Electrically-driven planetary transmission with electromagnetic gear shifting function

Abstract

The electrically-driven planetary transmission with the electromagnetic gear shifting function comprises a motor, a double-brake electromagnetic brake and a two-stage planetary reducer which are sequentially connected, a first sun gear of a first planetary reducer is connected with the motor, and a first planet carrier is meshed with a second sun gear; the spline gear sleeve movably sleeves a spline shaft of the first sun gear, is connected with a first dynamic friction plate of the first electromagnetic brake and is used for braking and releasing the first sun gear; and the spline gear disc is arranged on a first inner gear ring of the first planetary gear reducer, is connected with a second dynamic friction plate of the second electromagnetic brake and a first static friction plate of the first electromagnetic brake, and is used for braking and releasing the first inner gear ring. According to the transmission, three-gear working state switching is achieved through the double-brake electromagnetic brake and the two-stage planetary reducer, and the requirements of a low-speed large-torque load-bearing walking working condition in a load state, a high-speed small-torque rapid transition working condition in a no-load state and a neutral state working condition are met respectively.

Description

Technical Field

[0001] The invention relates to a transmission, in particular to an electrically driven planetary transmission with an electromagnetic shifting function. Background Art

[0002] With the breakthrough and rapid development of new energy batteries, motors, motor controllers and other technologies, the field of non-road new energy vehicles such as logistics transport vehicles, intelligent AGVs, and aerial work vehicles has been rapidly developed. The characteristics of industrial vehicles such as logistics transport vehicles, intelligent AGVs, and aerial work vehicles are that they often switch between loaded and unloaded states during work. The vehicle curb weight in the loaded state is heavy, and it completes the functions of carrying, transferring, and lifting heavy objects. The unloaded state often requires the vehicle's off-board walking drive to achieve rapid workplace transfer, shorten the invalid work time interval, and improve work efficiency. The function of the vehicle determines that the curb weight in the loaded state is greatly different from the curb weight in the unloaded state. Therefore, the loaded state requires the vehicle's off-board walking drive to achieve low-speed high-torque power output to meet the load requirements, and the unloaded state requires the vehicle's off-board walking drive to achieve high-speed low-torque power output. The existing technology realizes the electric drive parallel shaft gear or planetary gear transmission reducer that realizes the off-board walking drive function. In order to ensure the power output requirements of the loaded state, a parallel shaft gear or planetary gear transmission with a fixed transmission ratio is used, which cannot meet the requirements of the load and walking speed of the two working conditions at the same time. Summary of the invention

[0003] In order to solve the above problems, the present invention provides an electrically driven planetary transmission with an electromagnetic shifting function, and the specific technical solution is as follows:

[0004] An electrically driven planetary transmission with an electromagnetic shifting function comprises: a motor; a dual-braking electromagnetic brake, arranged on the motor, comprising a first electromagnetic brake and a second electromagnetic brake; a two-stage planetary reducer, arranged on the dual-braking electromagnetic brake, comprising a first planetary gear reducer and a second planetary gear reducer, the first sun gear of the first planetary gear reducer being connected to the motor, and the first planet carrier of the first planetary gear reducer being meshed with the second sun gear of the second planetary gear reducer; a spline gear sleeve, a movable sleeve being arranged on the spline shaft of the first sun gear and connected to the first dynamic friction plate of the first electromagnetic brake, for braking and releasing the first sun gear; and a spline gear plate, arranged on the first inner gear ring of the first planetary gear reducer, and connected to the second dynamic friction plate of the second electromagnetic brake and the first static friction plate of the first electromagnetic brake, for braking and releasing the first inner gear ring.

[0005] Preferably, the first planetary gear reducer further includes: a first planetary wheel, which is rotatably disposed on the first planet carrier and meshes with the first sun gear and the first inner ring gear.

[0006] Preferably, the second planetary gear reducer also includes: a second planetary wheel, which is meshed with the second sun gear; a second planetary carrier, which is rotatably connected to the second planetary wheel and the first inner ring gear, and the second planetary carrier is used to connect equipment; and a second inner ring gear, which is meshed with the second planetary wheel and rotatably arranged on the second planetary carrier, and the second inner ring gear is used to connect wheels.

[0007] Preferably, the two-stage planetary reducer also includes: a third oil seal, which is arranged on the second inner gear ring and movably abuts against the second planetary carrier; and a protective cover plate, which is arranged on the second inner gear ring and abuts against one end of the third oil seal.

[0008] Furthermore, the two-stage planetary reducer also includes: a water seal, which is arranged on the second planetary carrier and movably rests on the protective cover plate.

[0009] Preferably, the two-stage planetary reducer further includes: a second oil seal, which is arranged on the second planetary carrier and movably abuts against the first inner gear ring.

[0010] Preferably, the first electromagnetic brake also includes: a brake housing, which is respectively connected to the motor and the second planetary carrier of the second planetary gear reducer; a first brake excitation coil, which is arranged in the first brake excitation coil; a first brake spring, which is arranged in the brake housing; a first armature plate, which is axially movably arranged in the brake housing and abuts against the first brake spring, and the first armature plate is also arranged opposite to the first brake excitation coil; a pressure plate, which is rotatably arranged on the first armature plate; a first dynamic friction plate, which is axially movably arranged on one side of the pressure plate, and a sliding sleeve is arranged on the spline gear sleeve, and the first dynamic friction plate rotates synchronously with the spline gear sleeve; wherein, the first static friction plate is arranged between the first dynamic friction plates.

[0011] Preferably, the second electromagnetic brake also includes: a second brake excitation coil, which is arranged in the brake housing; a second brake spring, which is arranged in the brake housing; a second armature plate, which is axially movably arranged in the brake housing and abuts against the second brake spring, and the second armature plate is also arranged opposite to the second brake excitation coil; a second moving friction plate, which is movably sleeved on the spline gear plate, and the second moving friction plate rotates synchronously with the spline gear plate; a second static friction plate, which is axially movably arranged between the second moving friction plates; and a friction plate, which is arranged in the brake housing and opposite to the second moving friction plate.

[0012] Furthermore, the second electromagnetic brake further comprises: a height-equalizing column fixedly disposed in the brake housing, and the second armature disc and the second static friction plate are both slidably inserted into the height-equalizing column.

[0013] Preferably, it also includes: a transition flange seat, which is connected to the motor and the dual-brake electromagnetic brake respectively.

[0014] Compared with the prior art, the present invention has the following beneficial effects:

[0015] An electrically driven planetary transmission with electromagnetic shifting function provided by the present invention realizes three-speed working state switching through a dual-braking electromagnetic brake and a two-stage planetary reducer. The first gear operation meets the working conditions of low speed and high torque under load state of the machine equipment; the second gear operation meets the working conditions of high speed and small torque and rapid transition of the machine equipment under no-load state; the neutral state operation meets the working conditions of higher speed towing of the machine equipment or fault towing and towing. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is a stereogram of the present application;

[0017] Figure 2 is a cross-sectional view of the present application;

[0018] Figure 3 is an exploded view of this application;

[0019] Figure 4 It is an exploded view of a double-brake electromagnetic brake;

[0020] Figure 5 is a cross-sectional view of a double-braking electromagnetic brake;

[0021] Figure 6 It is an exploded diagram of a two-stage planetary gear reducer;

[0022] Figure 7It is a cross-sectional view of a two-stage planetary gear reducer;

[0023] Figure 8 It is the principle diagram of this application.

[0024] In the figure: 1-reluctance synchronous motor, 2-first O-ring, 3-transition flange seat, 4-double brake electromagnetic brake, 5-two-stage planetary reducer, 6-brake housing, 7-second O-ring, 8-third O-ring, 9-second electromagnetic brake excitation coil, 10-second armature plate, 11-equal height column, 12-second dynamic friction plate, 13-second static friction plate, 15-friction plate, 16-first dynamic friction plate, 17-first static friction plate, 18-spline gear sleeve, 20-pressure plate, 21-second bearing, 22-second brake spring, 23-locating pin, 25-first armature plate, 26-first brake spring, 27-first retaining ring, 28-first bearing, 29-first electromagnetic brake excitation coil, 30-first sun gear, 31-flat key, 32-spline gear plate, 33-first planetary gear shaft, 3 4-first planetary gear, 35-first planetary gear bearing, 36-first planetary carrier, 37-first inner gear ring, 38-second oil seal, 39-fourth bearing, 40-second inner gear ring, 41-sixth bearing, 42-fifth bearing, 43-second planetary gear bearing, 44-second planetary gear, 45-seventh bearing, 46-fourth O-ring, 47-second retaining ring, 48-third retaining ring, 49-second planetary gear shaft, 50-end cover, 51-fourth retaining ring, 52-second sun gear, 53-thrust washer, 54-second planetary carrier, 55-third oil seal, 56-protective cover plate, 57-water seal, 58-fifth retaining ring, 59-fifth O-ring, 60-sixth O-ring, 61-fixed, 62-third bearing, 63-first oil seal, 401-first electromagnetic brake, 402-second electromagnetic brake. DETAILED DESCRIPTION

[0025] The present invention will be further described with reference to the accompanying drawings.

[0026] like Figures 1 to 8As shown, an electric drive planetary transmission with electromagnetic shifting function includes a motor 1, a double-brake electromagnetic brake 4 and a two-stage planetary reducer 5. The motor 1 is installed on the double-brake electromagnetic brake 4 through a transition flange seat 3, and is rotatably connected to the first sun gear 30 through the spline inside the motor shaft; the double-brake electromagnetic brake housing 6 is rigidly installed on the two-stage planetary transmission reducer 5 through screws 19; a first bearing 28 is installed in the inner hole of the double-brake electromagnetic brake housing 6, and the first bearing 28 serves as the front support bearing of the motor 1; the first electromagnetic brake 401 of the double-brake electromagnetic brake 4 realizes the braking and releasing functional states of the first sun gear 30 through the first static friction plate 17, the first dynamic friction plate 16 and the spline gear sleeve 18; the second electromagnetic brake 402 of the double-brake electromagnetic brake 4 realizes the braking and releasing functional states of the first inner gear ring 37 through the second static friction plate 13, the second dynamic friction plate 12 and the spline gear plate 32 rigidly connected to the first inner gear ring 37; the first sun gear 30 shaft A first oil seal 63 and a third bearing 62 are provided; the first planetary carrier 36 is floatingly rotatably connected to the first inner gear ring 37, and the fourth bearing 39, the fifth bearing 42 and the second oil seal 38 are installed on the first inner gear ring 37; the first planetary carrier 36 is rotatably connected to the first planetary gear 34, and the first planetary carrier 36 is connected to the second sun gear 52 through an internal spline, and the outer rings of the fourth bearing 39, the fifth bearing 42 and the second oil seal 38 are fixedly installed on the second planetary carrier 54, and the second planetary carrier 54 is a fixed component and is installed on the machine equipment through a flange; the second planetary gear 44 is rotatably connected to the second planetary carrier 54; the sixth bearing 41 and the seventh bearing 45 are installed on the second planetary carrier 54, and the outer rings of the sixth bearing 41 and the seventh bearing 45 are installed in the inner hole of the second inner gear ring 40; the second inner gear ring 40 is a rotating component and is rotatably connected to the wheel of the machine equipment through a flange.

[0027] The dual-brake electromagnetic brake 4 is integrated between the motor 1 and the two-stage planetary reducer 5. The first O-ring 2, the second O-ring 7, the third O-ring 8 and the sixth O-ring 60 are installed between the joint surfaces of the motor 1, the transition flange seat 3, the brake housing 6 and the second planetary carrier 54.

[0028] The brake housing 6 is provided with a first electromagnetic brake 401 and a second electromagnetic brake 402. The brake housing 6 is respectively connected to the transition flange seat 3 and the second planetary carrier 54. The brake housing 6 is filled with glue to insulate and seal and is provided with a first brake excitation coil 29 and a second brake excitation coil 9. The brake housing 6 is provided with a spring mounting hole, on which a first brake spring 26 and a second brake spring 22 are respectively installed. The spring force of the first brake spring 26 acts on the first armature disk 25, and the spring force of the second brake spring 22 acts on the second armature disk 10. The first armature disk 25 can make axial reciprocating motion under the alternating action of the electromagnetic force of the first brake spring 26 and the first brake excitation coil 29, and the second armature disk 10 can make axial reciprocating motion under the alternating action of the electromagnetic force of the second brake spring 22 and the second brake excitation coil 9.

[0029] A second bearing 21 is installed in the inner hole of the first armature plate 25, a pressure plate 20 is installed on the inner ring of the second bearing 21, and a first retaining ring 27 is arranged on the outer diameter of the pressure plate 20 to prevent the second bearing 21 from coming out. The first armature plate 25 and the pressure plate 20 can withstand axial compression force, and the pressure plate 20 can freely rotate concentrically relative to the first armature plate 25 and cannot be axially separated. A positioning pin 23 and a fixing screw 24 are installed in the pin hole of the first armature plate 25. The first armature plate 25 can move axially but cannot rotate. An inner spline tooth groove is arranged in the inner hole of the first dynamic friction plate 16 to cooperate with the outer spline teeth of the spline gear sleeve 18. The outer diameter of the first static friction plate 17 is provided with spline outer teeth and is installed in the inner hole of the spline gear plate 32. In the spline tooth groove, the inner hole of the spline gear sleeve 18 matches the axial diameter of the first sun gear 30 and is connected by a flat key 31. The first brake spring 26 transmits the clamping force to the first static friction plate 17 and the first dynamic friction plate 16 through the first armature plate 25, the second bearing 21 and the pressure plate 20, locking the relative rotation between the first sun gear 30 and the spline gear plate 32, that is, the first inner gear ring 37. The first brake excitation coil 29 is energized to generate electromagnetic force to pull the first armature plate 25 to overcome the clamping force of the first brake spring 26 while completing the separation of the first static friction plate 17 and the first dynamic friction plate 16. The first sun gear 30 can rotate freely relative to the spline gear plate 32, that is, the first inner gear ring 37.

[0030] A height column 11 is installed in the pin hole of the second armature plate 10, one end face of the height column 11 is in contact with the brake housing 6, and the other end face is in contact with the friction plate 15. The friction plate 15 is rigidly connected to the brake housing 6 and the height column 11 through a screw 14. The height column 11 is installed in the pin hole of the second static friction plate 13 and the second armature plate 10 at the same time. The second static friction plate 13 and the second armature plate 10 can both move axially but cannot rotate. An internal spline tooth groove is provided in the inner hole of the second dynamic friction plate 12 to cooperate with the external spline teeth of the spline gear plate 32. The second brake spring 22 transmits the clamping force to the second dynamic friction plate 12 and the second static friction plate 13 through the second armature plate 10 to lock the rotational freedom of the first inner gear ring 37. The second brake excitation coil 9 generates an electromagnetic force in the energized state to pull the second armature plate 10 to overcome the clamping force of the second brake spring 22 while completing the separation action of the second dynamic friction plate 12 and the second static friction plate 13, so that the first inner gear ring 37 has rotational freedom.

[0031] The first sun gear 30 is rotatably installed in the inner ring of the third bearing 62, and is provided with a first oil seal 63. The third bearing 62 and the first oil seal 63 are installed in the inner hole of the spline gear plate 32. The first planetary gear shaft 33 is installed on the first planetary carrier 36. The first planetary gear bearing 35 is installed in the inner hole of the first planetary gear 34. The first planetary gear bearing 35 is rotatably installed on the first planetary gear shaft 33. The first planetary gear 34 is meshed with the inner and outer teeth of the first inner gear ring 37 for transmission. The fourth bearing 39, the fifth bearing 42 and the second oil seal 38 are installed on the outer diameter of the first inner gear ring 37. The fourth bearing 39, the fifth bearing 42 and the second oil seal 38 are installed in the inner hole of the second planetary carrier 54. The fourth retaining ring 51 is installed on the outer diameter of the first inner gear ring 37. The second sun gear 52 is connected with the inner spline tooth groove set in the inner hole of the first planetary carrier 36 through the external spline teeth, and rotates coaxially and concentrically. The second sun gear 52 A fifth retaining ring 58 is installed on it, a second planetary gear shaft 49 is installed on the second planetary carrier 54, a second planetary gear bearing 43 is installed in the inner hole of the second planetary gear 44, the second planetary gear bearing 43 is rotatably installed on the second planetary gear shaft 49, the second planetary gear 44 is meshed with the inner and outer teeth of the second inner gear ring 40 for transmission, a sixth bearing 41, a seventh bearing 45 and a third oil seal 55 are installed in the inner hole of the second inner gear ring 40, the sixth bearing 41 and the seventh bearing 45 are installed on the outer shaft diameter of the second planetary carrier 54, a second retaining ring 47 is installed on the outer shaft diameter of the second planetary carrier 54, the third oil seal 55 cooperates with the outer shaft diameter of the second planetary carrier 54 for sealing, the third oil seal 55 is provided with a protective cover plate 56, the protective cover plate 56 is provided with a water seal 57, an end cover 50 and a fourth O coil 46 are installed in the inner hole of the second inner gear ring 40, and a thrust washer 53 is installed in the inner hole of the end cover 50 to limit the axial displacement of the second sun gear 52.

[0032] The braking and releasing states of the first electromagnetic brake 401 and the second electromagnetic brake 402 are controlled by electrical signals. When the first electromagnetic brake 401 is in the released state and the second electromagnetic brake 402 is in the braking state, the first sun gear 30 can rotate freely relative to the first inner gear ring 37. The first inner gear ring 37 is a fixed component and cannot rotate. Both stages of planetary transmission participate in the reduction transmission, and the planetary transmission is placed in the low-speed first gear state.

[0033] The first electromagnetic brake 401 is in a braking state, the second electromagnetic brake 402 is in a released state, the rotational freedom of the first sun gear 30 relative to the first inner ring gear 37 is locked, and it can only rotate synchronously with the first inner ring gear 37. At the same time, the rotational freedom of the first planetary carrier 36 relative to the first sun gear 30 and the first inner ring gear 37 is also locked, and the three can only rotate together as an integral component, and the two-stage planetary transmission is placed in a high-speed second gear state.

[0034] The first electromagnetic brake 401 is in a released state, the second electromagnetic brake 402 is in a released state, and the planetary transmission components: the first sun gear 30 and the first inner ring gear 37 both have rotational freedom. At this time, the first planet carrier 36 cannot output power, and the two-stage planetary transmission is placed in a neutral state.

[0035] When the planetary transmission is placed in a low-speed first gear working state, the first electromagnetic brake 401 is controlled to lose power and switch to a braking state, thereby realizing an emergency braking function of the planetary transmission.

[0036] An electrically driven planetary transmission with an electromagnetic shifting function uses a reluctance synchronous motor as a power input device.

[0037] The double-braking electromagnetic brake adopts a spring-pressurized electromagnetic force to release a normally closed multi-friction plate brake. The large and small braking torque brakes are compactly integrated and can be disassembled and replaced.

[0038] A sealing structure design is adopted between all joint surfaces and rotating components, and the protection level of the electric drive planetary transmission in the assembled state reaches IP67.

[0039] The braking and releasing states of the first electromagnetic brake and the second electromagnetic brake are controlled by electrical signals. When the first electromagnetic brake is in the releasing state and the second electromagnetic brake is in the braking state, the first sun gear can rotate freely relative to the first inner gear ring, and the first inner gear ring is a fixed component and cannot rotate. Both the two-stage planetary transmission participates in the reduction transmission, and the planetary transmission is placed in a low-speed first gear state; when the first electromagnetic brake is in the braking state and the second electromagnetic brake is in the releasing state, the first sun gear is locked in freedom relative to the first inner gear ring and can only rotate synchronously with the first inner gear ring, and the first planet carrier is also locked in rotational freedom relative to the first sun gear and the first inner gear ring, and the three can only rotate together as an integral component, and the two-stage planetary transmission is placed in a high-speed second gear state; when the first electromagnetic brake is in the releasing state and the second electromagnetic brake is in the releasing state, the planetary transmission components: the first sun gear and the first inner gear ring both have rotational freedom, and at this time the first planet carrier cannot output power, and the two-stage planetary transmission is placed in a neutral state.

[0040] The braking and releasing states of the dual-braking electromagnetic brake are quickly switched and controlled through electrical signals to achieve the three-speed working state switching of the two-stage planetary transmission.

[0041] The two-stage planetary transmission switches between three working states. The first gear meets the requirements of low-speed and high-torque load-bearing walking conditions of the machine and equipment in a loaded state; the second gear meets the requirements of high-speed and small-torque rapid transition conditions of the machine and equipment in an unloaded state; and the neutral gear meets the requirements of higher-speed towing of the machine and equipment or towing in case of faults.

[0042] The technical principle of the present invention is described above in conjunction with specific embodiments. These descriptions are only for explaining the principle of the present invention and cannot be interpreted as limiting the protection scope of the present invention in any way. Based on the explanations herein, those skilled in the art can associate other specific implementations of the present invention without paying creative labor, and these methods will fall within the protection scope of the claims of the present invention.

Claims

1. An electrically driven planetary transmission with electromagnetic shifting function, characterized in that: include: Motor (1); A double-braking electromagnetic brake (4), arranged on the motor (1), comprising a first electromagnetic brake (401) and a second electromagnetic brake (402); A two-stage planetary reducer (5), arranged on the dual-brake electromagnetic brake (4), comprising a first planetary gear reducer and a second planetary gear reducer, wherein a first sun gear (30) of the first planetary gear reducer is connected to the motor (1), and a first planet carrier (36) of the first planetary gear reducer is meshed with a second sun gear (52) of the second planetary gear reducer; A spline gear sleeve (18), which is movably mounted on the spline shaft of the first sun gear (30) and connected to the first dynamic friction plate (16) of the first electromagnetic brake (401), and is used for braking and releasing the first sun gear (30); as well as A spline gear plate (32) is arranged on the first inner gear ring (37) of the first planetary gear reducer and is connected to the second dynamic friction plate (13) of the second electromagnetic brake and the first static friction plate (17) of the first electromagnetic brake (401) and is used for braking and releasing the first inner gear ring (37).

2. The electrically driven planetary transmission with electromagnetic shifting function according to claim 1, characterized in that: The first planetary gear reducer further comprises: a first planetary wheel (34), the first planetary wheel (34) being rotatably disposed on the first planet carrier (36) and meshing with the first sun gear (30) and the first inner gear ring (37).

3. The electrically driven planetary transmission with electromagnetic shifting function according to claim 2, characterized in that: The second planetary gear reducer also includes: A second planetary gear (44), the second planetary gear (44) meshing with the second sun gear (52); a second planet carrier (54), the second planet carrier (54) being rotatably connected to the second planetary gear (44) and the first inner ring gear (37), the second planet carrier (54) being used for connecting equipment; and A second inner gear ring (40), the second inner gear ring (40) is meshed with the second planetary gear (44) and is rotatably disposed on the second planetary carrier (54), and the second inner gear ring (40) is used to connect to the wheel.

4. The electrically driven planetary transmission with electromagnetic shifting function according to claim 3, characterized in that: The two-stage planetary reducer (5) further comprises: a third oil seal (55), the third oil seal (55) being disposed on the second inner gear ring (40) and movably abutting against the second planet carrier (54); and A protective cover plate (56) is disposed on the second inner gear ring (40) and abuts against one end of the third oil seal (55).

5. The electrically driven planetary transmission with electromagnetic shifting function according to claim 4, characterized in that: The two-stage planetary reducer (5) further comprises a water seal (57), wherein the water seal (57) is arranged on the second planet carrier (54) and movably abuts against the protective cover plate (56).

6. The electrically driven planetary transmission with electromagnetic shifting function according to claim 3, characterized in that: The two-stage planetary reducer (5) further comprises: a second oil seal (38), wherein the second oil seal (38) is arranged on the second planet carrier (54) and movably abuts against the first inner gear ring (37).

7. The electrically driven planetary transmission with electromagnetic shifting function according to claim 1, characterized in that: The first electromagnetic brake (401) further comprises: A brake housing (6), the brake housing (6) being connected to the motor (1) and the second planet carrier (54) of the second planetary gear reducer respectively; A first brake excitation coil (29), wherein the first brake excitation coil (29) is arranged inside the first brake excitation coil (29); a first brake spring (26), the first brake spring (26) being arranged in the brake housing (6); A first armature disc (25), the first armature disc (25) being movably disposed in the brake housing (6) along the axial direction and resting against the first brake spring (26), the first armature disc (25) being also disposed opposite to the first brake excitation coil (29); a pressure plate (20), the pressure plate (20) being rotatably mounted on the first armature plate (25); and A first dynamic friction plate (16) is movably arranged on one side of the pressure plate (20) along the axial direction, and is slidably sleeved on the spline gear sleeve (18), wherein the first dynamic friction plate (16) rotates synchronously with the spline gear sleeve (18); Wherein, the first static friction plate (17) is arranged between the first dynamic friction plates (16).

8. The electrically driven planetary transmission with electromagnetic shifting function according to claim 7, characterized in that: The second electromagnetic brake (402) further comprises: a second brake excitation coil (9), wherein the second brake excitation coil (9) is arranged in the brake housing (6); a second brake spring (22), the second brake spring (22) being arranged in the brake housing (6); A second armature disc (10), the second armature disc (10) being movably disposed in the brake housing (6) along the axial direction and resting against the second brake spring (22), the second armature disc (10) being also disposed opposite to the second brake excitation coil (9); A second dynamic friction plate (12), wherein the second dynamic friction plate (12) is movably sleeved on the spline gear plate (32), and the second dynamic friction plate (12) and the spline gear plate (32) rotate synchronously; a second static friction plate (13), the second dynamic friction plates (12) being movably arranged in the axial direction between the second dynamic friction plates (12); and A friction disc (15), wherein the friction disc (15) is arranged in the brake housing (6) and is arranged opposite to the second moving friction plate (12).

9. The electrically driven planetary transmission with electromagnetic shifting function according to claim 8, characterized in that: The second electromagnetic brake (402) further comprises: a height-equalizing column (11) fixedly arranged in the brake housing (6), and the second armature disc (10) and the second static friction plate (13) are both slidably inserted into the height-equalizing column (11).

10. The electrically driven planetary transmission with electromagnetic shifting function according to claim 1, characterized in that: Also includes: A transition flange seat (3), wherein the transition flange seat (3) is respectively connected to the motor (1) and the dual-brake electromagnetic brake (4).

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