CN216951528U - Planet row type transmission and vehicle - Google Patents
Planet row type transmission and vehicle Download PDFInfo
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- CN216951528U CN216951528U CN202220383128.0U CN202220383128U CN216951528U CN 216951528 U CN216951528 U CN 216951528U CN 202220383128 U CN202220383128 U CN 202220383128U CN 216951528 U CN216951528 U CN 216951528U
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Abstract
The utility model discloses a planet row type transmission and a vehicle, wherein the planet row type transmission comprises a motor, a first planet row, a second planet row, a left half shaft and a right half shaft; the first planet row comprises a first sun gear, a first planet wheel, a first gear ring and a first planet carrier, the first sun gear is meshed with the first planet wheel, the first planet wheel is meshed with the first gear ring, and the first planet wheel is arranged on the first planet carrier; the second planet row comprises a second sun gear, a second planet gear, a second ring gear and a second planet carrier, the second sun gear is meshed with the second planet gear, the second planet gear is meshed with the second ring gear, and the second planet gear is arranged on the second planet carrier; the motor is in transmission connection with the first sun gear through a rotor shaft; the first planet carrier is in transmission connection with the second gear ring; the second planet row is connected with the left half shaft and the right half shaft to transmit the power of the motor. The technical scheme of the utility model provides a light-weight transmission.
Description
Technical Field
The utility model relates to the technical field of vehicles, in particular to a planetary transmission and a vehicle.
Background
At present, with the development of new energy vehicle industry, electric vehicles have become a development trend. Under the trend of increasing sales of electric vehicles, the development of light weight of the electric vehicles is imperative.
In order to ensure the endurance mileage of an electric vehicle, a large battery is generally provided in the electric vehicle to meet the endurance requirement. As such, there is an increasing demand for weight reduction of other components in the electric vehicle.
At present, the transmission of the electric vehicle adopts a parallel shaft type layout, and meanwhile, the traditional bevel gear differential is used for power output. However, this transmission has a problem of heavy weight.
SUMMERY OF THE UTILITY MODEL
The utility model mainly aims to provide a planetary gear-type transmission and aims to provide a light-weight planetary gear-type transmission.
In order to achieve the purpose, the planetary gear set type transmission provided by the utility model comprises a motor, a first planetary gear set, a second planetary gear set, a left half shaft and a right half shaft;
the first planet row comprises a first sun gear, a first planet gear, a first gear ring and a first planet carrier, the first sun gear is meshed with the first planet gear, the first planet gear is meshed with the first gear ring, and the first planet gear is mounted on the first planet carrier;
the second planet row comprises a second sun gear, a second planet gear, a second ring gear and a second planet carrier, the second sun gear is meshed with the second planet gear, the second planet gear is meshed with the second ring gear, and the second planet gear is mounted on the second planet carrier;
the motor is in transmission connection with the first sun gear through a rotor shaft;
the first planet carrier is in transmission connection with the second gear ring;
the second planet row is connected with the left half shaft and the right half shaft to transmit the power of the motor.
Optionally, the second sun gear is connected to the left half shaft, and the second planet carrier is connected to the right half shaft.
Optionally, the second sun gear is connected to the right half shaft, and the second planet carrier is connected to the left half shaft.
Optionally, the first ring gear is located outboard of the first planet carrier, remote from the first sun gear, and fixed relative to a stationary portion of the planetary transmission.
Optionally, the first planet gear includes a first planet gear and a second planet gear that are connected, the first planet gear is engaged with the first sun gear, and the second planet gear is engaged with the first ring gear.
Optionally, the first planet gear includes a first planet gear and a second planet gear that are connected, the first planet gear is engaged with the first ring gear, and the second planet gear is engaged with the first sun gear.
Optionally, the first planet gear includes a first planet gear and a second planet gear that are connected, the first ring gear is empty and sleeved outside the rotor shaft and is relatively fixed with the casing of the planetary gear-type transmission, the first ring gear is engaged with the first planet gear, and the first sun gear is engaged with the second planet gear.
Optionally, the second planet wheel includes a first second planet wheel and a second planet wheel, which are engaged with each other, both the first second planet wheel and the second planet wheel are mounted on the second planet carrier, the first second planet wheel is engaged with the second gear ring, and the second planet wheel is engaged with the second sun gear.
Optionally, the rotor shaft is a hollow shaft, and the left half shaft passes through the rotor shaft.
The utility model also provides a vehicle comprising the planetary transmission.
According to the technical scheme, the first planet row and the second planet row which are connected are arranged in the planet row type transmission, and the power of the motor is transmitted to the left half shaft and the right half shaft through the first planet row and the second planet row. So, on the one hand, compare in adopting parallel shaft and bevel gear's derailleur structure among the prior art, reduced the required part quantity of derailleur to make planet row formula derailleur's whole weight reduce, make planet row formula derailleur's quality lighter, and then be favorable to the lightweight of vehicle. On the other hand, compared with a transmission structure with a parallel shaft and a bevel gear in the prior art, the overall size of the planetary row type transmission is reduced, the occupied space of the planetary row type transmission is reduced, and the structure of the planetary row type transmission is more compact.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural diagram of an embodiment of a planetary transmission of the present invention;
FIG. 2 is a schematic illustration of another embodiment of a planetary transmission according to the present invention;
FIG. 3 is a schematic illustration of a planetary transmission according to another embodiment of the present invention;
FIG. 4 is a schematic structural diagram of yet another embodiment of a planetary transmission according to the present invention.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) |
| 10 | |
130 | |
| 11 | |
140 | |
| 20 | |
200 | |
| 30 | Right |
210 | |
| 100 | |
220 | |
| 110 | |
221 | Second planet wheel 1 |
| 120 | |
222 | Second planet wheel 2 |
| 121 | First planet wheel 1 | 230 | |
| 122 | First planet gear 2 | 240 | Second planet carrier |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that all the directional indicators (such as up, down, left, right, front, and rear … …) in the embodiment of the present invention are only used to explain the relative position relationship between the components, the movement situation, etc. in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indicator is changed accordingly.
In addition, the descriptions related to "first", "second", etc. in the present invention are for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, "and/or" in the whole text includes three schemes, taking a and/or B as an example, including a technical scheme, and a technical scheme that a and B meet simultaneously; in addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
At present, with the development of new energy vehicle industry, electric vehicles have become a development trend. Under the trend of increasing sales of electric vehicles, the development of light weight of the electric vehicles is imperative.
In order to ensure the endurance mileage of an electric vehicle, a large battery is generally provided in the electric vehicle to meet the endurance requirement. As such, there is an increasing demand for weight reduction of other components in the electric vehicle.
At present, the transmission of the electric vehicle adopts a parallel shaft type layout, and meanwhile, the traditional bevel gear differential is used for power output. However, this transmission has a problem of heavy weight.
In view of this, the present invention proposes a planetary transmission.
Referring to fig. 1 to 4, in the embodiment of the present invention, the planetary gear set transmission includes a motor 10, a first planetary gear set 100, a second planetary gear set 200, a left half shaft 20, and a right half shaft 30.
The first planetary row 100 includes a first sun gear 110, a first planet gear 120, a first ring gear 130, and a first carrier 140, the first sun gear 110 is engaged with the first planet gear 120, the first planet gear 120 is engaged with the first ring gear 130, and the first planet gear 120 is mounted on the first carrier 140. Specifically, the first sun gear 110 is located at the center of the first planetary row 100, the first planetary gears 120 are engaged with the outer ring of the first sun gear 110, and in the circumferential direction of the first sun gear 110, the first planetary gears 120 may be provided in multiple groups, where the number of groups of the first planetary gears 120 is not limited. The first planet gear 120 is fixed to a first planet carrier 140, and the first planet carrier 140 provides fixed support for the first planet gear 120. Meanwhile, the first planet gear 120 is also meshed with the inner ring of the first ring gear 130, that is, the first planet gear 120, the adjacent first sun gear 110 and the adjacent first ring gear 130 are in a constantly meshed state, so that transmission among the first planet gear 120, the adjacent first sun gear 110 and the adjacent first ring gear 130 is realized.
The second planet row 200 comprises a second sun gear 210, a second planet gear 220, a second ring gear 230 and a second planet carrier 240, the second sun gear 210 being in mesh with the second planet gear 220, the second planet gear 220 being in mesh with the second ring gear 230, the second planet gear 220 being mounted on the second planet carrier 240. Specifically, the second sun gear 210 is located at the center of the second planet row 200, the second planet gears 220 are meshed with the outer ring of the second sun gear 210, and in the circumferential direction of the second sun gear 210, a plurality of groups of the second planet gears 220 may be provided, where the number of the groups of the second planet gears 220 is not limited. The second planet gears 220 are fixed to a second planet carrier 240, and the second planet carrier 240 provides fixed support for the second planet gears 220. Meanwhile, the second planet gear 220 is also meshed with the inner ring of the second ring gear 230, that is, the second planet gear 220 and the adjacent second sun gear 210 and second ring gear 230 are in a constant meshed state, so that transmission among the three is realized.
The electric machine 10 is in driving connection with the first sun gear 110 via the rotor shaft 11. Specifically, the motor 10 is a power source of the planetary transmission, and power of the motor 10 is transmitted to the planetary transmission through the rotor shaft 11. The motor 10 is connected to the first sun gear 110 of the first planetary row 100, and in one embodiment, the rotor shaft 11 of the motor 10 is directly splined to the first sun gear 110. Of course, the rotor shaft 11 of the motor 10 may be splined to the high-speed shaft, which is in turn splined to the first sun gear 110. The connection of the motor 10 and the first sun gear 110 realizes the transmission of the power of the motor 10 to the first planetary gear set 100.
The first carrier 140 is drivingly connected to the second ring gear 230. Specifically, the first planetary row 100 and the second planetary row 200 are in transmission connection through the first planet carrier 140 and the second ring gear 230, so that the power of the motor 10 can be transmitted to the second planetary row 200 through the first planetary row 100.
The second planetary row 200 is connected with the left and right half shafts 20 and 30 to transmit the power of the motor 10. Specifically, the half shafts are used to transmit power between the planetary differential and the drive wheels. The left half shaft 20 serves to transmit power of the motor 10 to a left wheel of the vehicle, and the right half shaft 30 serves to transmit power of the motor 10 to a right wheel of the vehicle. That is, the left half shaft 20 and the right half shaft 30 are power output shafts of the planetary gear transmission. The left half shaft 20 and the right half shaft 30 are both connected with the second planetary row 200, and the power of the motor 10 is transmitted to the left half shaft 20 and the right half shaft 30 through the first planetary row 100 and the second planetary row 200, so that the driving of the vehicle wheels is realized.
So, through set up the first planet row 100 and the second planet row 200 that are connected in the planet row formula derailleur, on the one hand, compare in the derailleur structure that adopts parallel shaft plus bevel gear among the prior art, reduced the required part quantity of derailleur to make the whole weight reduction of planet row formula derailleur, make the quality of planet row formula derailleur lighter, and then be favorable to the lightweight of vehicle. On the other hand, compared with a transmission structure with a parallel shaft and a bevel gear in the prior art, the overall size of the planetary transmission is reduced, the occupied space of the planetary transmission is reduced, and the structure of the planetary transmission is more compact.
According to the technical scheme, the first planetary row 100 and the second planetary row 200 which are connected are arranged in the planetary row type transmission, and the power of the motor 10 is transmitted to the left half shaft 20 and the right half shaft 30 through the first planetary row 100 and the second planetary row 200. So, on the one hand, compare in the derailleur structure that adopts parallel shaft plus bevel gear among the prior art, reduced the required part quantity of derailleur to make planet row formula derailleur's whole weight reduce, make planet row formula derailleur's quality lighter, and then be favorable to the lightweight of vehicle. On the other hand, compared with a transmission structure with a parallel shaft and a bevel gear in the prior art, the overall size of the planetary row type transmission is reduced, the occupied space of the planetary row type transmission is reduced, and the structure of the planetary row type transmission is more compact.
Further, the second sun gear 210 is connected to the left half shaft 20, and the second carrier 240 is connected to the right half shaft 30. Specifically, the second sun gear 210 is connected to the left half shaft 20, that is, the power of the motor 10 is transmitted to the left half shaft 20 through the second sun gear 210, so as to drive the left wheel; the second planet carrier 240 is connected to the right axle shaft 30, that is, the power of the motor 10 is transmitted to the right axle shaft 30 through the second planet carrier 240, thereby driving the right wheels. In this way, the second planetary row 200 functions as a differential by connecting the second sun gear 210 and the second carrier 240 to the left half shaft 20 and the right half shaft 30, respectively. On one hand, the output speed ratios of the two ends of the left half shaft 20 and the right half shaft 30 are equal through the combination of the second row of planet gears; on the other hand, the vehicle is caused to perform differential travel in the steering situation, as in the case of a conventional bevel gear differential.
Further, the second sun gear 210 is connected to the right half shaft 30, and the second carrier 240 is connected to the left half shaft 20. Specifically, the second sun gear 210 is connected to the right axle shaft 30, that is, the power of the motor 10 is transmitted to the right axle shaft 30 through the second sun gear 210, so as to drive the right wheels; the second planet carrier 240 is connected to the left half shaft 20, i.e. the power of the motor 10 is transmitted to the left half shaft 20 through the second planet carrier 240, thereby driving the left wheels. In this way, the second planet carrier 240 and the second sun gear 210 are connected to the right half shaft 30 and the left half shaft 20, respectively, so that the second planet row 200 performs the function of a differential. On one hand, the output speed ratios of the two ends of the left half shaft 20 and the right half shaft 30 are equal through the combination of the second row of planet gears; on the other hand, the vehicle is caused to perform differential travel in the steering situation, as in the case of a conventional bevel gear differential.
Further, the first ring gear 130 is located on the outer side of the first planetary row 100 away from the first sun gear 110 and is fixed relative to the stationary portion of the planetary transmission. Specifically, the first sun gear 110 is located at the middle of the first planetary row 100, and the first ring gear 130 is located on the outer side of the first planetary row 100 away from the first sun gear 110 in the radial direction of the first sun gear 110. That is, in the radial direction of the first sun gear 110, the first planet gear 120, and the first ring gear 130 are sequentially engaged with each other, so that transmission among the three is realized. Meanwhile, the first ring gear 130 is a brake, and the first ring gear 130 is relatively fixedly connected with a stationary part of the planetary transmission. The stationary part of the planetary transmission refers to stationary parts in the planetary transmission, such as a housing, a motor stator, a brake hub and the like of the planetary transmission. More specifically, the first ring gear 130 may be connected with the housing of the planetary transmission through splines, or may be connected with the housing through rectangular teeth.
Further, the first planet 120 includes a first planet 121 and a second planet 122 connected, the first planet 121 is engaged with the first sun gear 110, and the second planet 122 is engaged with the first ring gear 130. Specifically, the first planetary row 100 is an NW-type planetary gear structure. The first planet gear 120 is fixed to the first planet carrier 140 by a first planet gear shaft, the first planet gear shaft is perpendicular to the circumferential direction of the first sun gear 110, a first planet gear 121 and a first planet gear 122 are mounted on the first planet gear shaft, and the first planet gear 121 and the first planet gear 122 are in interference fit into a double planet gear through a shrink fit. The second first planet gear 122 is located on the side of the first planet gear 121 remote from the electric machine 10, the first planet gear 121 meshes with the first sun gear 110, and the second first planet gear 122 meshes with the first ring gear 130. In this way, the power of the motor 10 is sequentially transmitted to the second planetary gear set 200 through the first sun gear 110, the first planetary gear set 121, the second planetary gear set 122, and the first carrier 140, thereby realizing the transmission of the power of the motor 10 in the first planetary gear set 100. In this way, the speed reduction function of the planetary transmission is realized through the arrangement of the first planetary row 100, and the power of the motor 10 can realize the functions of speed reduction and torque increase after being transmitted through the first planetary row 100. The arrangement of the first planet gear 121 and the second planet gear 122 which are connected with each other improves the speed ratio of the planetary gear transmission, and enlarges the speed ratio range, so that the rotating speed range of the motor 10 can be larger, and different design requirements can be met.
Further, the first planet 120 includes a first planet 121 and a second planet 122 connected, the first planet 121 is engaged with the first ring gear 130, and the second planet 122 is engaged with the first sun gear 110. Specifically, the first planetary row 100 is an NW-type planetary gear structure. The first planet gear 120 is fixed to the first planet carrier 140 by a first planet gear shaft, the first planet gear shaft is perpendicular to the circumferential direction of the first sun gear 110, a first planet gear 121 and a first planet gear 122 are mounted on the first planet gear shaft, and the first planet gear 121 and the first planet gear 122 are in interference fit into a double planet gear through a shrink fit. The second first planet gear 122 is located on the side of the first planet gear 121 away from the electric machine 10, the first planet gear 121 is engaged with the first ring gear 130, and the second first planet gear 122 is engaged with the first sun gear 110. In this way, the power of the motor 10 is sequentially transmitted to the second planetary gear set 200 through the first sun gear 110, the second planetary gear 122, and the first carrier 140, thereby realizing the transmission of the power of the motor 10 in the first planetary gear set 100. In this way, the speed reduction function of the planetary transmission is realized through the arrangement of the first planetary row 100, and the power of the motor 10 can realize the functions of speed reduction and torque increase after being transmitted through the first planetary row 100. The first planetary row 100 improves the speed ratio of the planetary-row transmission and expands the speed ratio range, so that the range of the rotating speed of the motor 10 can be larger, and different design requirements can be met.
Further, the first planetary gear 120 includes a first planetary gear 121 and a second planetary gear 122 connected to each other, the first ring gear 130 is freely sleeved outside the rotor shaft 11 and fixed relative to the housing of the planetary transmission, the first ring gear 130 is engaged with the first planetary gear 121, and the first sun gear 110 is engaged with the second planetary gear 122. Specifically, the first planetary row 100 is an NW-type planetary gear structure. The first planet gear 120 is fixed to the first planet carrier 140 through a first planet gear shaft, the first planet gear shaft is perpendicular to the circumferential direction of the first sun gear 110, a first planet gear 121 and a first planet gear 122 are mounted on the first planet gear shaft, the first planet gear 121 and the first planet gear 122 form a duplex planet gear through shrink fit, and the first planet gear 122 is located on the side, away from the motor 10, of the first planet gear 121. The first ring gear 130 is mounted to the outside of the rotor shaft 11 via a needle bearing hollow and is rotatable circumferentially on the rotor shaft 11. That is, in the axial direction of the rotor shaft 11, the first ring gear 130 is located between the electric machine 10 and the first sun gear 110, the first ring gear 130 meshes with the first planet gears 121, and the first ring gear 130 is fixed relative to the housing of the planetary transmission. The first ring gear 130 may be connected to the housing of the planetary transmission via splines or rectangular teeth.
Further, the second planetary gear 220 includes a first planetary gear 221 and a second planetary gear 222, which are meshed with each other, the first planetary gear 221 and the second planetary gear 222 are both mounted on the second planet carrier 240, the first planetary gear 221 is meshed with the second ring gear 230, and the second planetary gear 222 is meshed with the second sun gear 210. Specifically, the second planet gears 220 are fixed to the second planet carrier 240 by a second planet shaft, which is fixed to the second planet carrier 240. The first planet gears 221 and the second planet gears 222 are respectively mounted on the second planet carrier 240 through the second planet gear shafts respectively corresponding to the first planet gears. The first planet gear 221 and the second planet gear 222 are in a constant mesh state, and the power of the motor 10 is transmitted to the second ring gear 230 through the first planet row 100, and then is transmitted to the first planet gear 221, the second planet gear 222, and the second sun gear 210 in sequence. The left half shaft 20 and the right half shaft 30 of the vehicle are connected with the second sun gear 210 and the second planet carrier 240, respectively, or the left half shaft 20 and the right half shaft 30 are connected with the second planet carrier 240 and the second sun gear 210, respectively, so that the power of the motor 10 is transmitted to the wheels. The second planetary gear 220 comprises a first planetary gear 221 and a second planetary gear 222, so that under the differential working condition, the high torque is obtained on the side with high rotating speed, and the low torque is obtained on the side with low rotating speed, so that the requirement of differential speed is met. On the other hand, the second planetary row 200 is more compact, so that the overall structure of the planetary-row transmission is more compact.
Further, the rotor shaft 11 is a hollow shaft, and the left half shaft 20 passes through the rotor shaft 11. Specifically, the rotor shaft 11 of the motor 10 is a hollow shaft, and the left half shaft 20 passes through the middle hollow of the rotor shaft 11 and is freely rotatable with respect to the rotor shaft 11, thereby transmitting power to the left wheel. Therefore, the overall structure of the planetary transmission is more compact.
The electric machine 10 is a power source of the planetary transmission and is used for providing power to the planetary transmission. More specifically, the electric machine 10 includes a stator and a rotor that outputs torque to the planetary transmission via a rotor shaft 11. The torque of the motor 10 is transmitted to the second planetary row 200 through the first planetary row 100, and the second planetary row 200 rotates under the action of the torque of the motor 10, so as to drive the left half shaft 20 and the right half shaft 30 to rotate, thereby driving the left wheel and the right wheel of the vehicle. In this way, speed reduction is achieved by the first planetary gear set 100 and differential speed is achieved by the second planetary gear set 200 to meet the speed requirement at the wheel end of the vehicle.
In one embodiment, the second sun gear 210 is connected to the left half shaft 20, and the second planet carrier 240 is connected to the right half shaft 30, wherein the second planet gears 220 comprise a first planet gear 221 and a second planet gear 222 which are meshed with each other. The torque transfer path for the left half shaft 20 at this time is: the electric machine 10-the first sun gear 110-the first planet gear 120-the first planet carrier 140-the second ring gear 230-the second planet gear one 221-the second planet gear two 222-the second sun gear 210-the left half shaft 20. The torque transfer path for the right half-shaft 30 is: the electric machine 10-the first sun gear 110-the first planet gear 120-the first planet carrier 140-the second ring gear 230-the second planet gear one 221-the second planet carrier 240-the right half shaft 30.
When the vehicle is running straight, the left and right wheels need to have the same rotational speed and torque. The torque of the motor 10 is reduced and increased in torque by the first planetary gear train 100, and then transmitted to the second planetary gear train 200, so that the rotation speed of the second planetary carrier 240 is the same as the rotation speed of the second sun gear 210, and the rotation speed and the torque output by the right half shaft 30 and the left half shaft 20 are the same.
When the vehicle left output speed is high, the left wheel speed and torque are higher than the right wheel speed and torque. When the vehicle turns right, the rotation speed of the left wheel is higher than that of the right wheel, and after being transmitted by the left half shaft 20 and the right half shaft 30, the larger rotation speed is transmitted to the second sun gear 210, and the smaller rotation speed is transmitted to the second planet carrier 240, at this time, the gear ratio of the second gear ring 230 and the second sun gear 210 makes the speed value of the second sun gear 210 increasing equal to the speed value of the second planet carrier 240 decreasing, so that the left half shaft 20 outputs the higher rotation speed and the higher torque, and the right half shaft 30 outputs the lower rotation speed and the smaller torque.
When the vehicle right output speed is high, the right wheel speed and torque are higher than the left wheel speed and torque. When the vehicle turns left, the rotation speed of the right wheel is higher than that of the left wheel, and after being transmitted by the left half shaft 20 and the right half shaft 30, the lower rotation speed is transmitted to the second sun gear 210, and the higher rotation speed is transmitted to the second planet carrier 240, at this time, the speed value of the second sun gear 210 descending is equal to the speed value of the second planet carrier 240 ascending through the tooth number ratio of the second gear ring 230 and the second sun gear 210, so that the left half shaft 20 outputs the lower rotation speed and the lower torque, and the right half shaft 30 outputs the higher rotation speed and the higher torque.
In another embodiment, the second sun gear 210 is connected to the right half shaft 30, and the second planet carrier 240 is connected to the left half shaft 20, wherein the second planet gears 220 comprise a first planet gear 221 and a second planet gear 222, which are meshed with each other. The torque transfer path for the left half shaft 20 at this time is: electric machine 10-first sun gear 110-first planet gear 120-first planet carrier 140-second ring gear 230-second planet gear one 221-second planet carrier 240-left half shaft 20. The torque transfer paths for the right half-shaft 30 are: the electric machine 10-the first sun gear 110-the first planet gear 120-the first planet carrier 140-the second ring gear 230-the second planet gear one 221-the second planet gear two 222-the second sun gear 210-the right half shaft 30. The specific differential principle is the same as that described above, and is not described in detail herein.
The utility model further provides a vehicle, which comprises the planetary transmission, the specific structure of the planetary transmission refers to the embodiments, and the vehicle adopts all technical schemes of all the embodiments, so that the vehicle at least has all the beneficial effects brought by the technical schemes of the embodiments, and the details are not repeated.
Therefore, the planetary transmission has the speed change function realized through the first planetary row 100 and the differential function realized through the second planetary row 200, so that the volume and the mass of transmission components are reduced, and the power density of the planetary transmission is greatly improved. Through the setting of first planet row 100 and second planet row 200, can realize that the speed ratio scope is wider, and the motor 10 rotational speed scope that makes planet row formula derailleur can bear is bigger to satisfy different design demands, and then enlarge the application scope of vehicle. Meanwhile, the axial structure of the planet row type transmission is more compact, the whole mass of the planet row type transmission is lighter, and light weight of a vehicle is facilitated.
The above description is only an alternative embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (10)
1. A planet row type transmission is characterized by comprising a motor, a first planet row, a second planet row, a left half shaft and a right half shaft;
the first planet row comprises a first sun gear, a first planet gear, a first gear ring and a first planet carrier, the first sun gear is meshed with the first planet gear, the first planet gear is meshed with the first gear ring, and the first planet gear is mounted on the first planet carrier;
the second planet row comprises a second sun gear, a second planet gear, a second ring gear and a second planet carrier, the second sun gear is meshed with the second planet gear, the second planet gear is meshed with the second ring gear, and the second planet gear is mounted on the second planet carrier;
the motor is in transmission connection with the first sun gear through a rotor shaft;
the first planet carrier is in transmission connection with the second gear ring;
the second planet row is connected with the left half shaft and the right half shaft to transmit the power of the motor.
2. The planetary transmission of claim 1, wherein the second sun gear is coupled to the left half shaft and the second carrier is coupled to the right half shaft.
3. The planetary transmission of claim 1, wherein the second sun gear is coupled to the right axle shaft and the second carrier is coupled to the left axle shaft.
4. The epicyclic gearbox of claim 1 wherein said first ring gear is located outboard of said first planet carrier and distal from said first sun gear and is fixed relative to a stationary portion of said epicyclic gearbox.
5. The planetary gearset of claim 4, wherein the first planet gear includes a first planet gear and a second planet gear connected, the first planet gear being in mesh with the first sun gear and the second planet gear being in mesh with the first ring gear.
6. The planetary transmission of claim 4, wherein the first planet includes a first planet and a second planet coupled, the first planet engaging the first ring gear, the second planet engaging the first sun gear.
7. The epicyclic transmission of claim 1 wherein said first planet gear comprises a first planet gear and a second planet gear connected, said first annulus being free of said rotor shaft and fixed relative to said housing of said epicyclic transmission, said first annulus meshing with said first planet gear, and said first sun meshing with said second planet gear.
8. The planetary gearset according to claim 1, wherein the second planetary gearset includes a first planetary gearset and a second planetary gearset that are in mesh, each mounted to the second carrier, the first planetary gearset being in mesh with the second ring gear, and the second planetary gearset being in mesh with the second sun gear.
9. The planetary range transmission of any one of claims 1-8, wherein the rotor shaft is a hollow shaft and the left axle shaft passes through the rotor shaft.
10. A vehicle characterized by comprising the planetary transmission according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220383128.0U CN216951528U (en) | 2022-02-23 | 2022-02-23 | Planet row type transmission and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220383128.0U CN216951528U (en) | 2022-02-23 | 2022-02-23 | Planet row type transmission and vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216951528U true CN216951528U (en) | 2022-07-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202220383128.0U Active CN216951528U (en) | 2022-02-23 | 2022-02-23 | Planet row type transmission and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216951528U (en) |
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2022
- 2022-02-23 CN CN202220383128.0U patent/CN216951528U/en active Active
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| TR01 | Transfer of patent right |
Effective date of registration: 20230620 Address after: No. 99, Beihui Road, Huishan Industrial Transformation Cluster, Wuxi City, Jiangsu Province, 214181 Patentee after: Wuxi Xingqu Power Technology Co.,Ltd. Patentee after: Wuxi Xingqu Technology Co.,Ltd. Patentee after: ZHEJIANG GEELY HOLDING GROUP Co.,Ltd. Address before: 310000 1760 Jiangling Road, Binjiang District, Hangzhou, Zhejiang. Patentee before: ZHEJIANG GEELY HOLDING GROUP Co.,Ltd. Patentee before: Wuxi Xingqu Technology Co.,Ltd. |