the third ring gear and a fourth sub-gear engaged with the third sun gear;
the third sub-gear and the fourth sub-gear are coaxial and are connected with each other, and the pitch circle diameter of the third sub-gear is smaller than that of the fourth sub-gear.
7. An automobile comprising an electrically driven transmission mechanism according to any one of claims 1 to 6.
CN202210745318.7A 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof Active CN115042560B (en)

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CN115071337B (en) * 2022-06-27 2024-04-05 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
WO2024139571A1 (en) * 2022-12-26 2024-07-04 无锡星驱动力科技有限公司 Vehicle and double-motor electric drive assembly thereof

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