Power assembly and vehicle

Abstract

The invention discloses a power assembly and a vehicle. The power assembly comprises a driving motor and a speed reducer, and the driving motor is provided with a motor shaft; the speed reducer is in power connection with a motor shaft and a driving shaft of the vehicle and comprises a plurality of planetary gear mechanisms which are sequentially in power connection; the motor shaft is parallel to the driving shaft, and the planetary gear mechanisms are all fixed to a shell of the driving motor. Therefore, the planetary gear mechanisms which are sequentially in power connection are all fixed to the shell of the driving motor, the motor shaft and the driving shaft of the vehicle are arranged in parallel, so that all parts of the power assembly are compact in structure, and the transmission ratio in the same space can be increased; and the power output flexibility of the vehicle under different working conditions and the lightweight design of the vehicle are improved.

Description

Technical Field

[0001] The present application relates to the field of vehicle technology, and in particular to a powertrain and a vehicle. Background Art

[0002] With the rapid development of electric vehicle technology, the performance requirements for vehicle power systems are increasing. As a key component in the electric drive system, the performance of the reducer directly affects the power, economy, NVH (noise, vibration, and harshness) performance and reliability of the entire vehicle. Traditional electric drive reducers used in electric vehicles mostly adopt a parallel shaft reducer design, which consists of a two-stage or multi-stage external meshing gear transmission mechanism to form a reduction structure, and is combined with a bevel gear differential to achieve a differential function. Although this type of reducer has a mature structure, it has the problems of large size and heavy weight, and its performance in terms of transmission efficiency, NVH performance and transmission ratio is unsatisfactory.

[0003] The patent with publication number CN114450508B and its name is Planetary Transmission with Differential proposes a technical solution of introducing a double planetary gear transmission combined with a differential module, realizing the parallel and colinear arrangement of the input shaft and the output shaft, which can achieve the effect of smaller volume and lighter weight. However, this technical solution faces the following technical limitations in practical application: First, the primary speed ratio of the double planetary gear transmission is equal to the pitch circle diameter of the large planetary gear in the double planetary gear divided by the pitch circle diameter of the sun gear, and the secondary speed ratio is equal to the pitch circle diameter of the secondary gear ring divided by the pitch circle diameter of the secondary planetary gear, resulting in a technical bottleneck in further improving the transmission ratio within a given space; second, due to the special structure of the double planetary gear, there is no gear ring support on the outside of the large planetary gear and no sun gear constraint on the inside of the small planetary gear, resulting in the inability to effectively offset the radial force generated by the planetary gear during the transmission process. This unbalanced force distribution not only aggravates the deformation of the planetary gear, the planetary gear pin and the planetary carrier, but also increases the gear meshing transmission error and aggravates the load and wear between components; third, due to the problem that the radial force of the planetary gear cannot be offset, the double planetary gear transmission has a large power loss in the energy transmission process, which affects the improvement of the transmission efficiency; fourth, in order to ensure the phase relationship between the double planetary gears, the large and small planetary gears need to be made into one piece, and the small planetary gear needs to be honed, which has a complex processing technology and high requirements on equipment.

[0004] The reducer of the vehicle electric drive system in the existing technology has limitations to varying degrees in terms of transmission ratio, NVH performance, reliability, efficiency and processing and manufacturing, which leads to reduced power output flexibility, vehicle NVH performance, system reliability and vehicle energy efficiency under different working conditions, and increases product manufacturing costs and cycles. Summary of the invention

[0005] The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the present application is to propose a powertrain, which makes the components of the powertrain compact by fixing multiple planetary gear mechanisms that are sequentially connected to the housing of the drive motor and arranging the motor shaft in parallel with the drive shaft of the vehicle, so as to improve the transmission ratio in the same space, which is conducive to improving the power output flexibility of the vehicle under different working conditions and the lightweight design of the vehicle.

[0006] The application also proposes a vehicle having the above power assembly.

[0007] According to the powertrain of the first aspect embodiment of the present application, the powertrain includes: a drive motor and a reducer, the drive motor has a motor shaft; the reducer is dynamically connected to the motor shaft and the drive shaft of the vehicle, and the reducer includes a plurality of planetary gear mechanisms dynamically connected in sequence; wherein the motor shaft is parallel to the drive shaft, and the plurality of planetary gear mechanisms are all fixed to the housing of the drive motor.

[0008] According to the powertrain of the present application, by fixing multiple planetary gear mechanisms that are power-connected in sequence to the housing of the drive motor and arranging the motor shaft in parallel with the drive shaft of the vehicle, the components of the powertrain are made compact, which can improve the transmission ratio in the same space, and is beneficial to improving the power output flexibility of the vehicle under different working conditions and the lightweight design of the vehicle, helping to save the performance and cost optimization of the entire powertrain, and free up more space for the passenger compartment of the vehicle, thereby improving the user experience.

[0009] According to some embodiments of the present application, there are at least two planetary gear mechanisms, and include: a first planetary gear mechanism and a second planetary gear mechanism, wherein the first power input end of the first planetary gear mechanism is connected to the motor shaft, the first power output end of the first planetary gear mechanism is connected to the second power input end of the second planetary gear mechanism, and the second power output end of the second planetary gear mechanism is connected to the drive shaft of the vehicle axle to drive the wheels on both sides of the axle drive shaft to rotate.

[0010] In some embodiments, the first planetary gear mechanism includes: a first sun gear, a first planetary gear and a first ring gear, the first sun gear is arranged on the motor shaft and forms the first power input end; the first planetary gear is configured in plurality, and the plurality of first planetary gears are evenly arranged around the first sun gear and mesh with the first sun gear; the first ring gear is arranged on a side of the first planetary gear radially away from the first sun gear and meshes with the first planetary gear, and the first ring gear forms the first power output end.

[0011] Furthermore, the first planetary gear mechanism further includes: a first planet carrier, one end of the first planet carrier is rotatably connected to the plurality of first planetary gears, and the other end of the first planet carrier is connected to the housing.

[0012] In some embodiments, the first sun gear and the motor shaft are constructed as an integral piece.

[0013] According to some embodiments of the present application, the second planetary gear mechanism includes: a second sun gear, a second planetary gear and a second planet carrier, the second sun gear forms the second power input end and is dynamically connected to the first planetary gear mechanism; the second planetary gear is configured as a plurality of second planetary gears, and the plurality of second planetary gears are evenly arranged around the circumference of the second sun gear and mesh with the second sun gear; one end of the second planet carrier is rotatably connected to the plurality of second planetary gears, and the other end is configured as the second power output end.

[0014] Furthermore, the second sun gear is connected to the first ring gear of the first planetary gear mechanism, or is constructed as an integral part.

[0015] In some embodiments, the second planetary gear mechanism further includes: a second ring gear, which is disposed on a side of the second planetary gear radially away from the second sun gear and meshed with the second planetary gear, and the second ring gear is connected to the housing.

[0016] According to some embodiments of the present application, the motor shaft is constructed as a hollow shaft and is sleeved on the drive shaft.

[0017] According to some embodiments of the present application, the drive shaft includes: a first drive shaft and a second drive shaft, a differential is arranged between the first drive shaft and the second drive shaft, and the second planetary carrier of the second planetary gear mechanism is dynamically connected to the differential.

[0018] According to some embodiments of the present application, the second planet carrier includes a carrier body and a connecting shaft, the second planetary gear is rotatably disposed on the connecting shaft, and the carrier body is connected to the input bevel gear of the differential, or is integrally formed.

[0019] According to some embodiments of the present application, an extension direction of the frame is orthogonal to an extension direction of the connecting axis.

[0020] According to a vehicle of an embodiment of the second aspect of the present application, the vehicle comprises: a powertrain according to any one of the above embodiments.

[0021] Additional aspects and advantages of the present application will be given in part in the description below, and in part will become apparent from the description below, or will be learned through the practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0023] Figure 1 is a schematic diagram of the powertrain structure according to an embodiment of the first aspect of the present application;

[0024] Figure 2 It is a schematic diagram of the powertrain structure according to the second embodiment of the present application.

[0025] Reference numerals:

[0026] 3000, wheel;

[0027] 2000a, a first driving shaft; 2000b, a second driving shaft;

[0028] 1000. Powertrain;

[0029] 11. Motor shaft; 12. Housing; 13. Rotor; 14. Stator; 15. Motor front bearing; 16. Motor rear bearing;

[0030] 21. A first planetary gear mechanism;

[0031] 211, first sun gear; 212, first planetary gear; 213, first ring gear; 214, first planet carrier;

[0032] 22, second planetary gear mechanism; 221, second sun gear; 222, second planetary gear; 223, second ring gear; 224, second planet carrier; 224a, carrier body; 224b, connecting shaft;

[0033] 3. Differential. DETAILED DESCRIPTION

[0034] The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application, and cannot be understood as limiting the present application.

[0035] Reference below Figure 1 and Figure 2 A powertrain 1000 and a vehicle according to an embodiment of the present application are described.

[0036] like Figure 1 and Figure 2 As shown, according to the power assembly 1000 of the embodiment of the first aspect of the present application, the power assembly 1000 includes: a driving motor and a reducer.

[0037] Among them, the driving motor has a motor shaft 11; the reducer is dynamically connected to the motor shaft 11 and the driving shaft of the vehicle, and the reducer includes multiple planetary gear mechanisms dynamically connected in sequence; the motor shaft 11 is parallel to the driving shaft, and the multiple planetary gear mechanisms are all fixed to the housing 12 of the driving motor.

[0038] Specifically, the drive motor is used to provide power and output it in the form of torque through the motor shaft 11. The reducer is connected to the motor shaft 11 and the drive shaft of the vehicle in a power connection. The power connection here means that the components can be directly connected or linked through an intermediate transmission component to achieve power transmission, so that the reducer can receive power from the motor shaft 11 and stably transmit it to the drive shaft of the vehicle, thereby driving the wheels to rotate. The reducer includes a plurality of planetary gear mechanisms that are connected in power in sequence. The plurality of planetary gear mechanisms can sequentially transmit and convert torque power from the motor shaft 11 according to a preset transmission ratio, and finally transmit the power to the drive shaft of the vehicle, wherein the conversion process can be achieved by the meshing between the planetary gears and the sun gear of the planetary gear mechanism. In the present application, multiple planetary gear mechanisms are fixed to the housing 12 of the drive motor, forming a compact and efficient transmission system, which makes the entire powertrain 1000 more compact in size and improves the stability and reliability of the entire powertrain. In addition, the motor shaft 11 is arranged in parallel with the drive shaft of the vehicle. The motor shaft 11, as the output end of the power source, is arranged parallel to the drive shaft of the vehicle, which is conducive to simplifying the transmission chain and reducing power loss and vibration caused by angular deviation. This further improves the compactness of the structure, can further save the space occupied by the powertrain 1000, and increase space utilization.

[0039] According to the powertrain 1000 of the present application, by fixing multiple planetary gear mechanisms that are power-connected in sequence to the housing of the drive motor and arranging the motor shaft 11 in parallel with the drive shaft of the vehicle, the components of the powertrain 1000 are made compact, which can improve the transmission ratio in the same space, and is beneficial to improving the power output flexibility of the vehicle under different working conditions and the lightweight design of the vehicle, helping to save the performance and cost optimization of the entire powertrain 1000, and free up more space for the passenger compartment of the entire vehicle, thereby improving the user experience.

[0040] In addition, in some specific embodiments of the present application, the driving motor has a rotor 13 and a stator 14. The rotor 13 is sleeved on the outer periphery of the motor shaft 11, and the stator 14 is arranged on the side of the rotor 13 radially away from the motor shaft 11. The stator 14 and the rotor 13 cooperate to convert electrical energy into mechanical energy, and output it through the rotation of the motor shaft 11 to provide a power source for the power assembly 1000.

[0041] In some other specific embodiments of the present application, a motor front bearing 15 and a motor rear bearing 16 are further provided in the drive motor to support the motor shaft 11 and improve the working stability and reliability of the motor.

[0042] like Figure 1 and Figure 2 As shown, according to some embodiments of the present application, there are at least two planetary gear mechanisms, and include: a first planetary gear mechanism 21 and a second planetary gear mechanism 22, the first power input end of the first planetary gear mechanism 21 is connected to the motor shaft 11, the first power output end of the first planetary gear mechanism 21 is connected to the second power input end of the second planetary gear mechanism 22, and the second power output end of the second planetary gear mechanism 22 is connected to the drive shaft to drive the wheels 3000 on both sides of the drive shaft axis to rotate.

[0043] Specifically, the first planetary gear mechanism 21 and the second planetary gear mechanism 22 are arranged in series to form a multi-stage deceleration effect. The first power input end of the first planetary gear mechanism 21 is connected to the motor shaft 11 to receive power input from the drive motor. The internal transmission parts of the first planetary gear mechanism 21 (such as an intermediate shaft or meshing gears) can realize preliminary deceleration and transmission of power, and the first power input end is connected to the second power input end of the second planetary gear mechanism 22, so that the second power input end can receive the power after deceleration from the first planetary gear mechanism 21. After further deceleration by the second planetary gear mechanism 22, the power can be transmitted to the drive shaft of the vehicle through the second power output end, and finally drive the wheels 3000 on both sides of the drive shaft to rotate. The optimized layout and gear meshing design of the two-stage planetary gear mechanism in the embodiment of the present application can reduce the gear meshing transmission error, reduce the load and wear between the components, thereby improving the vehicle's NVH performance and reliability, and can also reduce energy loss during power transmission, improve overall transmission efficiency, and optimize the energy efficiency of the vehicle. In addition, the two-stage planetary gear mechanism can adopt a conventional structure with a mature processing technology and no excessively high requirements for equipment, so the processing and manufacturing economy is better.

[0044] In addition, in some specific embodiments of the present application, the power transmission direction between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 is perpendicular to the axial direction of the motor shaft 11 and the drive shaft, so as to optimize the layout of the two-stage planetary gear mechanism. The first planetary gear mechanism 21 and the second planetary gear mechanism 22 can be arranged in series in a direction perpendicular to the motor shaft 11 and the drive shaft, and ensure that power can be smoothly transmitted from one stage to another. In this way, while ensuring a good power transmission effect, the layout flexibility of the first planetary gear mechanism 21 and the second planetary gear mechanism 22 can be improved, the overall structural compactness of the powertrain 1000 can be improved, the space utilization rate can be increased, and it is beneficial to improve the energy efficiency of the whole vehicle and the lightweight of the whole vehicle.

[0045] like Figure 1 As shown, according to some embodiments of the present application, the first planetary gear mechanism 21 includes: a first sun gear 211 , a first planetary gear 212 and a first ring gear 213 .

[0046] Among them, the first sun gear 211 is arranged on the motor shaft 11 and forms a first power input end; the first planetary gear 212 is constructed in multiple, and the multiple first planetary gears 212 are evenly arranged around the first sun gear 211 and meshed with the first sun gear 211; the first ring gear 213 is arranged on the side of the first planetary gear 212 radially away from the first sun gear 211, and meshed with the first planetary gear 212, and the first ring gear 213 forms a first power output end.

[0047] Specifically, the first sun gear 211 can be directly arranged on the motor shaft 11 of the drive motor, and rotate synchronously with the motor shaft 11 in some way (such as spline connection, etc.). The first sun gear 211 serves as a first power input end and can receive rotational power from the drive motor; the first planetary gear 212 can be constructed as a plurality of gears uniformly arranged circumferentially around the first sun gear 211, and each first planetary gear 212 is meshed with the first sun gear 211, so that the first planetary gear 212 and the first sun gear 211 are transmitted through tooth meshing, wherein the number and size of the first planetary gears 212 can be designed according to the actual transmission ratio and load-bearing capacity requirements; the first ring gear 213 can be arranged on the side of the plurality of first planetary gears 212 radially away from the first sun gear 211, and the radial inner side of the first ring gear 213 can be formed with internal teeth meshed with the external teeth of the first planetary gear 212, and the first planetary gear 212 and the first ring gear 213 are transmitted through tooth meshing.

[0048] It can be understood that the first planetary gear 212 rotates and revolves during the transmission process to transmit the rotational power input by the first sun gear 211 to the first ring gear 213, and realizes power deceleration and torque amplification in the process, and the first ring gear 213, as the first power output end, can transmit the power after deceleration and torque amplification to the second planetary gear mechanism 22 and other subsequent transmission components. The first planetary gear mechanism 21 can realize efficient power transmission and deceleration and torque increase through the meshing transmission of the first sun gear 211, the first planetary gear 212 and the first ring gear 213, and the first sun gear 211, the first planetary gear 212 and the first ring gear 213 are arranged radially, which also makes the entire first planetary gear mechanism 21 compact and small in size, which is conducive to saving space.

[0049] It should be pointed out that the first ring gear 213 serves as the outer component of the first planetary gear mechanism 21, and its internal teeth mesh with the outer teeth of the first planetary gear 212 to achieve power transmission. At the same time, the first ring gear 213 can also support and fix the first planetary gear 212, which can increase the accuracy of gear meshing transmission, help improve the uniformity of load distribution between components and protect components from damage, thereby improving the working reliability and working performance of the powertrain 1000.

[0050] like Figure 1 As shown, according to some embodiments of the present application, the first planetary gear mechanism 21 further includes: a first planet carrier 214 , one end of which is rotatably connected to the plurality of first planetary gears 212 , and the other end of which is connected to the housing 12 .

[0051] Specifically, one end of the first planetary carrier 214 can be connected to multiple first planetary gears 212, and the first planetary carrier 214 can support and fix the multiple first planetary gears 212, and realize the circumferential and radial limitation of the first planetary gears 212, so that the multiple first planetary gears 212 can be evenly arranged around the first sun gear 211 and rotate stably, thereby enhancing the structural stability of the first planetary gear mechanism 21 and improving the continuity and reliability of power transmission; the other end of the first planetary carrier 214 can be connected to the housing 12 of the drive motor to realize the installation and fixation of the first planetary carrier 214, and to improve the integration of the first planetary carrier 214 and the drive motor, and ensure the structural integrity of the entire powertrain 1000.

[0052] In addition, in some specific embodiments of the present application, a bearing hole or a journal matching the first planetary gear 212 is provided at one end of the first planetary carrier 214, and a rotatable connection between the first planetary carrier 214 and the first planetary gear 212 can be achieved through components such as bearings; the other end of the first planetary carrier 214 can be connected to the housing 12 of the drive motor by bolts, pins or other fasteners to form a stable support structure.

[0053] like Figure 1 As shown, according to some embodiments of the present application, the first sun gear 211 and the motor shaft 11 are constructed as an integral piece.

[0054] Specifically, by constructing the first sun gear 211 and the motor shaft 11 as an integral part, there is no connector or gap between the first sun gear 211 and the motor shaft 11, so that the number of components can be reduced, the cost can be saved, and the stability and reliability of the assembly structure of the first sun gear 211 and the motor shaft 11 can be improved, thereby improving the durability and reliability of the power assembly 1000. In addition, since the integral part does not have a connector or gap, the energy loss in the power transmission process can also be reduced, which is conducive to improving the overall transmission efficiency of the power assembly 1000.

[0055] like Figure 1 As shown, according to some embodiments of the present application, the second planetary gear mechanism 22 includes: a second sun gear 221 , second planetary gears 222 and a second planet carrier 224 .

[0056] Among them, the second sun gear 221 is formed as a second power input end and is power-connected to the first planetary gear mechanism 21; the second planetary gear 222 is constructed in multiple, and the multiple second planetary gears 222 are evenly arranged around the second sun gear 221 and meshed with the second sun gear 221; one end of the second planetary carrier 224 is rotatably connected to the multiple second planetary gears 222, and the other end is constructed as a second power output end.

[0057] Specifically, the second sun gear 221 can be arranged on the radially outer side or axial side of the first ring gear 213, and be directly or indirectly connected to the first ring gear 213 to receive power from the first planetary gear mechanism 21. The second sun gear 221 serves as a second power input end, and can introduce the power output by the first planetary gear mechanism 21 into the second planetary gear mechanism 22 to achieve further transmission and conversion. It can be understood that the design of the structure and size of the second sun gear 221 needs to consider the connection method and transmission ratio requirements with the first ring gear 213 to ensure the continuity and accuracy of power transmission; similarly, the second planetary gear 222 can be constructed as a plurality of gears uniformly arranged circumferentially around the second sun gear 221, and each second planetary gear 222 is meshed with the second sun gear 221, so that the second planetary gear 222 Transmission is achieved through tooth meshing with the second sun gear 221, wherein the number and size of the second planetary gears 222 can be designed according to the actual transmission ratio and load-bearing capacity requirements; one end of the second planetary carrier 224 can be connected to a plurality of second planetary gears 222 to support and fix the plurality of second planetary gears 222, thereby achieving circumferential and radial limitation of the second planetary gears 222, so that the plurality of second planetary gears 222 can be evenly arranged around the second sun gear 221 and rotate stably, thereby enhancing the structural stability of the second planetary gear mechanism 22 and improving the continuity and reliability of power transmission; the other end of the second planetary carrier 224 is constructed as a second power output end, which is connected to the drive shaft of the vehicle to transmit the power output of the second planetary gear mechanism 22 to the drive shaft to drive the wheels 3000 to rotate.

[0058] Similarly, the second planetary gear 222 rotates and revolves during the transmission process to transmit the rotational power input by the second sun gear 221 to the second planetary carrier 224, and in this process, power deceleration and torque amplification are achieved. The second planetary carrier 224, as the second power output end, can transmit the power after deceleration and torque amplification to the drive shaft to drive the wheel 3000 to rotate. The second planetary gear mechanism 22 can achieve efficient power transmission and deceleration and torque increase through the cooperation of the second sun gear 221, the second planetary gear 222 and the second planetary carrier 224. At the same time, the layout of the second sun gear 221, the second planetary gear 222 and the second planetary carrier 224 is conducive to improving the structural compactness of the second planetary gear mechanism 22, which helps to optimize the volume of the power assembly 1000 and save the layout space.

[0059] It should be pointed out that compared with the related technology, there is no ring gear structure on the outer side of the first-stage planetary gear and no sun gear on the inner side of the second-stage planetary gear, which leads to the inability to offset the radial forces of the two-stage planetary gears, increases the deformation of the planetary gears, planetary gear pins and planetary carriers, increases the gear meshing transmission error, increases the load and wear between the components, and poses a threat to the NVH performance and the long-term reliability of the system. The reducer of the present application adopts a first planetary gear mechanism 21 and a second planetary gear mechanism 22 arranged in series, a first ring gear 213 is provided on the outer side of the first planetary gear 212 in the first planetary gear mechanism 21, and a second sun gear 221 is provided on the inner side of the second planetary gear 222 in the second planetary gear mechanism 22, so that the radial forces of the two-stage planetary gear mechanisms can be completely offset, and the deformation of the planetary gears, planetary gear pins and planetary carriers is reduced, thereby improving the gear meshing transmission accuracy, reducing the load and wear between the components, and further improving the working reliability and NVH performance of the powertrain 1000.

[0060] like Figure 1 As shown, according to some embodiments of the present application, the second sun gear 221 is connected to the first ring gear 213 of the first planetary gear mechanism 21 , or is constructed as an integral piece.

[0061] Specifically, in the embodiment of the present application, the second sun gear 221 and the first ring gear 213 can be two independent components manufactured separately. The second sun gear 221 and the first ring gear 213 can be connected into a component through a specific connection structure. In some specific embodiments, the connection structure between the second sun gear 221 and the first ring gear 213 can be constructed as bolts, pins, etc. to ensure the stable connection and transmission accuracy between the second sun gear 221 and the first ring gear 213. The method of manufacturing the second sun gear 221 and the first ring gear 213 separately can make the manufacturing of the second sun gear 221 and the first ring gear 213 more flexible, and the size, shape and material of each component can be adjusted according to actual needs to achieve the best transmission effect and structural strength. In addition, it is also beneficial to improve manufacturing convenience, reduce costs and improve production efficiency. In addition, separate manufacturing can also make the maintenance and replacement of the second sun gear 221 and the first ring gear 213 more convenient and quick.

[0062] In the embodiment of the present application, the second sun gear 221 and the first ring gear 213 can also be constructed as an integral part. In this way, on the first hand, the connection interface between the two can be eliminated, and transmission failure or damage caused by loose or wear of the interface can be avoided, thereby effectively enhancing the structural strength of the entire component, enabling it to withstand greater forces and torques, thereby improving the reliability and durability of the powertrain 1000; on the second hand, the one-piece molded part can eliminate the intermediate connecting parts, thereby reducing the number of parts, which is beneficial to improving production efficiency, and is also beneficial to reducing the cost and weight of the powertrain 1000, and further saving the layout space occupied by the powertrain 1000; on the third hand, the one-piece molded part can also reduce the gap and friction between components, reduce the energy loss during power transmission, and enable power to be more smoothly transmitted from the first planetary gear mechanism 21 to the second planetary gear mechanism 22, which helps to improve transmission efficiency.

[0063] like Figure 1 As shown, according to some embodiments of the present application, the second planetary gear mechanism 22 also includes: a second ring gear 223, which is arranged on the side of the second planetary gear 222 radially away from the second sun gear 221 and meshed with the second planetary gear 222, and the second ring gear 223 is connected to the housing 12.

[0064] Specifically, the second ring gear 223 can be arranged on the side of the plurality of second planetary gears 222 radially away from the second sun gear 221, and the radial inner side of the second ring gear 223 can be formed with internal teeth meshing with the external teeth of the second planetary gears 222, and the second planetary gears 222 and the second ring gear 223 realize transmission through tooth meshing. It can be understood that the second ring gear 223, as the outer component of the second planetary gear mechanism 22, can play a good supporting and limiting role for the second planetary gear 222, and can further increase the accuracy of gear meshing transmission in the second planetary gear mechanism 22, further improve the uniformity of load distribution between components and protect components from damage, thereby further optimizing the working reliability and working performance of the powertrain 1000. In addition, the second ring gear 223 is connected to the housing 12 of the drive motor, which can enhance the structural stability of the entire powertrain 1000, and also help to optimize the power transmission path and improve transmission efficiency.

[0065] In addition, in some specific embodiments of the present application, the outer edge of the second gear ring 223 is formed with an interface or structure suitable for connecting to the drive motor housing 12, such as a bolt hole, a positioning pin hole, etc., so as to achieve a stable connection with the drive motor housing 12.

[0066] It should be pointed out that the first sun gear 211, the first planetary gear 212, the first ring gear 213, the second sun gear 221, the second planetary gear 222 and the second ring gear 223 of the present application can be but are not limited to a spur gear structure or a helical gear structure, etc., and the present application does not limit this.

[0067] like Figure 1 and Figure 2 As shown, according to some embodiments of the present application, the motor shaft 11 is constructed as a hollow shaft and is sleeved on the drive shaft.

[0068] Specifically, the motor shaft 11 can be constructed as a hollow shaft, which is hollow inside, saving material costs, reducing the weight of the motor shaft 11 itself, achieving overall cost reduction and weight reduction of the power assembly 100, and helping to improve the fuel economy and driving performance of the vehicle. At the same time, the inside of the hollow shaft can provide a layout space for the drive shaft, and the hollow shaft can be sleeved on at least part of the outer circumference of the drive shaft. This arrangement allows the motor shaft 11 and the drive shaft to be integrated on the same axis, thereby further improving the compactness of the structure and optimizing the spatial layout of the power assembly 1000.

[0069] like Figure 1 and Figure 2 As shown, according to some embodiments of the present application, the drive shaft includes: a first drive shaft 2000a and a second drive shaft 2000b, a differential 3 is arranged between the first drive shaft 2000a and the second drive shaft 2000b, and the second planetary carrier 224 of the second planetary gear mechanism 22 is power-connected to the differential 3.

[0070] Specifically, the axial lengths of the first drive shaft 2000a and the second drive shaft 2000b may be different, one end of the first drive shaft 2000a and one end of the second drive shaft 2000b are both connected to the output gear of the differential 3, and the other end of the first drive shaft 2000a and the other end of the second drive shaft 2000b are respectively suitable for connecting to the left and right wheels 3000 of the vehicle, so as to realize the power transmission between the differential 3 and the wheels 3000 and the adjustment and control of the left and right wheels 3000 by the differential 3. Among them, the differential 3 can be located on the side of the second planetary gear mechanism 22 that is axially away from the drive motor, and the differential 3 can have an input end gear and an output end gear. The input end gear can be connected to the second planet carrier 224 of the second planetary gear mechanism 22 to realize the transmission of power, ensure the smooth transmission of power from the second planetary gear mechanism 22 to the differential 3, and reduce energy loss and transmission noise, and the output end gear can be connected to the drive shaft to realize the distribution and output of power to the drive shaft. The differential 3 has a differential function. During the driving of the vehicle, the differential 3 can adjust the power distribution ratio of the left and right wheels 3000 according to different road conditions and driving conditions, allowing the left and right wheels 3000 to rotate at different speeds when the vehicle is turning, so as to improve the adaptability, passability and driving stability of the vehicle.

[0071] like Figure 1 and Figure 2 As shown, according to some embodiments of the present application, the second planetary carrier 224 includes a carrier body 224a and a connecting shaft 224b, the second planetary gear 222 is rotatably disposed on the connecting shaft 224b, and the carrier body 224a is connected to the input bevel gear of the differential 3, or is integrally formed.

[0072] Specifically, one end of the frame 224a is connected to one end of the connecting shaft 224b, and there may be multiple connecting shafts 224b. The other end of each connecting shaft 224b is connected to a second planetary gear 222 and arranged coaxially therewith, so that each second planetary gear 222 can independently rotate around its corresponding connecting shaft 224b and participate in the orbital motion of the entire second planetary gear mechanism 22 to ensure the accuracy and stability of power transmission; and one end of the frame 224a is connected to the same end of the multiple connecting shafts 224b in the extension direction (that is, the end away from the second planetary gear 222), and the extension directions of the frame 224a and the connecting shaft 224b are different, thereby realizing the change of power transmission direction, and the end of the frame 224a away from the connecting shaft 224b is linked with the drive shaft, and the power decelerated and torque amplified by the two-stage planetary gear mechanism can be transmitted to the drive shaft, driving the wheel 3000 to rotate.

[0073] It should be noted that the frame 224a can be connected to the input bevel gear of the differential 3, for example, by fasteners, welding, etc. The frame 224a can also be integrally formed with the input bevel gear of the differential 3 to save production costs, improve assembly efficiency, and improve the overall stability of the structure.

[0074] like Figure 1 and Figure 2 As shown, according to some embodiments of the present application, the extension direction of the frame 224a is orthogonal to the extension direction of the connecting shaft 224b.

[0075] Specifically, the extension direction of the frame 224a is orthogonal to the extension direction of the connecting shaft 224b, and the extension direction of the connecting shaft 224b can be consistent with the extension direction of the motor shaft 11 and the drive shaft. By setting the axial direction of the connecting shaft 224b and the frame 224a to be orthogonal, the power transmission direction is changed. On the one hand, while the reducer is flexibly arranged between the drive motor and the drive shaft to achieve the deceleration function, it can meet the requirement of parallel arrangement of the motor shaft 11 of the drive motor and the drive shaft; on the other hand, it can also make the entire second planetary carrier 224 structure more compact, which can further optimize the overall volume of the powertrain 1000.

[0076] like Figure 1 and Figure 2 As shown, according to the vehicle of the second aspect embodiment of the present application, the vehicle includes: a powertrain 1000 described in any one of the above embodiments, and the technical effects produced are consistent with those in the above embodiments, which will not be repeated here.

[0077] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0078] In the description of this application, "first feature" or "second feature" may include one or more of the features.

[0079] In the description of the present application, “plurality” means two or more.

[0080] In the description of the present application, a first feature being “on” or “under” a second feature may include that the first and second features are directly in contact with each other, or may include that the first and second features are not in direct contact with each other but are in contact with each other via another feature therebetween.

[0081] In the description of the present application, “above”, “over” and “above” a first feature to a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature.

[0082] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0083] Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims

1. A powertrain, characterized in that: include: A drive motor, the drive motor having a motor shaft (11); A reducer, the reducer is dynamically connected to the motor shaft (11) and the driving shaft of the vehicle, and the reducer comprises a plurality of planetary gear mechanisms dynamically connected in sequence; wherein The motor shaft (11) is parallel to the drive shaft, and the plurality of planetary gear mechanisms are all fixed to a housing (12) of the drive motor.

2. The powertrain according to claim 1, characterized in that: There are at least two planetary gear mechanisms, and they include: a first planetary gear mechanism (21) and a second planetary gear mechanism (22); a first power input end of the first planetary gear mechanism (21) is connected to the motor shaft (11); a first power output end of the first planetary gear mechanism (21) is connected to a second power input end of the second planetary gear mechanism (22); and a second power output end of the second planetary gear mechanism (22) is connected to the drive shaft to drive the wheels (3000) on both sides of the drive shaft to rotate.

3. The powertrain according to claim 2, characterized in that: The first planetary gear mechanism (21) comprises: A first sun gear (211), the first sun gear (211) being arranged on the motor shaft (11) and forming the first power input end; a first planetary gear (212), wherein the first planetary gear (212) is configured as a plurality of first planetary gears (212), and the plurality of first planetary gears (212) are evenly arranged in the circumferential direction around the first sun gear (211) and mesh with the first sun gear (211); A first ring gear (213), the first ring gear (213) is arranged on a side of the first planetary gear (212) radially away from the first sun gear (211) and meshes with the first planetary gear (212), and the first ring gear (213) forms the first power output end.

4. The powertrain according to claim 3, characterized in that: Also includes: A first planet carrier (214), one end of the first planet carrier (214) is rotatably connected to the plurality of first planetary gears (212), and the other end of the first planet carrier (214) is connected to the housing (12).

5. The powertrain according to claim 3, characterized in that: The first sun gear (211) and the motor shaft (11) are constructed as an integral piece.

6. The powertrain according to claim 2, characterized in that: The second planetary gear mechanism (22) comprises: a second sun gear (221), the second sun gear (221) forming the second power input end and being power-connected to the first planetary gear mechanism (21); A second planetary gear (222), wherein the second planetary gear (222) is configured as a plurality of second planetary gears (222), and the plurality of second planetary gears (222) are evenly arranged in the circumferential direction around the second sun gear (221) and mesh with the second sun gear (221); A second planet carrier (224), one end of the second planet carrier (224) is rotatably connected to the plurality of second planetary gears (222), and the other end is configured as the second power output end.

7. The powertrain according to claim 6, characterized in that: The second sun gear (221) is connected to the first ring gear (213) of the first planetary gear mechanism (21), or is constructed as an integral part.

8. The powertrain according to claim 6, characterized in that: Also includes: A second ring gear (223), the second ring gear (223) is arranged on a side of the second planetary gear (222) radially away from the second sun gear (221) and meshes with the second planetary gear (222), and the second ring gear (223) is connected to the housing (12).

9. The powertrain according to claim 1, characterized in that: The motor shaft (11) is constructed as a hollow shaft and is sleeved on the drive shaft.

10. The powertrain according to any one of claims 8, characterized in that: The drive shaft comprises: a first drive shaft (2000a) and a second drive shaft (2000b), a differential (3) is arranged between the first drive shaft (2000a) and the second drive shaft (2000b), and a second planetary carrier (224) of the second planetary gear mechanism (22) is power-connected to the differential (3).

11. The powertrain according to claim 10, characterized in that: The second planet carrier (224) comprises a carrier body (224a) and a connecting shaft (224b), the second planetary gear (222) is rotatably arranged on the connecting shaft (224b), and the carrier body (224a) is connected to the input bevel gear of the differential (3), or is integrally formed.

12. The powertrain according to claim 11, characterized in that: The extension direction of the frame (224a) is orthogonal to the extension direction of the connecting shaft (224b).

13. A vehicle, characterized in that: include: The powertrain according to any one of claims 1 to 12.

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