Double-motor double-planet-row power coupling assembly and working method thereof

Abstract

The invention relates to the field of mechanical transmission, in particular to a dual-motor dual-planet-row power coupling assembly and a working method.The dual-motor dual-planet-row power coupling assembly comprises a shell, a first motor and a second motor, a first planet row, a second planet row and a brake are arranged in the shell, an output shaft of the first motor is in transmission connection with the first planet row, and an output shaft of the second motor is in transmission connection with the second planet row; an output shaft of the second motor is simultaneously in transmission connection with the first planet row and the second sun gear; the second gear ring is in on-off connection with the shell through a brake; power is output from the second planet carrier; in the large-torque and high-rotating-speed mode, the first motor and the second motor are the same in rotating direction when driving at the same time, and meanwhile the output rotating direction of the second planet carrier is the same as the rotating directions of the first motor and the second motor. According to the assembly, high-speed-ratio large-torque and low-speed-ratio high-rotating-speed output can be achieved only through static mode switching without dynamic gear shifting, and the defect of dynamic gear shifting of an existing transmission is overcome.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission, and in particular to a dual-motor dual-planetary gear power coupling assembly and its working method. Background Technology

[0002] In the field of electric drive technology for existing large new energy vehicles (including off-road vehicles such as loaders), two-speed or multi-speed transmissions are generally used in order to meet the needs of low-speed high torque and high-speed high RPM.

[0003] There are two main types of transmissions: one is the parallel shaft gear and shift fork shifting technology, and the other is the planetary gear and wet multi-plate clutch technology. Both types have a fixed ratio between the motor speed and the output speed in a certain gear, which limits the degree of efficiency improvement. They also have problems such as complex shifting mechanisms, high cost, high failure rate, complex control process, long time consumption, sluggish power response, and even deviations in shift smoothness.

[0004] Although some dual planetary gearbox power coupling technologies have been disclosed in recent years, they all suffer from a low speed ratio under high torque conditions, or a high speed ratio resulting in a low maximum output speed. They are not ideal in balancing low-speed high torque and high speed of the vehicle. Summary of the Invention

[0005] The purpose of this invention is to provide a dual-motor dual-planetary gearbox power coupling assembly and its working method. This assembly can achieve high-speed ratio high torque and low-speed ratio high speed output, overcoming the pain points of dynamic shifting in existing transmissions.

[0006] The technical solution of this invention is as follows: a dual-motor dual-planetary gear power coupling assembly, comprising a housing, a first motor, and a second motor. The housing houses a first planetary gear set, a second planetary gear set, and a brake. The first planetary gear set includes a first sun gear, a first ring gear, and a first planet carrier. The second planetary gear set includes a second sun gear, a second ring gear, and a second planet carrier. The output shaft of the first motor is drive-connected to the first planetary gear set, and the output shaft of the second motor is drive-connected to both the first planetary gear set and the second sun gear. The second ring gear is connected to the housing via the brake in a switchable manner. When the brake is engaged, the second ring gear is braked by the housing; when the brake is disengaged, the second ring gear can rotate relative to the housing. The first ring gear or the first sun gear is directly connected to the second ring gear or connected to it via the first clutch; the first ring gear and the first sun gear that are not connected to the second ring gear, as well as one of the first planetary carriers, are connected to the first motor; the first ring gear, the first sun gear, and the first planetary carrier that are not connected to the second ring gear or the first motor are connected to the second motor and the second sun gear simultaneously. Power is output from the second planetary carrier; when the first motor and the second motor drive simultaneously in high torque and high speed mode, the direction of rotation is the same, and the output rotation direction of the second planetary carrier is the same as that of the first motor and the second motor.

[0007] Optionally, when the first gear ring and the second gear ring are directly connected for transmission, and only one brake is provided without a clutch, the first gear ring and the second gear ring are manufactured as a single piece, and the first planetary gear set and the second planetary gear set share a single gear ring.

[0008] Optionally, the output shaft of the first motor is a hollow shaft, the first sun gear is a hollow gear, the first motor is connected to the first sun gear in a transmission connection, and the second motor passes through the first motor and the first sun gear respectively and is simultaneously connected to the first planetary carrier and the second sun gear in a transmission connection.

[0009] Optionally, the output shaft of the first motor is a hollow shaft, the first motor is connected to the first planetary carrier via a transmission, and the output shaft of the second motor passes through the first motor and the first planetary carrier and is simultaneously connected to the first sun gear and the second sun gear via a transmission.

[0010] Optionally, the first sun gear is directly connected to the second ring gear, the first sun gear is a hollow gear, the output shaft of the first motor is a hollow shaft, the first motor is connected to the first ring gear, the output shaft of the second motor passes through the first motor and the first ring gear and is connected to the first planetary carrier, and the first planetary carrier passes through the first sun gear and is connected to the second sun gear.

[0011] Optionally, the first sun gear is directly connected to the second ring gear, the first sun gear is a hollow gear, the output shaft of the first motor is a hollow shaft, the first motor is connected to the first planetary carrier, the output shaft of the second motor passes through the first motor and the first planetary carrier and is connected to the first ring gear, and the first ring gear passes through the first sun gear and is connected to the second sun gear.

[0012] Optionally, it also includes a first one-way overrunning clutch, which is disposed between the second gear ring and the housing; when the second planetary carrier is driven in the forward direction, and the second gear ring is at zero speed and has a tendency to reverse relative to the housing, the first one-way overrunning clutch locks, causing the second gear ring to be braked by the housing; otherwise, the first one-way overrunning clutch overruns, and the second gear ring can rotate relative to the housing.

[0013] Optionally, when a first clutch is provided, the first clutch is located between the first gear ring and the second gear ring, and one end of the first clutch is connected to the first gear ring in a driving connection, and the other end of the first clutch is connected to the second gear ring in a driving connection. The first clutch controls the engagement and disengagement of the first gear ring and the second gear ring. The brake is located between the second gear ring and the housing, and one end of the brake is connected to the second gear ring, and the other end of the brake is connected to the housing.

[0014] Furthermore, a second one-way overrunning clutch is provided between the first gear ring and the second gear ring; when driving in the forward direction and the forward rotation speed of the second gear ring is greater than that of the first gear ring, the second one-way overrunning clutch is locked, and the second gear ring and the first gear ring rotate synchronously; otherwise, the second one-way overrunning clutch overruns.

[0015] Optionally, the second motor and the first motor are arranged opposite each other on two sides. The output end of the second planetary carrier is hollow. The output shaft of the second motor passes through the second planetary carrier and is connected to the second sun gear. The second sun gear is connected to the first planetary carrier. The second planetary carrier is fixedly connected to the first gear. The first gear meshes with the second gear, and power is output from the second gear.

[0016] Furthermore, when the second motor is arranged opposite to the first motor, a non-travel load is added. The input shaft of the non-travel load passes through the first motor and the first sun gear and is connected to the first planetary carrier via a second clutch to achieve a switchable transmission connection.

[0017] A working method applied to a dual-motor dual-planetary gear power coupling assembly. 1) High torque mode: The brakes are engaged, and the first and second gear rings are braked by the housing through the brakes. At this time, the first and second motors rotate in the same direction. The power of the first motor is transmitted to the first planetary carrier through the first sun gear and the first planetary gear. According to the planetary gear motion law, when the first gear ring is braked, the rotation direction of the first planetary carrier remains unchanged and is the same as the rotation direction of the first motor. The power of the second motor is directly transmitted to the first planetary carrier and merges with the power transmitted from the first motor to the second sun gear. The power continues to be output from the second planetary carrier through the second planetary gear. According to the planetary gear motion law, when the second gear ring is braked, the rotation direction of the second planetary carrier remains unchanged and is the same as the rotation direction of the first and second motors. When the torque demand is not large, only the first motor or the second motor can be started, and the other motor can idle or be powered off. 2) High-speed mode: The brake is disengaged, and the first and second gear rings can rotate relative to the housing. At this time, the first and second motors rotate in the same direction. The power of the first motor is transmitted to the first gear ring through the first sun gear and the first planet gear. Part of the power of the second motor is transmitted to the first gear ring through the first planet carrier and the first planet gear, and then through the second gear ring and the second planet gear to the second planet carrier. The other part of the power of the second motor is transmitted to the second planet carrier through the second sun gear and the second planet gear, and then through the second gear ring to the second planet carrier, and output from the second planet carrier. 3) Switching from high torque mode to high speed mode: In high torque mode, when the speed of the first motor increases to a certain level and it is difficult to continue to increase or the efficiency of continuing to increase decreases significantly and the vehicle does not require high torque, the brake is disengaged, and the first and second gear rings can rotate relative to the housing. The assembly switches to high speed mode. At this time, the speeds of the first and second motors are adjusted so that the first and second motors work in the high-efficiency range. Under the condition of satisfying the drive torque and the motors working in the high-efficiency range, the speeds of the first and second motors are made similar or equal so that the relative speeds of the components of the first and second planetary gear sets are as small as possible or zero. 4) Switching from high-speed mode to high-torque mode: In high-speed mode, when the speed of the first motor decreases to a certain level and continues to decrease, resulting in a significant decrease in efficiency, or when the output torque of the high-speed mode is insufficient to meet the drive requirements, the speed of the first motor is gradually increased, while the speed of the second motor remains unchanged or is appropriately reduced. This causes the forward rotation speed of the first and second gear rings to gradually decrease to 0. Then, the first and second gear rings tend to reverse, causing the first one-way overrunning clutch to engage. This prevents the first and second gear rings from reversing and keeps them in a stopped state. At this time, the brake engages, fully braking the first and second gear rings. The assembly enters high-torque mode. Under the condition of meeting the drive torque, the output torque of the first and second motors is adjusted so that the two motors operate within the torque-efficient range. 5) Power supply: When the brake is powered off, power is transmitted from the wheels in the opposite direction of the drive path to the first motor and the second motor, which then generate electricity for the first motor and the second motor.

[0018] Compared with the prior art, the present invention has the following advantages: 1) This assembly can achieve high-speed torque and low-speed high-speed output by simply switching static modes without dynamic shifting, thus overcoming the pain points of dynamic shifting in existing transmissions.

[0019] 2) The brakes of this assembly can engage or disengage when the gear ring speed is zero or low, without causing shock or jerking during engagement or disengagement, ensuring smooth vehicle operation. Because engagement or disengagement occurs at zero or low speed, a large speed ratio can be achieved, reducing the number of clutches and gears, making the assembly structure simpler, lower in cost, and more reliable.

[0020] 3) Since the motor efficiency is very low during start-up and low-speed phases, the assembly can be driven in high-speed mode when the vehicle starts with low torque or is driven at low speed with low torque. At this time, the speeds of the first motor and the second motor can both operate in the high-efficiency range or close to the high-efficiency range.

[0021] 4) In high-speed mode, the first and second motors rotate at speeds as close as possible to each other, thereby reducing the relative speeds between gears and other related parts, minimizing energy loss due to friction, and reducing wear on gears and other related parts, thus extending their service life. In high-torque mode, the motors, sun gear, and planetary carrier rotate in the same direction, which also helps reduce relative speeds, further reducing energy loss, wear on gears and other related parts, and extending their service life.

[0022] 5) Since the brake of this assembly switches modes in a static state, the requirements for the brake are low. Moreover, there is only one brake in the two modes, unlike a multi-speed transmission which has two or more clutches. If three states are required, only one clutch needs to be added to increase the number of gears in the assembly. Therefore, the cost can be greatly reduced, and the structure is very simple, which can achieve a smaller volume and reduce the space occupied.

[0023] 6) This assembly has various application structures; the appropriate structure should be selected according to actual needs, such as... Figure 1 The structure, with the gear ring located on the outermost circumference and the sun gear in the middle, is designed according to its working principle. This eliminates the need for additional connecting parts, saving costs. Furthermore, the absence of other components passing through the outer circumference of the gear ring further reduces the volume and minimizes the loss of churning energy. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the dual-motor dual-planetary gear power coupling assembly of the present invention.

[0025] Figure 2 This is a power transmission route diagram for the high-torque mode connection between the first planetary carrier and the second sun gear in Embodiment 1 of the present invention.

[0026] Figure 3 This is a power transmission route diagram for the high-speed mode connection between the first planetary carrier and the second sun gear in Embodiment 1 of the present invention.

[0027] Figure 4 This is a power transmission route diagram for the high-torque mode of connecting two sun gears in Embodiment 2 of the present invention.

[0028] Figure 5 This is a power transmission route diagram for the high-speed mode of connecting two sun gears in Embodiment 2 of the present invention.

[0029] Figure 6 This is a power transmission route diagram for the high-torque mode connection between the first planetary carrier and the second sun gear in Embodiment 3 of the present invention.

[0030] Figure 7 This is a power transmission route diagram for the high-torque mode connection between the first planetary carrier and the second sun gear in Embodiment 3 of the present invention.

[0031] Figure 8 This is a power transmission route diagram for the high torque mode connection between the first gear ring and the second sun gear in Embodiment 4 of the present invention.

[0032] Figure 9 This is a power transmission route diagram for the high-speed mode connection between the first gear ring and the second sun gear in Embodiment 4 of the present invention.

[0033] Figure 10 This is a power transmission route diagram for the torque-medium speed mode in Embodiment 5 of the present invention.

[0034] Figure 11 This is a schematic diagram of two motors arranged opposite each other in Embodiment Six of the present invention.

[0035] Figure 12 This is a power transmission route diagram for a non-walking load installed in Embodiment 7 of the present invention.

[0036] In the diagram: 1-Housing; 2-Brake; 3-First Motor; 4-Second Motor; 5-First Sun Gear; 6-First Planetary Gear; 7-First Ring Gear; 8-Second Sun Gear; 9-Second Planetary Gear; 10-Second Ring Gear; 11-First Planetary Carrier; 12-Second Planetary Carrier; 14-First Clutch; 15-First Gear; 16-Second Gear; 17-Non-Traffic Load; 18-Second Clutch; 19-First One-Way Overrunning Clutch; 20-Second One-Way Overrunning Clutch. Detailed Implementation

[0037] To make the above features and advantages of the present invention more readily understood, specific embodiments are described below in conjunction with the accompanying drawings, but the present invention is not limited thereto. Example 1 (Reference) Figures 1 to 3

[0038] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0039] Specifically, the first planetary gear set includes a first sun gear 5, first planet gears 6, a first ring gear 7, and a first planet carrier 11. The second planetary gear set includes a second sun gear 8, second planet gears 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is drivenly connected to the first planetary gear set, and the output shaft of the second motor 4 is simultaneously drivenly connected to both the first planetary gear set and the second sun gear 8. The second ring gear 10 is connected to the housing 1 via a brake 2, allowing it to rotate relative to the housing 1. When the brake 2 is engaged, the second ring gear 10 is braked by the housing 1; when the brake 2 is disengaged, the second ring gear 10 can rotate relative to the housing 1. Power is output from the second planet carrier 12.

[0040] In this embodiment, the first gear ring 7 and the second gear ring 10 are directly connected for transmission, and only one brake 2 is provided without a clutch. To reduce costs, the first gear ring 7 and the second gear ring 10 are manufactured as a single piece. Specifically, the first planetary gear set and the second planetary gear set share a single gear ring. When the brake 2 is engaged, the first gear ring 7 and the second gear ring 10 are simultaneously braked by the housing. When the brake 2 is disengaged, the first gear ring 7 and the second gear ring 10 can rotate simultaneously relative to the housing 1.

[0041] In this embodiment, the first motor 3 and the second motor 4 are located on the same side, and the output shaft of the first motor 3 is a hollow shaft, and the first sun gear 5 is a hollow gear (in this document, "hollow" refers to a shaft hole with components such as a clearance shaft). The first motor 3 is connected to the first sun gear 5 in a transmission connection; the output shaft of the second motor 4 passes through the first motor 3, its output shaft, and the first sun gear 5, and is simultaneously connected to the first planetary carrier 11 and the second sun gear 8 in a transmission connection.

[0042] In this embodiment, conventional clutches such as coupling sleeves, dog-tooth clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0043] In this embodiment, the dual-motor dual-planetary gear power coupling assembly may further include a first one-way overrunning clutch 19, which is disposed between the second ring gear 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second ring gear 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second ring gear 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second ring gear 10 can rotate relative to the housing 1.

[0044] The above connection, through the engagement and disengagement of the brake 2, can achieve at least two working modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, the direction of rotation is the same. At the same time, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. Example 2 (Reference) Figure 4 and Figure 5

[0045] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0046] Specifically, the first planetary gear set includes a first sun gear 5, first planet gears 6, a first ring gear 7, and a first planet carrier 11. The second planetary gear set includes a second sun gear 8, second planet gears 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is drivenly connected to the first planetary gear set, and the output shaft of the second motor 4 is simultaneously drivenly connected to both the first planetary gear set and the second sun gear 8. The second ring gear 10 is connected to the housing 1 via a brake 2, allowing it to rotate relative to the housing 1. When the brake 2 is engaged, the second ring gear 10 is braked by the housing 1; when the brake 2 is disengaged, the second ring gear 10 can rotate relative to the housing 1. Power is output from the second planet carrier 12.

[0047] In this embodiment, the first gear ring 7 and the second gear ring 10 are directly connected for transmission, and only one brake 2 is provided without a clutch. To reduce costs, the first gear ring 7 and the second gear ring 10 are manufactured as a single piece. Specifically, the first planetary gear set and the second planetary gear set share a single gear ring. When the brake 2 is engaged, the first gear ring 7 and the second gear ring 10 are simultaneously braked by the housing; when the brake 2 is disengaged, the first gear ring 7 and the second gear ring 10 can rotate simultaneously relative to the housing 1.

[0048] In this embodiment, the first motor 3 and the second motor 4 are located on the same side, and the output shaft of the first motor 3 is a hollow shaft. The first motor 3 is connected to the first planetary carrier 11 for transmission. The output shaft of the second motor 4 passes through the first motor 3 and the first planetary carrier 11 and is connected to the first sun gear 5 and the second sun gear 8 for transmission.

[0049] In this embodiment, conventional clutches such as coupling sleeves, dog clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0050] In this embodiment, the dual-motor dual-planetary gear power coupling assembly may further include a first one-way overrunning clutch 19, which is disposed between the second ring gear 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second ring gear 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second ring gear 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second ring gear 10 can rotate relative to the housing 1.

[0051] The above connection, through the engagement and disengagement of the brake 2, can achieve at least two working modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, the direction of rotation is the same. At the same time, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. The operating method of the dual-motor dual-planetary gear power coupling assembly with only one brake and no clutch in Examples 1 and 2:

[0052] Let the rotational speed of the first sun gear 5 be N1s and its torque be T1s; the rotational speed of the first ring gear 7 be N1r and its torque be T1r; the rotational speed of the first planetary carrier 11 be N1h and its torque be T1h; the rotational speed of the second sun gear 8 be N2s and its torque be T2s; the rotational speed of the second ring gear 10 be N2r and its torque be T2r; and the rotational speed of the second planetary carrier 12 be N2h and its torque be T2h. For simplicity, the speed ratio from the first sun gear 5 to the first planetary carrier 11 in the first planetary gear set is i1, and the speed ratio from the second sun gear 8 to the second planetary carrier 12 in the second planetary gear set is i2. The peak torque of the first motor 3 is T1max, the on-time torque is T1, the rotational speed is N1, the peak rotational speed is N1max, the power is P1, and the peak power is P1max. The peak torque of the second motor 4 is T2max, the on-time torque is T2, the rotational speed is N2, the peak rotational speed is N2max, the power is P2, and the peak power is P2max. Oil stirring, gear friction losses, and bearing friction losses are ignored. Forward rotation of the planetary carrier corresponds to vehicle forward movement, and reverse rotation of the planetary carrier corresponds to vehicle backward movement.

[0053] 1) High Torque Mode: With the brake engaged, the first ring gear 7 and the second ring gear 10 are braked by the housing 1 via the brake 2. At this time, the first motor 3 and the second motor 4 rotate in the same direction. The power of the first motor 3 is transmitted to the first planetary carrier 11 through the first sun gear 5 and the first planetary gear 6. According to the planetary gear motion law, when the first ring gear 7 is braked, the first planetary carrier 11 rotates in the same direction as the first motor 3, with a torque T1h = i1 * T1. The power of the second motor 4 is directly transmitted to the first planetary carrier 11 and merges with the power transmitted from the first motor 3 into the second sun gear 5, with a torque T2s = i1 * T1 + T2. The power continues to be output from the second planetary carrier 12 through the second planetary gear 9. According to the planetary gear motion law, when the second ring gear 10 is braked, the second planetary carrier 12 rotates in the same direction as the first motor 3 and the second motor 4, with an output torque T2h = i2 * ( i1*T1+T2), that is, the torque of the first motor 3 is output according to the speed ratio i1*i2, and the torque of the second motor 4 is output according to the speed ratio i2. The overall speed ratio is large. According to the actual needs of the working conditions, the values ​​of T1 and T2 are determined according to the principle of high efficiency. When the torque demand is not large, only the first motor 3 or the second motor 4 can be started, and the other motor can idle or be powered.

[0054] 2) High-speed mode: Brake 2 is disengaged, and the first ring gear 7 and the second ring gear 10 can rotate relative to the housing 1. At this time, the first motor 3 and the second motor 4 rotate in the same direction. The power of the first motor 3 is transmitted to the first ring gear through the first sun gear 5 and the first planetary gear 6. A portion of the power of the second motor 4 is transmitted to the first ring gear 7 through the first planetary carrier 11 and the first planetary gear 6, along with the power of the first motor 3. At this time, the rotational speed of the first ring gear 7 is N1r = (i1 * N1h - N1s) / (i1 - 1), that is, N1r = (i1 * N1h - N1s) / (i1 - 1). The second ring gear 10 rotates at speed N2r = N1r. Then, the second ring gear 10 and the second planetary gear 9 transmit the power to the second planetary carrier 12. Another part of the power of the second motor 4 is transmitted to the second planetary carrier 12 through the second sun gear 8 and the second planetary gear 9, together with the power transmitted through the second ring gear 10, and output from the second planetary carrier 12. At this time, the rotational speed of the second planetary carrier 12 is N2h = (N2s + (i2-1) * N2r) / i2, that is, N2h = (N2 + (i2-1) * (i1 * N2-N1) / (i1-1)) / i2. When N1 = N2, N2h = N2, which is equivalent to the high speed mode. If the output speeds of the two motors are the same, the overall speed ratio is 1.

[0055] 3) Switching from high torque mode to high speed mode: In high torque mode, when the speed of the first motor 3 increases to a certain level and it is difficult to continue to increase or the efficiency of further increasing decreases significantly and the vehicle does not require high torque, the brake 2 is disengaged, and the first gear ring 7 and the second gear ring 10 can rotate relative to the housing. The assembly switches to high speed mode. At this time, the speeds of the first motor 3 and the second motor 4 are adjusted so that the first motor 3 and the second motor 4 operate in the high-efficiency range as much as possible. Under the condition of satisfying the drive torque and the motor operating in the high-efficiency range, the speeds of the first motor 3 and the second motor 4 are made as close as possible or equal to each other, so that the relative speeds of the components of the first planetary gear set and the second planetary gear set are as small as possible or zero, so as to reduce wear between components, reduce energy loss, reduce component damage, and extend the service life of components.

[0056] 4) Switching from high-speed mode to high-torque mode: In high-speed mode, when the speed of the first motor 3 decreases to a certain level and continues to decrease, resulting in a significant drop in efficiency, or when the output torque of the high-speed mode is insufficient to meet the drive requirements, the speed of the first motor 3 is gradually increased, while the speed of the second motor 4 remains unchanged or is appropriately reduced, so that the forward rotation speed of the first gear ring 7 and the second gear ring 10 gradually decreases to 0. Then, the first gear ring 7 and the second gear ring 10 tend to reverse, and the first one-way overrunning clutch 19 is engaged, so that the first gear ring 7 and the second gear ring 10 cannot reverse and remain in a stopped state. At this time, the brake 2 is engaged, so that the first gear ring 7 and the second gear ring 10 are fully braked, and the assembly enters the high-torque mode. Under the condition of meeting the drive torque, the output torque of the first motor 3 and the second motor 4 is adjusted so that the two motors work in the torque-efficient range as much as possible.

[0057] 5) Power supply: When the brake is powered off, power is transmitted from the wheel to the first motor 3 and the second motor 4 in the opposite direction of the drive path, so as to generate electricity for the first motor 3 and the second motor 4. Example 3 (Reference) Figure 6 and Figure 7

[0058] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0059] Specifically, the first planetary gear set includes a first sun gear 5, first planet gears 6, a first ring gear 7, and a first planet carrier 11. The second planetary gear set includes a second sun gear 8, second planet gears 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is drivenly connected to the first planetary gear set, and the output shaft of the second motor 4 is simultaneously drivenly connected to both the first planetary gear set and the second sun gear 8. The second ring gear 10 is connected to the housing 1 via a brake 2, allowing it to rotate relative to the housing 1. When the brake 2 is engaged, the second ring gear 10 is braked by the housing 1; when the brake 2 is disengaged, the second ring gear 10 can rotate relative to the housing 1. Power is output from the second planet carrier 12.

[0060] In this embodiment, the first sun gear 5 is directly connected to the second ring gear 10. The first motor 3 and the second motor 4 are located on the same side. The first sun gear 5 is a hollow gear. The output shaft of the first motor 3 is a hollow shaft. The first motor 3 is connected to the first ring gear 7. The output shaft of the second motor 4 passes through the first motor 3 and the first ring gear 7 and is connected to the first planetary carrier 11. The first planetary carrier 11 (the output shaft of the second motor 4 continues to extend) passes through the first sun gear 5 and is connected to the second sun gear 8.

[0061] In this embodiment, conventional clutches such as coupling sleeves, dog-tooth clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0062] In this embodiment, the dual-motor dual-planetary gear power coupling assembly may further include a first one-way overrunning clutch 19, which is disposed between the second ring gear 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second ring gear 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second ring gear 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second ring gear 10 can rotate relative to the housing 1.

[0063] The above connection, through the engagement and disengagement of the brake 2, can achieve at least two working modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, the direction of rotation is the same. At the same time, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. Example 4 (Reference) Figure 8 and Figure 9

[0064] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0065] Specifically, the first planetary gear set includes a first sun gear 5, first planet gears 6, a first ring gear 7, and a first planet carrier 11. The second planetary gear set includes a second sun gear 8, second planet gears 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is drivenly connected to the first planetary gear set, and the output shaft of the second motor 4 is simultaneously drivenly connected to both the first planetary gear set and the second sun gear 8. The second ring gear 10 is connected to the housing 1 via a brake 2, allowing it to rotate relative to the housing 1. When the brake 2 is engaged, the second ring gear 10 is braked by the housing 1; when the brake 2 is disengaged, the second ring gear 10 can rotate relative to the housing 1. Power is output from the second planet carrier 12.

[0066] In this embodiment, the first sun gear 5 is directly connected to the second ring gear 10. The first motor 3 and the second motor 4 are located on the same side. The first sun gear 5 is a hollow gear. The output shaft of the first motor 3 is a hollow shaft. The first motor 3 is connected to the first planetary carrier 11. The output shaft of the second motor 4 passes through the first motor 3 and the first planetary carrier 11 and is connected to the first ring gear 7. The first ring gear 7 passes through the first sun gear 7 (the output shaft of the second motor 4 continues to extend) and is connected to the second sun gear 8.

[0067] In this embodiment, conventional clutches such as coupling sleeves, dog-tooth clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0068] In this embodiment, the dual-motor dual-planetary gear power coupling assembly further includes a first one-way overrunning clutch 19, which is disposed between the second gear ring 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second gear ring 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second gear ring 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second gear ring 10 can rotate relative to the housing 1.

[0069] The above connection, through the engagement and disengagement of the brake 2, can achieve at least two working modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, the direction of rotation is the same. At the same time, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. Example 5 (Reference) Figure 10

[0070] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0071] Specifically, the first planetary gear set includes a first sun gear 5, a first planet gear 6, a first ring gear 7, and a first planet carrier 11; the second planetary gear set includes a second sun gear 8, a second planet gear 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is connected to the first planetary gear set via a transmission connection, and the output shaft of the second motor 4 is connected to both the first planetary gear set and the second sun gear 8 via a transmission connection.

[0072] In this embodiment, the first motor 3 is connected to the first sun gear 5 via a transmission connection; the first motor 3 and the second motor 4 are located on the same side, and the output shaft of the first motor 3 is a hollow shaft, while the first sun gear 5 is a hollow gear. The output shaft of the second motor 4 passes through the first motor 3, its output shaft, and the first sun gear 5, and is simultaneously connected to the first planetary carrier 11 and the second sun gear 8 via a transmission connection.

[0073] In this embodiment, a first clutch 14 is provided, which is located between the first gear ring 7 and the second gear ring 10. One end of the first clutch 14 is connected to the first gear ring 7, and the other end of the first clutch 14 is connected to the second gear ring 10. The first clutch 14 controls the engagement and disengagement of the first gear ring 7 and the second gear ring 10.

[0074] Brake 2 is positioned between the second gear ring 10 and the housing 1, with one end of brake 2 connected to the second gear ring 10 and the other end connected to the housing. The second gear ring 10 is connected to the housing 1 via brake 2, allowing it to rotate relative to the housing 1 when brake 2 is engaged and when brake 2 is disengaged. Power is output from the second planetary carrier 12.

[0075] In this embodiment, conventional clutches such as coupling sleeves, dog-tooth clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0076] In this embodiment, the dual-motor dual-planetary gear power coupling assembly further includes a first one-way overrunning clutch 19, which is disposed between the second gear ring 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second gear ring 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second gear ring 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second gear ring 10 can rotate relative to the housing 1.

[0077] In this embodiment, a second one-way overrunning clutch 20 is also provided, which is located between the first gear ring 7 and the second gear ring 10. When driving in the forward direction and the forward rotation speed of the second gear ring 10 is greater than that of the first gear ring 7, the second one-way overrunning clutch 20 is locked, and the second gear ring 10 and the first gear ring 7 rotate synchronously; otherwise, the second one-way overrunning clutch 20 overruns.

[0078] The above connection, through the engagement and disengagement of brake 2, enables at least two operating modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, their directions of rotation are the same. Furthermore, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. With the assistance of the first clutch 14, the assembly can achieve three operating modes: high torque mode, medium torque and medium speed mode, and high speed mode. The working method of the dual-motor dual-planetary gear power coupling assembly with an added first clutch:

[0079] 1) High torque mode: The first clutch 14 and the brake 2 are engaged, and the rest are the same as the working method of the dual-motor dual-planetary gear power coupling assembly with only one brake and no clutch (step 1).

[0080] 2) Medium torque and medium speed mode: The first clutch 14 is disengaged, the first ring gear 7 can rotate relative to the housing 1, the brake 2 remains engaged, the second ring gear 10 is braked by the housing 1, the second motor 4 remains driven, the power of the second motor 4 is transmitted to the second planetary carrier 12 through the second sun gear 8 and the second planetary gear 9, and the power is output from the second planetary carrier 12. At this time, the output torque of the second planetary carrier 12 is T2h=i2*T2, and the output speed of the second planetary carrier 12 is N2h=N2 / i2. Since the speed ratio of the planetary gears is greater than 2, the maximum output torque in this mode is less than that in the high torque mode but greater than that in the high speed mode. The maximum output speed in this mode is greater than that in the high torque mode but less than that in the high speed mode. The first motor 3 idles or stops.

[0081] 3) High-speed mode: The first clutch 14 engages, the brake 2 disengages, and the rest is the same as step 2 of the working method of the dual-motor dual-planetary gear power coupling assembly with only one brake and no clutch.

[0082] 4) High Torque to Medium Torque / Medium Speed ​​Mode: In high torque mode, when the speed of the first motor 3 is N1, the speed of the second motor 4 is N2 = N1 / i1. Therefore, when the maximum speed of the second motor 4 is comparable to the maximum speed of the first motor 3, and the first motor 3 reaches its maximum or near maximum speed, the second motor 4 can continue to increase its speed. When the speed of the first motor 3 increases to a certain level and becomes difficult to increase further, or when the efficiency of further increase decreases significantly and the vehicle does not require high torque, the first motor 3 stops driving, the first clutch 14 disengages, and the first gear ring 7 can rotate relative to the housing 2, thus switching to medium torque / medium speed mode. This also increases the output torque of the second motor 4 to compensate for the reduced power caused by the first motor 3 stopping, ensuring smooth power output. The first motor 3 follows suit, rotating or stopping.

[0083] 5) Switching from medium torque and medium speed mode to high speed mode: In medium torque and medium speed mode, when the speed of the second motor 4 increases to a certain level and it is difficult to continue to increase or the efficiency of continuing to increase decreases significantly, and the torque required for vehicle driving is less than the medium torque, the brake 2 disengages, the first motor 3 restarts, and the second motor 4 stops output or reduces speed, so that the second ring gear 10 rotates forward under the reaction of the second planetary carrier 12 and the forward rotation speed tends to exceed that of the first ring gear 7. At this time, the second one-way overrunning clutch 20 locks, the first ring gear 7 and the second ring gear 10 synchronize, and then the first clutch 14 engages, so that the assembly switches to high speed mode, and the first motor 3 and the second motor 4 provide power in high speed mode.

[0084] 6) Switching from high-speed mode to medium-torque medium-speed mode: In high-speed mode, when the speed of the first motor 3 decreases to a certain level and continues to decrease, resulting in a significant decrease in efficiency, or when the output torque of the high-speed mode is insufficient to meet the drive requirements, the first clutch 14 disengages, gradually increasing the speed of the second motor 4, causing the forward rotation speed of the second gear ring 10 to gradually decrease to 0, followed by a reverse rotation trend, and engaging the first one-way overrunning clutch 19. At this time, the brake 2 engages, the second gear ring 10 is fully braked, the first motor 3 stops power output, and the first gear ring 7 can rotate relative to the housing 1, thus switching the assembly to medium-torque medium-speed mode.

[0085] 7) Switching from medium torque and medium speed mode to high torque mode: In medium torque and medium speed mode, when the speed of the second motor 4 decreases to a certain level and continues to decrease, resulting in a significant decrease in efficiency, or when the output torque of the high speed mode is difficult to meet the drive requirements, the speed N1 of the first motor 3 is adjusted so that N1=i1*N2 or N1≈i1*N2, thereby making the speed of the first gear ring 7 0 or close to 0. At this time, the first clutch 14 is engaged, and the first gear ring 7 and the second gear ring 10 are simultaneously braked by the housing 1, and the assembly switches to high torque mode.

[0086] 8) Power supply: When the brake is powered off, power is transmitted from the wheel to the first motor 3 and the second motor 4 in the opposite direction of the drive path, so as to generate electricity for the first motor 3 and the second motor 4. Example 6 Reference Figure 11

[0087] A dual-motor dual-planetary gearbox power coupling assembly includes a housing 1, a first motor 3, and a second motor 4. The housing 1 houses a first planetary gearbox, a second planetary gearbox, and a brake 2. The first and second planetary gearboxes are single-stage planetary gearboxes, composite planetary gearboxes, or variations thereof, but all possess three core basic components: a sun gear, a ring gear, and a planet carrier. Preferably, the planetary gearboxes in this application have an NGW (internal-male-external) structure.

[0088] Specifically, the first planetary gear set includes a first sun gear 5, a first planet gear 6, a first ring gear 7, and a first planet carrier 11; the second planetary gear set includes a second sun gear 8, a second planet gear 9, a second ring gear 10, and a second planet carrier 12. The output shaft of the first motor 3 is connected to the first planetary gear set via a transmission connection, and the output shaft of the second motor 4 is connected to both the first planetary gear set and the second sun gear 8 via a transmission connection.

[0089] In this embodiment, the first motor 3 is connected to the first sun gear 5 via a transmission connection; the second motor and the first motor are arranged opposite each other on opposite sides; the output end of the second planetary carrier 12 is hollow, and the output shaft of the second motor 12 passes through the second planetary carrier 12 and is connected to the second sun gear 8 via a transmission connection; the second sun gear 8 (the output shaft of the second motor 12 continues to extend) is connected to the first planetary carrier 11 via a transmission connection. The second planetary carrier 12 is fixedly connected to a first gear 15, which meshes with a second gear 16, and power is output from the second gear 16.

[0090] In this embodiment, the brake 2 is disposed between the second gear ring 10 and the housing 1. The second gear ring 10 is connected to the housing 1 via the brake 2, so that when the brake 2 is engaged, the second gear ring 10 is braked by the housing 1, and when the brake 2 is disengaged, the second gear ring 10 can rotate relative to the housing 1.

[0091] In this embodiment, conventional clutches such as coupling sleeves, dog-tooth clutches, wet multi-plate clutches, and electromagnetic clutches can be used as brakes 2.

[0092] In this embodiment, the dual-motor dual-planetary gear power coupling assembly may further include a first one-way overrunning clutch 19, which is disposed between the second ring gear 10 and the housing 1. When the second planetary carrier 12 is driven in the forward direction, and the second ring gear 10 is at zero speed and has a tendency to reverse relative to the housing 1, the first one-way overrunning clutch 19 locks, causing the second ring gear 10 to be braked by the housing. Otherwise, the first one-way overrunning clutch 19 overruns, and the second ring gear 10 can rotate relative to the housing 1.

[0093] The above connection, through the engagement and disengagement of the brake 2, can achieve at least two working modes: high torque and high speed. It also ensures that when the first motor 3 and the second motor 4 are driven simultaneously in both high torque and high speed modes, the direction of rotation is the same. At the same time, the output rotation direction of the second planetary carrier 12 is the same as that of the first motor 3 and the second motor 4. Example 7 (Reference) Figure 12

[0094] The difference between this embodiment and Embodiment Six is ​​that the output shaft of the first motor 3 is a hollow shaft, and the first sun gear 5 is a hollow gear. A non-traveling load 17, such as an oil pump or water pump (for example, added on the same side as the first motor 3), is added. The input shaft of the non-traveling load 17 passes through the first motor 3 and the first sun gear 5 and is connected to the first planetary carrier 11 via a second clutch 18 for a disengageable transmission connection. When the second clutch 18 is engaged, the non-traveling load 17 is connected to the first planetary carrier 11, and power can be transmitted to the non-traveling load 17 through the first planetary carrier 11; when the second clutch 18 is disengaged, the first planetary carrier 11 does not transmit power to the non-traveling load 17. Operating method of a dual-motor dual-planetary gear power coupling assembly with non-travel loads but without a first clutch:

[0095] 1) In the same working method of a dual-motor dual-planetary gear power coupling assembly with only one brake and no clutch, steps 1)-5) the second clutch 18 disengages when the non-travel load 17 is not working.

[0096] 2) Operation of Non-Traveling Load 17 in Parked State: In the parked state, the vehicle brakes, which is equivalent to braking the second planetary carrier 12. Brake 2 disengages, allowing the first ring gear 7 and second ring gear 10 to rotate relative to the housing 2. The second clutch 18 engages, and the non-traveling load 17 is connected to the first planetary carrier 11 via the second clutch 18. The first motor 3 and second motor 4 are started, with the output shafts of the first motor 3 and second motor 4 rotating in the same direction. Part of the power from the second motor 4 is directly transmitted to the non-traveling load 17 via the second clutch 18, and the other part is transmitted to the first planetary carrier 11 via the second sun gear 8, second ring gear 10, first ring gear 7, and first planetary gear 6. The power from the first motor 3 is transmitted to the first planetary carrier 11 via the first sun gear 5 and first planetary gear 6, and together with the other part of the power transmitted from the second motor 4 to the first planetary carrier 11, it is transmitted to the non-traveling load 17 via the second clutch 18. Optionally, when the power required by the non-traveling load 17 is low, to ensure high-efficiency operation, the first motor 3 may idle or follow the power supply.

[0097] The above description is only a preferred embodiment of the present invention. For those skilled in the art, designing different forms of dual-motor dual-planetary gearbox power coupling assemblies and their working methods according to the teachings of the present invention does not require creative labor. All equivalent changes, modifications, substitutions and variations made in accordance with the scope of the patent application of the present invention without departing from the principles and spirit of the present invention shall be covered by the present invention.

Claims

1. A dual-motor dual-planetary gearbox power coupling assembly, comprising a housing, a first motor, and a second motor, characterized in that, The housing contains a first planetary gear set, a second planetary gear set, and a brake. The first planetary gear set includes a first sun gear, a first ring gear, and a first planet carrier. The second planetary gear set includes a second sun gear, a second ring gear, and a second planet carrier. The output shaft of the first motor is connected to the first planetary gear set, and the output shaft of the second motor is connected to both the first planetary gear set and the second sun gear. The second ring gear is connected to the housing via the brake in a switchable manner. When the brake is engaged, the second ring gear is braked by the housing. When the brake is disengaged, the second ring gear can rotate relative to the housing. The first ring gear or the first sun gear is directly connected to the second ring gear or connected to it via the first clutch; the first ring gear and the first sun gear that are not connected to the second ring gear, as well as one of the first planetary carriers, are connected to the first motor; the first ring gear, the first sun gear, and the first planetary carrier that are not connected to the second ring gear or the first motor are connected to the second motor and the second sun gear simultaneously. Power is output from the second planetary carrier; when the first motor and the second motor drive simultaneously in high torque and high speed mode, the direction of rotation is the same, and the output rotation direction of the second planetary carrier is the same as that of the first motor and the second motor.

2. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, characterized in that, When the first gear ring and the second gear ring are directly connected for transmission, and only one brake is provided without a clutch, the first gear ring and the second gear ring are manufactured as a single piece, and the first planetary gear set and the second planetary gear set share a single gear ring.

3. The dual-motor dual-planetary gearbox power coupling assembly according to claim 2, characterized in that, The output shaft of the first motor is a hollow shaft, and the first sun gear is a hollow gear. The first motor is connected to the first sun gear in a transmission connection. The second motor passes through the first motor and the first sun gear and is simultaneously connected to the first planetary carrier and the second sun gear in a transmission connection.

4. The dual-motor dual-planetary gearbox power coupling assembly according to claim 2, characterized in that, The output shaft of the first motor is a hollow shaft. The first motor is connected to the first planetary carrier via a transmission. The output shaft of the second motor passes through the first motor and the first planetary carrier and is simultaneously connected to the first sun gear and the second sun gear via a transmission.

5. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, characterized in that, The first sun gear is directly connected to the second ring gear. The first sun gear is a hollow gear. The output shaft of the first motor is a hollow shaft. The first motor is connected to the first ring gear. The output shaft of the second motor passes through the first motor and the first ring gear and is connected to the first planetary carrier. The first planetary carrier passes through the first sun gear and is connected to the second sun gear.

6. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, characterized in that, The first sun gear is directly connected to the second ring gear. The first sun gear is a hollow gear. The output shaft of the first motor is a hollow shaft. The first motor is connected to the first planetary carrier. The output shaft of the second motor passes through the first motor and the first planetary carrier and is connected to the first ring gear. The first ring gear passes through the first sun gear and is connected to the second sun gear.

7. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, characterized in that, It also includes a first one-way overrunning clutch, which is located between the second gear ring and the housing; when the second planetary carrier is driven in the forward direction, and the second gear ring is at zero speed and has a tendency to reverse relative to the housing, the first one-way overrunning clutch locks, causing the second gear ring to be braked by the housing; otherwise, the first one-way overrunning clutch overruns, and the second gear ring can rotate relative to the housing.

8. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, 2, 3, 4 or 7, characterized in that, When a first clutch is provided, it is positioned between the first and second gear rings, with one end of the first clutch connected to the first gear ring and the other end connected to the second gear ring. The first clutch controls the engagement and disengagement of the first and second gear rings. A brake is positioned between the second gear ring and the housing, with one end connected to the second gear ring and the other end connected to the housing. A second one-way overrunning clutch is provided between the first and second gear rings. When driving in the forward direction and the forward rotation speed of the second gear ring is greater than that of the first gear ring, the second one-way overrunning clutch locks, and the second and first gear rings rotate synchronously. Otherwise, the second one-way overrunning clutch overruns.

9. The dual-motor dual-planetary gearbox power coupling assembly according to claim 1, 2, 3, 4, 5, 6 or 7, characterized in that, The second motor and the first motor are arranged opposite each other on two sides. The output end of the second planetary carrier is hollow. The output shaft of the second motor passes through the second planetary carrier and is connected to the second sun gear. The second sun gear is connected to the first planetary carrier. The second planetary carrier is fixed with a first gear. The first gear meshes with the second gear, and power is output from the second gear. When the second motor and the first motor are arranged opposite each other, a non-travel load is added. The input shaft of the non-travel load passes through the first motor and the first sun gear and is connected to the first planetary carrier through a second clutch to achieve a switchable transmission connection.

10. A method of operating the dual-motor dual-planetary gearbox power coupling assembly according to any one of claims 1, 2, 3, 4, 7, 8, and 9, characterized in that, 1) High torque mode: The brakes are engaged, and the first and second gear rings are braked by the housing through the brakes. At this time, the first and second motors rotate in the same direction. The power of the first motor is transmitted to the first planetary carrier through the first sun gear and the first planetary gear. According to the planetary gear motion law, when the first gear ring is braked, the rotation direction of the first planetary carrier remains unchanged and is the same as the rotation direction of the first motor. The power of the second motor is directly transmitted to the first planetary carrier and merges with the power transmitted from the first motor to the second sun gear. The power continues to be output from the second planetary carrier through the second planetary gear. According to the planetary gear motion law, when the second gear ring is braked, the rotation direction of the second planetary carrier remains unchanged and is the same as the rotation direction of the first and second motors. When the torque demand is not large, only the first motor or the second motor can be started, and the other motor can idle or be powered off. 2) High-speed mode: The brake is disengaged, and the first and second gear rings can rotate relative to the housing. At this time, the first and second motors rotate in the same direction. The power of the first motor is transmitted to the first gear ring through the first sun gear and the first planet gear. Part of the power of the second motor is transmitted to the first gear ring through the first planet carrier and the first planet gear, and then through the second gear ring and the second planet gear to the second planet carrier. The other part of the power of the second motor is transmitted to the second planet carrier through the second sun gear and the second planet gear, and then through the second gear ring to the second planet carrier, and output from the second planet carrier. 3) Switching from high torque mode to high speed mode: In high torque mode, when the speed of the first motor increases to a certain level and it is difficult to continue to increase or the efficiency of continuing to increase decreases significantly and the vehicle does not require high torque, the brake is disengaged, and the first and second gear rings can rotate relative to the housing. The assembly switches to high speed mode. At this time, the speeds of the first and second motors are adjusted so that the first and second motors work in the high-efficiency range. Under the condition of satisfying the drive torque and the motors working in the high-efficiency range, the speeds of the first and second motors are made similar or equal so that the relative speeds of the components of the first and second planetary gear sets are as small as possible or zero. 4) Switching from high-speed mode to high-torque mode: In high-speed mode, when the speed of the first motor decreases to a certain level and continues to decrease, resulting in a significant decrease in efficiency, or when the output torque of the high-speed mode is insufficient to meet the drive requirements, the speed of the first motor is gradually increased, while the speed of the second motor remains unchanged or is appropriately reduced. This causes the forward rotation speed of the first and second gear rings to gradually decrease to 0. Then, the first and second gear rings tend to reverse, causing the first one-way overrunning clutch to engage. This prevents the first and second gear rings from reversing and keeps them in a stopped state. At this time, the brake engages, fully braking the first and second gear rings. The assembly enters high-torque mode. Under the condition of meeting the drive torque, the output torque of the first and second motors is adjusted so that the two motors operate within the torque-efficient range. 5) Power supply: When the brake is powered off, power is transmitted from the wheels to the first motor and the second motor in the opposite direction of the drive path, so as to generate electricity for the first motor and the second motor.

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