CN115042560A - Automobile and electric drive transmission mechanism thereof - Google Patents

Automobile and electric drive transmission mechanism thereof Download PDF

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Publication number
CN115042560A
CN115042560A CN202210745318.7A CN202210745318A CN115042560A CN 115042560 A CN115042560 A CN 115042560A CN 202210745318 A CN202210745318 A CN 202210745318A CN 115042560 A CN115042560 A CN 115042560A
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CN
China
Prior art keywords
gear
planetary
sun gear
ring
gears
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Granted
Application number
CN202210745318.7A
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Chinese (zh)
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CN115042560B (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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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 planetary gear mechanism, a second planetary gear mechanism and a first planet carrier, wherein the first planetary gear mechanism comprises a first inner gear ring, a first sun gear arranged in the first inner gear ring, and a first planet gear, a second planet gear and a first planet carrier which are meshed with the first inner gear ring; the second planetary gear mechanism comprises a fixed second inner gear ring, a second sun gear arranged in the second inner gear ring and a second planet carrier; the third planetary gear mechanism comprises a fixed third inner gear ring, a third sun gear arranged in the third inner gear ring, a fourth planetary gear and a third planet carrier which is in rotary connection with the fourth planetary gear; a first half shaft connected to the second carrier; and a second half shaft connected to the third carrier; the electric drive transmission mechanism can realize speed change and differential functions at the same time, reduces the volume and the mass of a transmission part, and greatly improves the power density of the transmission.

Description

Automobile and electric drive transmission mechanism thereof
Technical Field
The present invention relates to the field of automobiles, particularly to an automobile and an electric drive transmission mechanism thereof.
Background
At present, with the development of the new energy automobile industry, electric automobiles become a development trend. Because the electric vehicle needs a larger battery to increase the endurance mileage, the quality of the pure electric vehicles sold in the current market is far higher than that of the traditional fuel oil vehicles. Under the trend that the sales volume of pure electric vehicles is increasing day by day, the lightweight development of electric vehicles is imperative, and the requirement for reducing weight of each part in the automobile is higher and higher.
The design of current electric motor car derailleur is mostly parallel shaft overall arrangement, uses traditional bevel gear differential mechanism to carry out power take off simultaneously. The design scheme occupies a large volume and has a heavy weight.
Disclosure of Invention
In order to solve the above technical problem, the present application provides an electrically driven transmission mechanism, which includes:
the first planetary gear mechanism comprises a first inner gear ring, a first sun gear arranged in the first inner gear ring, first planetary gears meshed with the first inner gear ring, second planetary gears meshed with the first sun gear and the first planetary gears, and a first planet carrier rotationally connected with the first planetary gears and the second planetary gears;
the second planetary gear mechanism comprises a fixed second inner gear ring, a second sun gear arranged in the second inner gear ring, a third planetary gear meshed with the second inner gear ring and the second sun gear and a second planet carrier in rotary connection with the third planetary gear;
the third planetary gear mechanism comprises a fixed third ring gear, a third sun gear arranged in the third ring gear, a fourth planetary gear meshed with the third ring gear and the third sun gear and a third planet carrier in rotary connection with the fourth planetary gear;
the first half shaft is connected to the second planet carrier and is coaxially arranged with the second sun gear; and
a second half shaft connected to the third carrier and disposed coaxially with the third sun gear;
wherein the first sun gear is in driving connection with the second sun gear, and the first planet carrier is in driving connection with the third sun gear.
In an exemplary embodiment, the first planetary gear set is disposed between the second planetary gear set and the third planetary gear set, 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
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 inner gear ring, the second inner gear ring, the third inner gear ring, 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 planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear are all 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 gears, the second planet gears, the third planet gears and the fourth planet gears 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 circular ring structure sleeved on the first ring gear and capable of rotating around its 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, each of the first planetary gears and the second planetary gears is provided in plurality, and the first planetary gears are respectively meshed with 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.
In one exemplary embodiment, each of the third planetary gear and the fourth planetary gear is provided in plurality;
the plurality of third planetary gears are evenly distributed in the circumferential direction of the second sun gear, and the plurality of fourth planetary gears are evenly distributed in the circumferential direction of the third sun gear.
In an exemplary embodiment, the third planetary gears include 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 are 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 meshed with the third ring gear and a fourth sub gear meshed with the third sun gear;
the third sub gear and the fourth sub gear are coaxial and connected with each other, and the pitch circle diameter of the third sub gear is smaller than that of the fourth sub gear.
The present application also proposes a motor vehicle comprising any of the electric drive transmissions as described above.
The electric drive transmission mechanism can realize speed change and differential functions at the same time, reduces the volume and the mass of a transmission part, and greatly improves the power density of the transmission. Compared with the traditional differential with parallel shafts and bevel gears, the differential reduces the number of required parts, and has more compact structure and lighter weight.
When the first planetary gear mechanism divides the torque into two paths to be respectively input to the second planetary gear mechanism and the third planetary gear mechanism, 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 second planetary gear mechanism and the third planetary gear mechanism can be designed to be more compact and lighter.
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 may be realized and attained by the instrumentalities and combinations particularly pointed out in the specification and the drawings.
Drawings
The drawings are intended to provide an understanding of the present disclosure, and are to be considered as forming a part of the specification, and are to be used together with the embodiments of the present disclosure to explain the present disclosure without limiting the present disclosure.
Fig. 1 is a schematic structural diagram of an electric drive transmission mechanism according to a first embodiment of the present application;
fig. 2 is a schematic structural diagram of an electric drive transmission mechanism according to a second embodiment of the present application.
Detailed Description
Example one
Referring to fig. 1, fig. 1 illustrates an electric drive transmission 100 of the present embodiment. The electric drive transmission 100 includes an electric motor 8, a first planetary gear mechanism 1, a second planetary gear mechanism 2, a third planetary gear mechanism 3, a first rotating shaft 4, a second rotating 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, first planetary gears 14, second planetary gears 15, and a first carrier 13. The second planetary gear mechanism 2 includes a second ring gear 21, a second sun gear 22, third planetary gears 24, and a second carrier 23. The third planetary gear mechanism 3 includes a third ring gear 31, a third sun gear 32, fourth planetary gears 34, and a third carrier 33.
The motor 8 includes a stator and a rotor 81, and the rotor 81 is rotatable with respect to the stator. The rotor 81 may be configured as a circular ring structure, and the rotor 81 can rotate around its axis.
The first ring gear 11 is configured in a ring shape, and a plurality of teeth are 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 circumferential 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 circular 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 arranged, and the second ring gear 21 and the third ring gear 31 are respectively arranged on two opposite sides of the first ring gear 11. The second ring gear 21 and the third ring gear 31 are both 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 disposed, and neither the second ring gear 21 nor the third ring gear 31 is movable relative to the stator of the motor 8. The second ring gear 21 and the third ring gear 31 may be outer casings connected to the electric drive transmission mechanism 100 at outer edges thereof, and the second ring gear 21 and the third ring gear 31 may also be mounting bases connected to the electric drive transmission mechanism 100. The pitch circle diameters of the second ring gear 21 and the third ring gear 31 may be the same.
The first sun gear 12 is designed as a spur 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 connecting carrier 131, a first planetary shaft 132, and a second planetary shaft 133. The first link frame 131 is disposed at one side of the first sun gear 12. The first and second planet shafts 132 and 133 are connected to the first connecting carrier 131. The first and second planetary shafts 132 and 133 are parallel to the axial direction of the first sun gear 12. The first and second planetary shafts 132 and 133 each extend between the first sun gear 12 and the first ring gear 11. The first planet shaft 132 is farther from the first sun gear 12 than the second planet 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 gear 14 is sleeved on the first planetary shaft 132, and the axis of the first planetary gear 14 is parallel to the axis of the first sun gear 12. The first planetary gears 14 are rotatable about the axis of the first planetary shaft 132. The first planetary gears 14 are also engaged with the first ring gear 11.
The second planetary gears 15 may be cylindrical gears. The second planet gears 15 are sleeved on the second planet shafts 133, and the axes of the second planet gears 15 are parallel to the axis of the first sun gear 12. The second planetary gears 15 can rotate about the axis of the second planetary shaft 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 rotation shaft 4 is configured as a straight bar. One end of the first rotation 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 a flat key or a spline connection.
The first rotation shaft 4 is disposed 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 a flat key or a splined connection, to the first shaft 4. The second sun gear 22 is disposed coaxially 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 carrier 23 includes a second link 231 and a third planet shaft 232. The second connecting frame 231 is arranged on the side of the second sun gear 22 facing away from the first rotation axis 4. The third planetary shaft 232 is connected to the second connection frame 231. The third planetary shaft 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 designed 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 engaged with the second ring gear 21 and the second sun gear 22.
The first half shaft 6 is configured as a straight bar. 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 the second connecting portion of the second carrier 23. The first half shaft 6 is disposed coaxially with the second sun gear 22.
The second rotary shaft 5 is configured as a straight bar. The second rotating shaft 5 is arranged on the side of the first connecting part of the first planet carrier 13, which is far away from the first sun gear. One end of the second rotating shaft 5 is connected to the first connecting portion of the first carrier 13. The second rotary shaft 5 is disposed coaxially with the first sun gear 12. The second shaft 5 is constrained to rotate only about its own axis.
The third sun gear 32 is designed as a spur gear. The third sun gear 32 is connected to the end of the second shaft 5 facing away from the first planet carrier 13. The third sun gear 32 and the second rotating shaft 5 may be in a keyed connection, such as a flat key connection or a spline connection. 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 connecting 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 connecting frame 331. The fourth planetary shaft 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 gears 34 are designed as spur gears. The fourth planetary gears 34 are sleeved on the fourth planetary shafts 332 and can rotate around the fourth planetary shafts 332, and the axes of the fourth planetary gears 34 are 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 of straight-bar configuration. The second axle 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 connecting portion of the third carrier 33. The second axle shaft 7 is arranged coaxially with the third sun gear 32.
In the present embodiment, when the motor 8 drives the first ring gear 11 to rotate, the torque is input into the electric drive transmission mechanism 100 from the first ring gear 11 of 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 may respectively circumscribe two wheels, such that the first half shaft 6 and the second half shaft 7 may respectively drive the two wheels to rotate.
The path for the torque transmitted 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, from the second planet carrier 23 to the first half shaft 6.
The path for the torque transfer from the first ring gear 11 to the second axle shaft 7 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, 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 axle shaft 7.
When the automobile runs on a flat road 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 moving linearly. 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.
Meanwhile, the torque is reduced and increased in the process of being input from the motor 8 to the first planetary gear mechanism 1 and being respectively transmitted 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, so that the transmission ratio of the electric drive transmission mechanism 100 is large.
In conclusion, the electrically-driven transmission mechanism 100 can realize speed change and differential functions at the same time, reduce the volume and mass of transmission parts, and greatly improve the power density of the transmission. Compared with the traditional differential with parallel shafts and bevel gears, the differential reduces the number of required parts, and has more compact structure and lighter weight. When the first planetary gear mechanism 1 divides the torque into two paths and inputs the torque 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 only bear 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 lighter.
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 electric motor 8 are configured as coaxial mechanisms, and the electric drive transmission mechanism 100 is arranged symmetrically with respect to 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 planet gears 14, the second planet gears 15, the third planet gears 24, and the fourth planet gears 34 are all cylindrical gears with axes parallel to each other, so that the transmission efficiency of the electric drive transmission mechanism 100 is greater compared to a conventional parallel shaft bevel gear differential.
In an 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 inner gear ring 11 is twice that of the first sun gear 12, when the automobile runs on a flat road and runs along a straight line, the torque output by the first half shaft 6 is equal to that output by the second half shaft 7, and the rotating speeds of the first half shaft 6 and the second half shaft 7 are equal.
In an exemplary embodiment, the first planetary gear 14, the second planetary gear 15, the first planetary shaft 132 and the second planetary shaft 133 are all provided in plurality and in 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 each greater than or equal to 3. The first planetary gears 14 are respectively sleeved on the 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 engaged with the plurality of second planetary gears 15, respectively.
The plurality of first planetary gears 14 are evenly distributed in the circumferential direction of the first ring gear 11. The plurality of second planetary gears 15 are evenly distributed in the circumferential direction of the first sun gear 12.
Thus, the first ring gear 11 and the first sun gear 12 are more uniformly stressed.
In the first exemplary embodiment, a plurality of third planetary gears 24, fourth planetary gears 34, third planetary shafts 232, and fourth planetary shafts 332 are provided. 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 number of the third planetary gears 24 is the same as that of the third planetary shafts 232, and the third planetary gears 24 are sleeved on the third planetary shafts 232 in a one-to-one correspondence manner. The plurality of third planetary gears 24 are evenly 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 second search planetary shafts in a one-to-one correspondence manner. The plurality of fourth planetary gears 34 are evenly distributed in the circumferential direction of the third sun gear 32.
In this way, the forces applied to 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 electric drive transmission mechanism 100a of the second embodiment is different from the electric drive transmission mechanism 100 of the first embodiment in the third planetary gear and the fourth planetary gear, and for avoiding redundancy, only the part of the electric drive transmission mechanism 100a of the second embodiment that is different from the electric drive transmission mechanism 100 of the first embodiment will be described below.
As shown in fig. 2, the third planetary gears 24a include a first sub gear 241a and a second sub gear 242 a. The first sub gear 241a and the second sub gear 242a are both sleeved on the third planetary shaft 232 and both can rotate around the third planetary shaft 232. The first sub gear 241a and the second sub gear 242a are coaxially disposed, and one ends of the first sub gear 241a and the second sub gear 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 gears 24a may be of unitary construction. The third planetary gears 24a may be dual gears. The pitch circle diameter of the first sub gear 241a is smaller than that of the second sub gear 242 a.
The fourth planetary gear 34a includes a third sub gear 341a and a fourth sub gear 342 a. The third sub gear 341a and the fourth sub gear 342a are both sleeved on the fourth planet shaft 332 and can rotate around the fourth planet 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 gears 34a may be an integrally formed structure. The fourth planetary gears 34a may be double gears. The pitch circle diameter of the third sub gear 341a is smaller than that of the fourth sub gear 342 a.
In this way, the second planetary gear mechanism 2a and the third planetary gear mechanism 3a can further reduce the speed and increase the torque of the electrically driven transmission mechanism, so that the transmission ratio of the electrically driven transmission mechanism 100a is larger.
EXAMPLE III
The present embodiment also provides a vehicle including the electric drive transmission mechanism according to the first embodiment or the second embodiment.
The present application describes embodiments, but the description is illustrative rather than 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 instead of any other feature or element in any other embodiment, unless expressly limited otherwise.
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 disclosed in this application may also be combined with any conventional features or elements to form a unique inventive concept as defined by the claims. Any feature or element of any embodiment may also be combined with features or elements from other inventive aspects to form yet another unique inventive aspect, as defined by 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. Furthermore, various modifications and changes may be made within the scope of the appended claims.
Further, 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 orders of steps are possible as will be understood by those of ordinary skill in the art. Therefore, the particular order of the steps set forth in the specification should not be construed as limitations on the claims. Further, 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 (10)

1. An electrically driven transmission, comprising:
the first planetary gear mechanism comprises a first inner gear ring, a first sun gear arranged in the first inner gear ring, first planetary gears meshed with the first inner gear ring, second planetary gears meshed with the first sun gear and the first planetary gears, and a first planet carrier rotationally connected with the first planetary gears and the second planetary gears;
the second planetary gear mechanism comprises a fixed second inner gear ring, a second sun gear arranged in the second inner gear ring, a third planetary gear meshed with the second inner gear ring and the second sun gear and a second planet carrier in rotary connection with the third planetary gear;
the third planetary gear mechanism comprises a fixed third ring gear, a third sun gear arranged in the third ring gear, a fourth planetary gear meshed with the third ring gear and the third sun gear and a third planet carrier in rotary connection with the fourth planetary gear;
the first half shaft is connected to the second planet carrier and is coaxially arranged with the second sun gear; and
a second half shaft connected to the third carrier and disposed coaxially with the third sun gear;
wherein the first sun gear is in driving connection with the second sun gear, and the first planet carrier is in driving connection with the third sun gear.
2. The electrically driven transmission of claim 1, wherein the first planetary gear mechanism is disposed between a second planetary gear mechanism and the third planetary gear mechanism, the electrically driven transmission further comprising
The two ends of the first rotating shaft are respectively connected with the first sun gear and the second sun gear; and
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 inner gear ring, the second inner gear ring, the third inner gear ring, 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 planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear are all parallel to the axis of the first sun gear.
3. The electric drive transmission of claim 2, wherein the first sun gear, the second sun gear, the third sun gear, the first planet gears, the second planet gears, the third planet gears, and the fourth planet gears are each cylindrical gears.
4. An electric drive transmission according to any one of claims 1 to 3, further comprising an electric motor for driving the first annulus gear in rotation.
5. The electric drive transmission of claim 4, wherein the electric machine includes a rotor configured as a ring-shaped structure that fits over the first ring gear and is rotatable about its axis.
6. An electric drive transmission according to any of claims 1 to 3, wherein the number of teeth of the first annulus gear is twice the number of teeth of the first sun gear.
7. An electric drive transmission according to any of claims 1 to 3, wherein a plurality of the first planetary gears and the second planetary gears are provided, and the plurality of the first planetary gears are respectively meshed with the 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.
8. An electric drive transmission according to any 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 are evenly distributed in the circumferential direction of the second sun gear, and the plurality of fourth planetary gears are evenly distributed in the circumferential direction of the third sun gear.
9. An electric drive transmission according to any of claims 1 to 3, wherein the third planetary gear comprises 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 are 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 meshed with the third ring gear and a fourth sub gear meshed with the third sun gear;
the third sub gear and the fourth sub gear are coaxial and connected with each other, and the pitch circle diameter of the third sub gear is smaller than that of the fourth sub gear.
10. An automobile, characterised by comprising an electric drive transmission according to any one of claims 1 to 9.
CN202210745318.7A 2022-06-27 2022-06-27 Automobile and electric drive transmission mechanism thereof Active CN115042560B (en)

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