An electrically driven axle

Abstract

The utility model provides a kind of electric drive axle, comprising: motor, planetary mechanism and gearbox;Planetary mechanism includes: first planetary row and second planetary row;First planetary row is connected between motor and second planetary row;Gearbox, including at least one parallel shaft mechanism;Wherein one end of a parallel shaft mechanism is the input end of gearbox;The input end of gearbox is respectively connected with second planet carrier or planetary output shaft transmission under the action of butt joint component;Through the integrated design of two-stop planetary row and two-stop parallel axle gearbox, four-stop variable speed function is realized, while improving transmission efficiency, lightweight and good space adaptability are realized.

Description

Technical Field

[0001] This utility model relates to the field of electric drive axles, and in particular to an electric drive axle. Background Technology

[0002] An electric drive axle is an integrated unit consisting of a motor, gearbox, etc., used to drive the wheels. For example, the electric drive axle disclosed in publication number CN117565648A includes: a drive axle, a gearbox, a motor, and a power take-off (PTO). The gearbox has an input shaft, an intermediate shaft, and an output shaft that are sequentially connected in transmission. The input shaft, intermediate shaft, and output shaft are all parallel to the drive axle. The motor is connected to the input shaft in transmission, and the drive axle and PTO are connected to the output shaft in transmission.

[0003] However, existing electric drive axles typically employ multi-stage gear transmissions, which suffer from problems such as complex structure, heavy weight, and low transmission efficiency. Furthermore, traditional designs have shortcomings in their lubrication systems, including significant oil churning losses and high lubrication oil requirements, leading to increased overall costs. Utility Model Content

[0004] The purpose of this invention is to provide an electric drive bridge to solve the problems of complex structure, large size and high energy loss of existing electric drive bridges.

[0005] This utility model provides an electric drive axle with the following technical solution: a motor, a planetary mechanism, and a gearbox;

[0006] The planetary mechanism includes: a first planetary gear set and a second planetary gear set; the first planetary gear set is connected between the motor and the second planetary gear set;

[0007] The first planetary gear set includes: a first sun gear and a first planet gear; the first sun gear is connected to the motor, and the first sun gear meshes with the first planet gear;

[0008] The second planetary gear set includes: a planetary output shaft, a second sun gear, a second ring gear, second planet gears, and a second planet carrier; the second sun gear is fixedly sleeved on the planetary output shaft; the second ring gear and the second sun gear are concentrically arranged; all the second planet gears mesh between the second sun gear and the second ring gear; the second planet carrier is fixedly connected to all the second planet gears; the input end of the second planet carrier passes through the second planet gears in sequence; the second planet gears are located away from the output end of the second planet carrier.

[0009] The gearbox includes at least one parallel shaft mechanism; one end of the parallel shaft mechanism is the input end of the gearbox; the input end of the gearbox is connected to the second planetary carrier or the planetary output shaft respectively under the action of the docking assembly.

[0010] Preferably, the gearbox includes: a first parallel shaft mechanism and a second parallel shaft mechanism;

[0011] The first parallel shaft mechanism and the second parallel shaft mechanism are arranged side by side; the second parallel shaft mechanism is located between the first parallel shaft mechanism and the differential.

[0012] Preferably, the first parallel shaft mechanism includes: a first transmission shaft and a first gear set;

[0013] The first drive shaft is coaxially arranged with the planetary output shaft;

[0014] The first gear set is arranged on the first transmission shaft; the first gear set includes, in sequence: a docking assembly, a first gear drive gear, a shifting assembly, and a second gear drive gear; the output end of the docking assembly and the input end of the shifting assembly are fixedly sleeved on the first transmission shaft; the first gear drive gear and the second gear drive gear are loosely sleeved on the first transmission shaft.

[0015] Preferably, the shift assembly includes: a shift gear and a gear engagement sleeve;

[0016] The shift gear is fixedly sleeved on the first drive shaft; the gear engagement sleeve is slidably sleeved on the shift gear; the shift engagement sleeve moves axially along the first drive shaft to engage with the first gear drive gear or the second gear drive gear.

[0017] Preferably, the second parallel shaft mechanism includes: a second transmission shaft and a second gear set;

[0018] The second drive shaft is parallel to the first drive shaft;

[0019] The second gear set is fixedly mounted on the second transmission shaft; the second gear set includes, in sequence: a power output gear, a first-gear driven gear, and a second-gear driven gear.

[0020] Preferably, the first gear drive gear meshes with the first gear driven gear; the second gear drive gear meshes with the second gear driven gear; and the power output gear meshes with the differential.

[0021] Preferably, the first gear set further includes: a power take-off drive gear;

[0022] The power take-off drive gear is sleeved on the first drive shaft and located between the docking assembly and the first drive gear; the power take-off drive gear meshes with the power take-off unit.

[0023] Preferably, the output end of the first drive shaft is fixedly connected to the oil pump.

[0024] Preferably, the planetary mechanism further includes: a synchronization component;

[0025] The input of the synchronization component can be selectively aligned with either a first shift position or a second shift position; the first shift position corresponds to the planetary output shaft; and the second shift position corresponds to the output of the second planetary carrier.

[0026] Preferably, the docking assembly includes: a docking gear and a docking engagement sleeve;

[0027] The docking gear is fixedly sleeved on the first transmission shaft. The docking engagement sleeve is slidably connected to the shift gear on the docking gear. The docking engagement sleeve moves axially along the first transmission shaft to disconnect or connect with the output end of the synchronization component.

[0028] Compared with existing technologies, this technical solution has the following advantages:

[0029] 1. The planetary mechanism is a single-stage transmission, the gearbox is a two-stage transmission, and the whole system adopts a three-stage transmission to reduce mechanical losses and improve transmission efficiency.

[0030] 2. The planetary mechanism adopts a planetary gear shifting design with a large speed ratio, which effectively reduces the gear ratio in the subsequent gearbox, thereby reducing the gear weight and size and achieving a lightweight design.

[0031] 3. The high-speed rotating planetary mechanism directly drives the lubricating oil pump through the first transmission shaft, reducing the power transmission links, thereby reducing the loss of lubricating oil due to churning and improving the efficiency of the lubrication system.

[0032] 4. A four-speed transmission design is achieved based on a two-speed planetary mechanism and a two-speed gearbox, so that the output speed and torque of the motor can be flexibly adjusted according to different driving conditions and load requirements, so that the motor can give full play to its performance and improve power economy.

[0033] 5. The power output gear adopts a small speed ratio design, increasing the ground clearance of the entire electric drive axle. The planetary mechanism and gearbox have a compact structure, which significantly reduces the overall size of the transmission system and minimizes the space occupied between transmission components.

[0034] 6. Due to the reduction in the overall size of the transmission system, the number of internal components requiring lubrication and the space available are also reduced, thereby lowering the required amount of lubricating oil and operating costs.

[0035] The present invention will be further described below with reference to the accompanying drawings and embodiments. Attached Figure Description

[0036] Figure 1 This is an overall schematic diagram of the electric drive bridge described in this utility model;

[0037] Figure 2 This is a schematic diagram of the planetary structure of the electric drive bridge described in this utility model;

[0038] Figure 3 This is a schematic diagram of the gearbox of the electric drive axle described in this utility model.

[0039] In the picture:

[0040] 1. Motor; 11. Drive shaft of the motor; 2. Planetary gear mechanism; 21. First planetary gear set; 211. First sun gear; 212. First planetary gear; 22. Second planetary gear set; 221. Planetary output shaft; 222. Second sun gear; 223. Second ring gear; 224. Second planetary gear; 225. Second planetary carrier; 23. Synchronization assembly; 3. Gearbox; 31. First parallel shaft mechanism; 311. First drive shaft; 312. First gear set; 3121. Connecting assembly; 3122. Power take-off drive gear; 3123. First gear drive gear; 3124. Shifting assembly; 3125. Second gear drive gear; 32. Second parallel shaft mechanism; 321. Second drive shaft; 322. Second gear set; 3221. Power output gear; 3222. First gear driven gear; 3223. Second gear driven gear; 4. Differential; 5. Power take-off; 6. Oil pump. Detailed Implementation

[0041] The following description is intended to disclose the present invention so that those skilled in the art can implement it. The preferred embodiments described below are merely examples, and other obvious variations will occur to those skilled in the art. The basic principles of the present invention defined in the following description can be applied to other embodiments, modifications, improvements, equivalents, and other technical solutions that do not depart from the spirit and scope of the present invention.

[0042] like Figure 1 As shown, this utility model provides an electric drive axle, including: a motor 1, a planetary mechanism 2, and a gearbox 3;

[0043] The planetary mechanism 2 includes: a first planetary gear set 21 and a second planetary gear set 22; the first planetary gear set 21 is connected between the motor 1 and the second planetary gear set 22;

[0044] The first planetary gear set 21 includes: a first sun gear 211 and a first planet gear 212; the first sun gear 211 is connected to the motor 1, and the first sun gear 211 meshes with the first planet gear 212;

[0045] The second planetary gear set 22 includes: a planetary output shaft 221, a second sun gear 222, a second ring gear 223, second planet gears 224, and a second planet carrier 225; the second sun gear 222 is fixedly sleeved on the planetary output shaft 221; the second ring gear 223 and the second sun gear 222 are concentrically arranged; all the second planet gears 224 are meshed between the second sun gear 222 and the second ring gear 223; the second planet carrier 225 is fixedly connected to all the second planet gears 224; the input end of the second planet carrier 225 passes through the second planet gears 224 in sequence; the second planet gears 224 are away from the output end of the second planet carrier 225;

[0046] The gearbox 3 includes at least one parallel shaft mechanism; one end of the parallel shaft mechanism is the input end of the gearbox 3; the input end of the gearbox 3 is connected to the second planetary carrier 225 or the planetary output shaft 221 respectively under the action of the docking assembly 3121.

[0047] Specifically, the electric drive axle includes: motor 1, planetary mechanism 2, gearbox 3, differential 4, power take-off 5, and oil pump 6.

[0048] Motor 1 is used to provide power and outputs the power through the motor's drive shaft 11.

[0049] In a preferred embodiment, motor 1 has a rated power of 150kW, a peak power of 252kW, a rated torque of 285Nm, a peak torque of 550Nm, a maximum speed of 6000rpm, and is matched with an electronic control specification of 600A / 800A.

[0050] The planetary mechanism 2 is a two-stage planetary gear design. Specifically, the planetary mechanism 2 includes a first planetary gear 21, a second planetary gear 22, and a synchronization component 23. The first planetary gear 21 is connected between the motor 1 and the second planetary gear 22; the second planetary gear 22 is located between the first planetary gear 21 and the synchronization component 23.

[0051] The first planetary gear set 21 includes a first sun gear 211 and a first planet gear 212. The first sun gear 211 is fixedly connected to the drive shaft 11 of the motor; the first sun gear 211 meshes with the first planet gear 212.

[0052] The second planetary gear set 22 includes: planetary output shaft 221, second sun gear 222, second ring gear 223, second planetary gear 224, and second planetary carrier 225.

[0053] The planetary output shaft 221 is fixedly fitted with a second sun gear 222; the second ring gear 223 and the second sun gear 222 are concentrically arranged; the second ring gear 223 is fixed in the housing of the gearbox 3, forming the fixed internal ring gear of the planetary gear train. All the second planet gears 224 mesh between the second sun gear 222 and the second ring gear 223, that is, the second planet gears 224 are externally meshed with the second sun gear 222, and internally meshed with the second ring gear 223, to achieve power splitting. The input end of the second planet carrier 225 is fixedly connected to all the second planet gears 224; the input end of the second planet carrier 225 passes through the second planet gears 224 in sequence; the second planet gears 224 are away from the output end of the second planet carrier 225. The number of first planet gears 212 is not greater than the number of second planet gears 224.

[0054] Synchronization component 23 is one of the actuators used for gear shifting. Synchronization component 23 is mounted on planetary output shaft 221 and is located between second sun gear 222 and gearbox 3.

[0055] In a preferred embodiment, the input end of the synchronizing assembly 23 is provided with a spline or clutch structure, which can be selectively connected to the planetary output shaft 221 or the second planetary carrier 225 to facilitate the transmission of power to the gearbox 3. That is, through the connection of the synchronizing assembly 23 to the planetary output shaft 221 or the second planetary carrier 225, the gearbox 3 can selectively engage with either the second sun gear 222 or the second planetary carrier 225 based on the synchronizing assembly 23 to obtain power from the second sun gear 222 or the second planetary gear 224, thereby realizing gear shifting operation.

[0056] Specifically, when a shift command is received, the input of the synchronization component 23 can be selectively aligned with either the first shift position or the second shift position; the first shift position corresponds to the planetary output shaft 221; and the second shift position corresponds to the output of the second planetary carrier 225.

[0057] Understandably, if the input end of the synchronization component 23 is aligned with the first shift position, then upon receiving a clutch engagement command, the input end of the synchronization component 23 is connected to the planetary output shaft 221 to obtain the power output from the second sun gear 222, and transmits this power to the gearbox 3 via the synchronization component 23. At this time, the electric drive output relationship is as follows: motor drive shaft 11 → first sun gear 211 → first planetary gear 212 → second planetary gear 224 → second sun gear 222 → planetary output shaft 221 → synchronization component 23 → gearbox 3.

[0058] If the input end of the synchronizing component 23 is aligned with the second shift position, then upon receiving a clutch engagement command, the input end of the synchronizing component 23 is connected to the second planetary carrier 225 to obtain the power output from the second planetary gear 224, and transmits this power to the gearbox 3 via the synchronizing component 23. At this time, the electric drive output relationship is as follows: motor drive shaft 11 → first sun gear 211 → first planetary gear 212 → second planetary gear 224 → second planetary carrier 225 → synchronizing component 23 → gearbox 3.

[0059] This utility model adopts a high-ratio NW planetary gear shifting design, and uses a combination design of double planetary gears (first planetary gear 21 and second planetary gear 22) and synchronization component 23 to realize power splitting and gear shifting functions, effectively reducing the gear ratio in the subsequent gearbox 3, thereby reducing gear weight and size, and achieving lightweight design.

[0060] The gearbox 3 is a two-speed parallel shaft design, including one input end and at least one output end.

[0061] The gearbox 3 is connected in series with the planetary mechanism 2, and the speed ratio is further amplified through a two-speed gear pair, ultimately achieving four-speed output. Specifically, the gearbox 3 includes: a first parallel shaft mechanism 31 and a second parallel shaft mechanism 32.

[0062] The first parallel shaft mechanism 31 and the second parallel shaft mechanism 32 are arranged side by side; the first parallel shaft mechanism 31 is located between the power take-off 5 and the second parallel shaft; the second parallel shaft mechanism 32 is located between the first parallel shaft mechanism 31 and the differential 4.

[0063] The first parallel shaft mechanism 31 includes: a first transmission shaft 311 and a first gear set 312.

[0064] The first drive shaft 311 is coaxially arranged with the planetary output shaft 221.

[0065] The first gear set 312 is arranged on the first drive shaft 311; the first gear set 312 includes, in sequence: docking assembly 3121, power take-off drive gear 3122, first gear drive gear 3123, shifting assembly 3124, and second gear drive gear 3125.

[0066] The docking assembly 3121, the power take-off drive gear 3122, the first gear drive gear 3123, the shifting assembly 3124, and the second gear drive gear 3125 are arranged sequentially at intervals on the first transmission shaft 311; the docking assembly 3121 is close to the planetary mechanism 2. The output end of the docking assembly 3121, the power take-off drive gear 3122, and the input end of the shifting assembly 3124 are fixedly sleeved on the first transmission shaft 311; the first gear drive gear 3123 and the second gear drive gear 3125 are loosely sleeved on the first transmission shaft 311.

[0067] In a preferred embodiment, the docking assembly 3121 is used to perform power disconnection / connection between the planetary mechanism 2 and the gearbox 3. The docking assembly 3121 includes a docking gear and a docking engagement sleeve.

[0068] The docking sleeve is the input end of the docking assembly 3121, and the docking gear is the output end of the docking assembly 3121. The docking gear is fixedly sleeved on the input end of the first drive shaft 311. The docking sleeve is slidably sleeved on the shift gear; the docking sleeve can slide along the axial direction of the first drive shaft 311 to disconnect or connect with the output end of the synchronization assembly 23, thereby completing the power input switching.

[0069] Specifically, upon receiving a clutch disengagement command, the mating engagement sleeve moves along the first drive shaft 311 in a direction away from the planetary mechanism 2 to disconnect the mating engagement sleeve from the output end of the synchronization component 23, thereby separating the planetary structure from the gearbox 3 and allowing the shifting component 3124 to freely switch gears.

[0070] Upon receiving the clutch engagement command, the mating engagement sleeve moves along the first drive shaft 311 toward the planetary mechanism 2 so that the mating engagement sleeve engages with the output end of the synchronization component 23, thereby transmitting power to the wheels via the planetary mechanism 2 and the gearbox 3.

[0071] In a preferred embodiment, the shift assembly 3124 is one of the actuating components for gear switching. The shift assembly 3124 includes a shift gear and a gear engagement sleeve.

[0072] The shift gear is the input end of the shift assembly 3124, and the gear engagement sleeve is the output end of the shift assembly 3124.

[0073] The shift gear is fixedly sleeved on the first drive shaft 311; the shift engagement sleeve is slidably sleeved on the shift gear; the shift engagement sleeve moves axially along the first drive shaft 311 to engage with the first drive gear 3123 or the second drive gear 3125 to achieve two-speed shifting. That is, when a shift command is received, the shift fork pushes the shift engagement sleeve to move along the first drive shaft 311 to mesh with the first drive gear 3123 or the second drive gear 3125.

[0074] In a preferred embodiment, the power take-off drive gear 3122 is sleeved on the first drive shaft 311 and located between the docking assembly 3121 and the first drive gear 3123. The power take-off drive gear 3122 serves as one of the output ends of the first parallel shaft mechanism 31 and is connected to the power take-off unit 5. Specifically, a third drive shaft is provided, which is parallel to the first drive shaft 311. A power take-off driven gear is fixedly sleeved on the third drive shaft, and the power take-off driven gear meshes with the power take-off drive gear 3122. The third drive shaft is connected to the power take-off unit 5 for power take-off from external equipment.

[0075] In a preferred embodiment, the output end of the first drive shaft 311 serves as one of the output ends of the first parallel shaft mechanism 31, and is fixedly connected to the oil pump 6. Its high-speed rotating planetary mechanism 2 directly drives the lubricating oil pump 6 via the first drive shaft 311, avoiding the problems of excessive power transmission links and significant energy loss that may occur with traditional motor drives. This reduces energy loss during the agitation of the lubricating oil and improves the efficiency of the lubrication system. Furthermore, through lubrication simulation and a reasonable housing lubrication design, the required amount of lubricating oil is effectively reduced, the lubrication effect on gears and bearings is improved, transmission efficiency is increased, and operating costs are reduced.

[0076] The second parallel shaft mechanism 32 includes: a second transmission shaft 321 and a second gear set 322;

[0077] The second drive shaft 321 is parallel to the first drive shaft 311; understandably, the second drive shaft 321 is parallel to the planetary output shaft 221.

[0078] The second gear set 322 is fixedly mounted on the second transmission shaft 321; the second gear set 322 includes, in sequence: a power output gear 3221, a first gear driven gear 3222, and a second gear driven gear 3223.

[0079] The power output gear 3221, the first gear driven gear 3222, and the second gear driven gear 3223 are arranged sequentially and at intervals on the second transmission shaft 321; wherein the power output gear 3221, the first gear driven gear 3222, and the second gear driven gear 3223 are fixedly sleeved on the second transmission shaft 321.

[0080] The first-gear drive gear 3123 meshes with the first-gear driven gear 3222, and the second-gear drive gear 3125 meshes with the second-gear driven gear 3223, facilitating the transmission of power during gear shifting. The power output gear 3221 meshes with the differential 4 to output power to the wheels. The power output gear 3221 employs a small gear ratio design, resulting in a relatively small diameter. This design, while ensuring power transmission, allows for more space under the electric drive axle, effectively increasing the ground clearance of the entire electric drive axle.

[0081] The gearbox 3 selects to engage with either the first gear drive gear 3123 or the second gear drive gear 3125 via the shift assembly 3124 to achieve gear shifting.

[0082] When the shift fork pushes the gear engagement sleeve to move so that it engages with the first gear drive gear 3123, the power of the planetary mechanism 2 is transmitted to the power output gear 3221 via the first gear drive gear 3123.

[0083] Understandably, the shift gears drive the first gear drive gear 3123 to rotate based on the gear engagement sleeve. Since the first gear drive gear 3123 meshes with the first gear driven gear 3222, the first gear drive gear 3123 can drive the first gear driven gear 3222 to rotate; thereby driving the second drive shaft 321 to rotate, and then the second drive shaft 321 drives the power output gear 3221 to rotate; the power output gear 3221 is connected to the differential 4; since the second drive shaft 321 also drives the second gear driven gear 3223 to rotate, and the second gear driven gear 3223 meshes with the second gear drive gear 3125, at this time, the second gear driven gear 3223 drives the second gear drive gear 3125 to idle. Its electric drive output relationship is: planetary mechanism 2 → docking assembly 3121 → first drive shaft 311 → shift assembly 3124 → first gear drive gear 3123 → first gear driven gear 3222 → second drive shaft 321 → power output gear 3221.

[0084] When the shift fork pushes the gear engagement sleeve to move so that it engages with the second gear drive gear 3125, the power of the planetary mechanism 2 is transmitted to the power output gear 3221 via the second gear drive gear 3125.

[0085] Understandably, the shift gear drives the second-gear drive gear 3125 to rotate based on the gear engagement sleeve. Since the second-gear drive gear 3125 meshes with the second-gear driven gear 3223, it can drive the second-gear driven gear 3223 to rotate, thereby driving the second transmission shaft 321 to rotate. The second transmission shaft 321 then drives the power output gear 3221 to rotate; the power output gear 3221 is connected to the differential 4. At this time, since the second transmission shaft 321 also drives the first-gear driven gear 3222 to rotate, and the first-gear driven gear 3222 meshes with the second-gear drive gear 3125, the first-gear driven gear 3222 drives the first-gear drive gear 3123 to idle. Electric drive output relationship: Planetary mechanism 2 → docking assembly 3121 → first transmission shaft 311 → shift assembly 3124 → second-gear drive gear 3125 → second-gear driven gear 3223 → second transmission shaft 321 → power output gear 3221.

[0086] The shaft system of this utility model adopts a parallel arrangement (planetary mechanism 2 and gearbox 3 are coaxial), combined with a compact gear pair design, which can adapt to the chassis layout requirements of different vehicle models and has strong expandability. By rationally arranging the shaft system according to the overall vehicle space and supplementing it with a mechanical oil pump, the weight and size of the transmission system can be effectively reduced, the system rigidity can be improved, and the lubrication effect and NVH performance can be optimized.

[0087] The existing design uses a 4-stage transmission. Its motor parameters include: rated power 150kW, peak power 252kW, rated torque 285Nm, peak torque 550Nm, maximum speed 10000rpm, matching electrical control cabinet specification 600A, main gearbox speed ratio: two gears 20.02 / 10.23; auxiliary gearbox planetary gear ratio 3.55 / 1. Its gear parameters are shown in Table 1.

[0088]

[0089] (Table 1)

[0090] The planetary mechanism 2 and the gearbox 3 of this invention are both two-speed transmissions. Therefore, the electric drive axle of this invention can achieve a four-speed transmission design, which allows for flexible adjustment of the motor's output speed and torque according to different driving conditions and load requirements, enabling the motor to fully utilize its performance and improve power economy. The parameters of each gear are shown in Table 2.

[0091]

[0092] (Table 2)

[0093] Based on the existing design and the gear parameters of this utility model, it can be seen that this utility model adopts a 3-stage transmission (the planetary mechanism is the 1st stage transmission and the gearbox is the 2nd stage transmission). By reasonably allocating the speed ratio and load of each stage of transmission, the power transmission path is optimized, the energy loss in the power transmission process is reduced, thereby effectively reducing mechanical losses and significantly improving transmission efficiency.

[0094] The following is a brief description of the gear shifting process:

[0095] When the user depresses the clutch, a clutch disengagement command is received; based on the clutch disengagement command, the connection between planetary mechanism 2 and gearbox 3 is disconnected; according to the user's shifting operation, shifting commands are received; these shifting commands include: first gear command, second gear command, third gear command, and fourth gear command. When the user releases the clutch, a clutch engagement command is received; based on the clutch engagement command, the connection between planetary mechanism 2 and gearbox 3 is restored, completing gear locking.

[0096] Specifically, when a first gear command is received, the synchronization component 23 aligns with the first shift position (aligns with the planetary output shaft 221), and the shift fork pushes the gear engagement sleeve (to the right) to engage with the first gear drive gear 3123; when a clutch engagement command is received, the electric drive output relationship is as follows: motor drive shaft 11 → first-stage drive gear → first-stage driven gear → second planetary gear 224 → second sun gear 222 → planetary output shaft 221 → synchronization component 23 → engagement component 3121 → first transmission shaft 311 → shift component 3124 → first gear drive gear 3123 → first gear driven gear 3222 → second transmission shaft 321 → power output gear 3221 → differential 4.

[0097] When a second gear command is received, the synchronization component 23 aligns with the first shift position (aligns with the planetary output shaft 221), and the shift fork pushes the gear engagement sleeve (to the left) to engage with the second gear drive gear 3125, thus achieving the engagement of the shift gear and the second gear drive gear 3125. When a clutch engagement command is received, the electric drive output relationship is as follows: motor drive shaft 11 → first-stage drive gear → first-stage driven gear → second planetary gear 224 → second sun gear 222 → planetary output shaft 221 → synchronization component 23 → engagement component 3121 → first transmission shaft 311 → shift component 3124 → second gear drive gear 3125 → second gear driven gear 3223 → second transmission shaft 321 → power output gear 3221 → differential 4.

[0098] When a third gear command is received, the synchronization component 23 aligns with the second shift position (aligns with the second planetary carrier 225), and the shift fork pushes the gear engagement sleeve (to the right) to engage with the first gear drive gear 3123, thus achieving the engagement of the shift gear and the first gear drive gear 3123. When a clutch engagement command is received, the electric drive output relationship is as follows: motor drive shaft 11 → first-stage drive gear → first-stage driven gear → second planetary gear 224 → second planetary carrier 225 → synchronization component 23 → docking component 3121 → first transmission shaft 311 → shift component 3124 → first gear drive gear 3123 → first gear driven gear 3222 → second transmission shaft 321 → power output gear 3221 → differential 4.

[0099] When a fourth gear command is received, the synchronization component 23 aligns with the second shift position (aligns with the second planetary carrier 225), and the shift fork pushes the gear engagement sleeve (to the left) to mesh with the second gear drive gear 3125, thus achieving the engagement of the shift gear and the second gear drive gear 3125. When a clutch engagement command is received, the electric drive output relationship is as follows: motor drive shaft 11 → first-stage drive gear → first-stage driven gear → second planetary gear 224 → second planetary carrier 225 → synchronization component 23 → docking component 3121 → first transmission shaft 311 → shift component 3124 → second gear drive gear 3125 → second gear driven gear 3223 → second transmission shaft 321 → power output gear 3221 → differential 4.

[0100] The above embodiments are only used to illustrate the technical ideas and features of this utility model. Their purpose is to enable those skilled in the art to understand the content of this utility model and implement it accordingly. The scope of patent application of this utility model should not be limited by these embodiments. That is, any equivalent changes or modifications made in accordance with the spirit disclosed in this utility model still fall within the patent scope of this utility model.

Claims

1. An electrically driven axle, characterized in that include: Electric motor (1), planetary mechanism (2) and gearbox (3); The planetary mechanism (2) includes: a first planetary gear set (21) and a second planetary gear set (22); the first planetary gear set (21) is connected between the motor (1) and the second planetary gear set (22); The first planetary gear set (21) includes a first sun gear (211) and a first planet gear (212); the first sun gear (211) is connected to the motor (1), and the first sun gear (211) meshes with the first planet gear (212); The second planetary gear set (22) includes: a planetary output shaft (221), a second sun gear (222), a second ring gear (223), second planet gears (224), and a second planet carrier (225); the second sun gear (222) is fixedly sleeved on the planetary output shaft (221); the second ring gear (223) and the second sun gear (222) are concentrically arranged; all the second planet gears (224) are meshed between the second sun gear (222) and the second ring gear (223); the second planet carrier (225) is fixedly connected to all the second planet gears (224); the input end of the second planet carrier (225) passes through the second planet gears (224) in sequence; the second planet gears (224) are away from the output end of the second planet carrier (225); The gearbox (3) includes at least one parallel shaft mechanism; one end of the parallel shaft mechanism is the input end of the gearbox (3); the input end of the gearbox (3) is connected to the second planetary carrier (225) or the planetary output shaft (221) respectively under the action of the docking assembly (3121).

2. An electric drive axle as in claim 1, wherein, The gearbox (3) includes: a first parallel shaft mechanism (31) and a second parallel shaft mechanism (32); The first parallel shaft mechanism (31) and the second parallel shaft mechanism (32) are arranged side by side; the second parallel shaft mechanism (32) is located between the first parallel shaft mechanism (31) and the differential (4).

3. An electrically variable drive axle as in claim 2, wherein: The first parallel shaft mechanism (31) includes: a first transmission shaft (311) and a first gear set (312); The first drive shaft (311) is coaxially arranged with the planetary output shaft (221); The first gear set (312) is arranged on the first transmission shaft (311); the first gear set (312) includes, in sequence: a docking assembly (3121), a first gear drive gear (3123), a shifting assembly (3124), and a second gear drive gear (3125); the output end of the docking assembly (3121) and the input end of the shifting assembly (3124) are fixedly sleeved on the first transmission shaft (311); the first gear drive gear (3123) and the second gear drive gear (3125) are loosely sleeved on the first transmission shaft (311).

4. An electrically variable drive axle as in claim 3, wherein: The shift assembly (3124) includes: a shift gear and a gear engagement sleeve; The shift gear is fixedly sleeved on the first transmission shaft (311); the gear engagement sleeve is slidably sleeved on the shift gear; the shift engagement sleeve moves axially along the first transmission shaft (311) to engage with the first gear drive gear (3123) or the second gear drive gear (3125).

5. An electric drive axle as in claim 3, wherein, The second parallel shaft mechanism (32) includes: a second transmission shaft (321) and a second gear set (322); The second drive shaft (321) is parallel to the first drive shaft (311); The second gear set (322) is fixedly mounted on the second transmission shaft (321); the second gear set (322) includes, in sequence: a power output gear (3221), a first driven gear (3222), and a second driven gear (3223).

6. An electrically variable drive axle as in claim 5, wherein: The first gear drive gear (3123) meshes with the first gear driven gear (3222); the second gear drive gear (3125) meshes with the second gear driven gear (3223); the power output gear (3221) meshes with the differential (4).

7. An electric drive axle as in claim 3, wherein, The first gear set (312) further includes: a power take-off drive gear (3122); The power take-off drive gear (3122) is sleeved on the first transmission shaft (311) and located between the docking assembly (3121) and the first drive gear; the power take-off drive gear (3122) meshes with the power take-off device (5).

8. An electric drive axle as in claim 1, wherein, The output end of the first drive shaft (311) is fixedly connected to the oil pump (6).

9. An electric drive bridge as described in claim 1, characterized in that, The planetary mechanism (2) also includes: a synchronization component (23); The input of the synchronization component (23) can be selectively aligned with a first shift position or a second shift position; the first shift position corresponds to the planetary output shaft (221); the second shift position corresponds to the output of the second planetary carrier (225).

10. An electrically variable drive axle as in claim 9, wherein, The docking assembly (3121) includes: a docking gear and a docking sleeve; The docking gear is fixedly sleeved on the first transmission shaft (311), and the docking engagement sleeve is slidably connected to the shift gear on the docking gear. The docking engagement sleeve moves axially along the first transmission shaft (311) to disconnect or connect with the output end of the synchronization component (23).

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