Planetary differential torque vectoring device

Abstract

The utility model discloses a kind of planetary differential torque vector devices, including with composite planet carrier, composite planet carrier is equipped with composite big planet wheel and composite small planet wheel, the side of composite big planet wheel is equipped with left planet mechanism, left planet mechanism is connected to left half shaft in one end, and the other end is connected to composite small gear ring, and composite small gear ring is engaged with composite small planet wheel;The side of composite small planet wheel away from composite big planet wheel is equipped with right planet mechanism, right planet mechanism at least has first element, second element and right sun gear, and composite small sun gear is equipped on right sun gear, and first element is drivingly connected to composite planet carrier or composite small gear ring, and second element is used to receive the output torque of actuating assembly.The utility model has the beneficial effect mainly reflected in: composite planet mechanism and left planet mechanism mutually cooperate to make total speed ratio reach above 13, without making vector motor larger or increasing current, power of the system can be increased, effectively improve the economy of the system.

Description

Technical Field

[0001] This utility model relates to the field of automotive power chassis technology, and more specifically, to a planetary differential torque vectoring device. Background Technology

[0002] Conventional differential transmissions enable cornering by allowing the two drive wheels to rotate at different speeds. The transmission distributes drive torque equally to both wheels (open differential). The disadvantage is that the wheel with better traction only has as much traction as the wheel on a slippery surface or a wheel lightly loaded during cornering. A differential lock, which partially engages the two drive wheels through friction, can be used to increase traction and improve driving dynamics. With an adjustable differential lock, the cornering capability of an open differential can be combined with the improved traction of a locking differential. Differential transmissions are also called differentials or differential-compensated transmissions.

[0003] As disclosed in patent publication number CN120096312A, an electric vehicle drive device is provided, the device comprising: a first planetary gear set including three first planetary gear elements, wherein the first element is connected to a motor and the second element is connected to a first output shaft; a second planetary gear set including three second planetary gear elements, wherein the first element is connected to a third element of the three first planetary gear elements, the second element is connected to a second output shaft, and the third element is fixed; and a third planetary gear set including three third planetary gear elements, wherein the first element and the second element are respectively connected to two elements of the three first planetary gear elements, and the third element is connected to a torque vectoring motor. However, this device functions as a basic differential without torque differential. The two planetary gear sets need to satisfy 1 + |k1| = |k1| * |k2| (where || is the absolute value). Considering space and structural limitations, we take k1 = -4.5 and k2 = -1.222, resulting in a total speed ratio of 1 + |k1| * |k2| + |k1| (where || is the absolute value). Calculations show that this speed ratio is approximately 11. To ensure the vector motor does not rotate during straight-line travel, k3 = k2 = -1.222, a characteristic value less than the conventional design specification |-1.5|. In this implementation example, achieving this speed ratio through a positive conversion mechanism between the second and third planetary gear sets is not problematic; however, this doubles the number of planetary gears in the second and third planetary gear sets, leading to increased cost and reduced transmission efficiency. The arrangement of the third planetary gear set is complex, with many nested and circuitous shaft structures at the connection between the second and third planetary gear sets. Furthermore, the vector motor connects to the third planetary gear set via parallel shaft reduction, further increasing the system's complexity. Utility Model Content

[0004] The purpose of this invention is to overcome the shortcomings of the existing technology and provide a planetary differential torque vectoring device.

[0005] The objective of this utility model is achieved through the following technical solution: A planetary differential torque vectoring device includes a composite planetary carrier fixedly connected to a right half-shaft. The composite planetary carrier has a composite large planetary gear and a composite small planetary gear that rotate integrally with the same angular velocity. The composite large planetary gear receives the output torque of a drive motor. A left planetary mechanism is located on the side of the composite large planetary gear away from the composite small planetary gear. One end of the left planetary mechanism is connected to the left half-shaft, and the other end is driven to a composite small gear ring via a connecting shaft. The composite small gear ring meshes with the composite small planetary gear. The torque introduced by the composite small planetary gear is proportionally distributed between the composite small gear ring and the composite planetary carrier. A right planetary mechanism is located on the side of the composite small planetary gear away from the composite large planetary gear. The right planetary mechanism has at least a first element, a second element, and a right sun gear. A composite small sun gear that rotates synchronously with the right sun gear meshes with the composite planetary gear. The first element is driven to the composite planetary carrier or the composite small gear ring, and the second element receives the output torque of an actuation component.

[0006] Preferably, the left planetary mechanism includes a left planetary carrier and a first component. The first component has a second component and a third component that mesh with it. The second component is connected to the compound small gear ring through the connecting shaft. The third component is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier is fixedly connected to the left half-shaft. The left half-shaft is coaxial with the right half-shaft, the output shaft of the drive motor, and the output shaft of the vector motor.

[0007] Preferably, the first component includes a first planetary gear and a second planetary gear disposed on the left planetary carrier, the first planetary gear and the second planetary gear meshing with each other; the first planetary gear meshes with a second component, the second component being a left sun gear; the second planetary gear meshes with a third component, the third component being a left gear ring.

[0008] Preferably, the first component includes a first planetary gear and a second planetary gear that are integrally rotated at the same angular velocity on the left planet carrier. The first planetary gear meshes with the second component, which is the left large sun gear. The second planetary gear meshes with a third component, which is the left small sun gear.

[0009] Preferably, the first element is a right planetary carrier, the second element is a right ring gear, the right planetary carrier is connected to the composite planetary carrier, the right planetary carrier is provided with a right planetary gear, and the right planetary gear meshes with the right sun gear and the right ring gear.

[0010] Preferably, the first element is a right planetary carrier, the second element is a right ring gear, the right planetary carrier is connected to the composite planetary carrier, and the right planetary carrier is provided with a right major planetary gear and a right minor planetary gear that rotate integrally with the same angular velocity. The right major planetary gear meshes with the right sun gear, and the right minor planetary gear meshes with the right ring gear.

[0011] Preferably, the second element is a right planetary carrier, the first element is a right gear ring, the right gear ring is fixedly connected to the composite small gear ring, the right planetary carrier is provided with a right planetary gear, and the right planetary gear meshes with the right sun gear and the right gear ring.

[0012] Preferably, the second element is a right planetary carrier, and the first element is a right ring gear. The right planetary carrier is provided with a right major planet gear and a right minor planet gear that rotate integrally with the same angular velocity. The right minor planet gear meshes with the right ring gear, and the right major planet gear meshes with the right sun gear.

[0013] Preferably, the actuation component includes at least a vector motor, the output shaft of which is connected to the second element.

[0014] Preferably, the output shaft of the vector motor is equipped with a speed reducer.

[0015] The beneficial effects of this utility model are mainly reflected in: 1. The design is ingenious, with the first component directly connected to the composite planetary carrier or composite small gear ring, without any nested or convoluted structures, making the structural design easier and the cost lower. It ensures a smaller radial dimension while maintaining axial dimensions, resulting in a more rational and compact layout.

[0016] 2. The combination of the composite large planetary gear and the composite small planetary gear increases torque, allowing for more reasonable values ​​of the characteristic value k of each planetary gear set. Furthermore, the speed ratio of the entire system can be increased, resulting in a shorter drive motor, lower cost, and effective solution to the problem of insufficient differential torque, thus having a wide range of applicability.

[0017] 3. The combination of the compound planetary mechanism and the left planetary mechanism enables a total speed ratio of 13 or higher. This allows for the use of smaller vector motors, increasing the system's power without requiring larger vector motors or higher current, thus effectively improving the system's economy. Furthermore, this layout is rational and compact, reducing space requirements and making the system more miniaturized, which is beneficial for efficient layout design.

[0018] 4. The left planetary mechanism, compound planetary mechanism and right planetary mechanism are arranged side by side, which can significantly reduce the radial dimension and lower the overall height of the vehicle. At the same time, the speed ratio of the entire system can be larger, resulting in a shorter drive motor and lower cost.

[0019] 5. The space inside the composite planetary gear and the composite small planetary gear is used to arrange the splined internal and external gear hubs of the half shaft. This way, it will not occupy additional axial space outside the drive system. The half shaft can be made longer and its included angle can be arranged more optimally, solving the problems of the half shaft being too short and the ground clearance being too small in the coaxial system.

[0020] 6. In this application, the characteristic value of the composite planetary mechanism is k1=-5.5, the characteristic value of the left planetary mechanism is k2=2.182, and the characteristic value of the right planetary mechanism is k3=-4.26 or -4.78. The characteristic values ​​k1, k2 and k3 are all within the ideal range that can be achieved by conventional structural design and manufacturing. Therefore, there are no problems such as difficulty in selecting needle roller bearings, load sharing design and poor manufacturing process. The development and manufacturing difficulty is smaller, which is conducive to the development of enterprises.

[0021] 7. The reducer can reduce speed and increase torque, which can solve the problem of insufficient differential torque capacity of the vector motor. Attached Figure Description

[0022] The technical solution of this utility model will be further described below with reference to the accompanying drawings: Figure 1 : A schematic diagram of the structure of the first embodiment of this utility model; Figure 2 : A schematic diagram of the structure of the second embodiment of this utility model; Figure 3 : A schematic diagram of the structure of the third embodiment of this utility model; Figure 4 : A schematic diagram of the structure of the fourth embodiment of this utility model; Figure 5 : A schematic diagram of the structure of the fifth embodiment of this utility model; Figure 6 : A schematic diagram of the structure of the sixth embodiment of this utility model. Detailed Implementation

[0023] The present invention will now be described in detail with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments are not limited to the present invention, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the protection scope of the present invention.

[0024] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0025] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0026] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0027] like Figures 1 to 6 As shown, this utility model discloses a planetary differential torque vectoring device, including a left half-shaft 7 and a right half-shaft 5 arranged coaxially. A left planetary mechanism 2, a compound planetary mechanism 1, and a right planetary mechanism 3 are arranged sequentially between the left half-shaft 7 and the right half-shaft 5. The left planetary mechanism 2, the compound planetary mechanism 1, and the right planetary mechanism 3 are arranged side by side, which can significantly reduce the radial dimension and lower the height of the vehicle. At the same time, the speed ratio of the entire system can be larger, resulting in a shorter drive motor and lower cost.

[0028] In this utility model, the composite planetary mechanism 1 includes a composite planetary carrier 11 fixedly connected to the right half-shaft 5. The composite planetary carrier 11 is provided with a composite large planetary gear 12 and a composite small planetary gear 13 that rotate integrally with the same angular velocity. The composite large planetary gear and the composite small planetary gear cooperate with each other to increase torque, which can make the characteristic value k of each planetary gear set more reasonable, and the speed ratio of the whole system can be larger, making the drive motor shorter, the cost lower, and effectively solving the problem of insufficient differential torque, and has a wide range of applicability.

[0029] The composite planetary gear 12 meshes with the composite sun gear 16, which is fixedly mounted at the output end of the drive motor 4. A left planetary mechanism 2 is located on the side of the composite planetary gear 12 away from the composite planetary gear 13. One end of the left planetary mechanism 2 is connected to the left half-shaft 7, and the other end is connected to the composite pinion gear 15 via a connecting shaft 25. The composite pinion gear 15 meshes with the composite planetary gear 13, and the torque introduced by the composite planetary gear 13 is proportionally distributed between the composite pinion gear 15 and the composite planetary carrier 11. The composite planetary gear 13 has a right planetary mechanism 3 on the side away from the composite planetary gear 12. The right planetary mechanism 3 has at least a first element 31, a second element 34, and a right sun gear 33. The right sun gear 33 has a composite sun gear 14 that rotates synchronously with it. The composite sun gear 14 meshes with the composite planetary gear 13. The first element 31 is drive-connected to the composite planet carrier 11 or the composite small gear ring 15. The second element 34 is used to receive the output torque of the actuation component. The above design is ingenious. The space inside the composite planetary gear 12 and the composite planetary gear 13 is used to arrange the splined internal and external gear hubs of the half-shaft. This avoids occupying additional axial space outside the drive system, allowing the half-shaft to be made longer and its included angle to be arranged more optimally, solving the problems of excessively short half-shafts and insufficient ground clearance in coaxial systems.

[0030] In the above, the compound planetary mechanism 1 and the left planetary mechanism 2 are differential mechanisms that integrate reduction and differential functions. To meet the basic differential function of differential speed without torque difference, the two planetary gear sets must satisfy 1+|k1|=|k1|*|k2-1| (|| is the absolute value). The formula for calculating the characteristic value k of the compound planetary mechanism is: k=zr*zp1 / (zp2*zs), where zp1 is the number of teeth of the compound planetary gear meshing with the compound sun gear, and zp2 is... The number of teeth on the compound planetary gear meshing with the compound ring gear, zr is the number of teeth on the compound ring gear, and zs is the number of teeth on the compound sun gear. Because zp1 / zp2 is greater than 1, the compound planetary mechanism, through the stepped planetary gear arrangement, can easily achieve a large characteristic value k compared to a single-row ordinary planetary mechanism. Taking k1 = -5.5, then k2 = 2.182 for the left planetary mechanism. Therefore, the overall speed ratio is 1 + |k1|*|k2 - 1| + |k1| = 13 (|| is the absolute value). In the above, since the compound planetary mechanism 1 and the left planetary mechanism 2 cooperate to achieve an overall speed ratio of over 13, a smaller vector motor can be selected. This allows for increased power of the system without increasing the size or current of the vector motor, effectively improving the system's economy. Simultaneously, this layout is reasonable and compact, reducing space occupation and making the system smaller, which is beneficial for a rational layout.

[0031] Furthermore, the actuation component includes at least a vector motor 6, the output shaft of which is connected to the second element 34, and a reducer 61 is provided on the output shaft of the vector motor 6. The reducer 61 can reduce speed and increase torque, thus solving the problem of insufficient differential torque capacity of the vector motor. In addition, the drive motor 4 and the vector motor 6 are hydraulically or electrically driven; of course, other driving methods can also be used, all of which fall within the protection scope of this utility model.

[0032] like Figure 1 As shown in the first embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the composite small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 mounted on the left planetary carrier 21. The first planetary gear 221 and the second planetary gear 222 mesh with each other. The first planetary gear 221 meshes with the second component 23, which is the left sun gear. The second planetary gear 222 meshes with the third component 24, which is the left gear ring. The first element 31 is a right planetary carrier, and the second element 34 is a right gear ring. The right planetary carrier is connected to the composite planetary carrier 11. The right planetary carrier is provided with a right planetary gear 32, which meshes with the right sun gear 33 and the right gear ring.

[0033] The working process of the first embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft via the composite small gear ring 15, connecting shaft 25, left sun gear, second element 22, and left planetary carrier 21.

[0034] When the vehicle is cornering, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 works, and its output shaft transmits power to the compound planetary carrier 11 and the right sun gear 33 through the right ring gear and the right planetary gear. The compound planetary carrier 11 transmits power to the right half-shaft 5, and the right sun gear 33 transmits power to the compound small planetary gear 13. The compound small planetary gear 13 transmits power to the left half-shaft 7 through the compound small ring gear 15, the connecting shaft 25, the left sun gear, the first component 22, and the left planetary carrier 21. The torque transmitted to the left and right half-shafts is divided into left positive and right negative torques after the planetary gear ratio, or left negative and right positive torques of equal magnitude but opposite direction, ultimately creating a "differential torque" effect between the two half-shafts.

[0035] like Figure 2 As shown in the second embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the composite small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 mounted on the left planetary carrier 21. The first planetary gear 221 and the second planetary gear 222 mesh with each other. The first planetary gear 221 meshes with the second component 23, which is the left sun gear. The second planetary gear 222 meshes with the third component 24, which is the left gear ring. The first element 31 is a right planetary carrier, and the second element 34 is a right gear ring. The right planetary carrier is connected to the composite planetary carrier 11. The right planetary carrier is provided with a right large planetary gear 321 and a right small planetary gear 322 that rotate together at the same angular velocity. The right large planetary gear 321 meshes with the right sun gear 33, and the right small planetary gear 322 meshes with the right gear ring.

[0036] The working process of the second embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft 7 via the composite small gear ring 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21.

[0037] When the vehicle corners, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 operates, and its output shaft transmits power to the first element 32 through the right ring gear. The first element 32 transmits power to the right planetary carrier 31 and the right sun gear 33, respectively. The right planetary carrier 31 transmits power to the compound planetary carrier 11, which in turn transmits power to the right half-shaft 5. The right sun gear 33 transmits power to the compound planetary gear 13, and the compound planetary carrier 11 transmits power to the right half-shaft 5. Simultaneously, the compound planetary gear 13 transmits power to the left half-shaft 7 through the compound small ring gear 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21. The torque transmitted to the left and right half-shafts, after being processed by the planetary gear ratio, forms a torque that is positive on the left and negative on the right, or negative on the left and positive on the right, with equal magnitudes but opposite directions, ultimately creating a "differential torque" effect between the two half-shafts.

[0038] like Figure 3 As shown in the third embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the compound small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 that rotate integrally with the same angular velocity on the left planetary carrier 21. The first planetary gear 221 meshes with the second component 23, which is a left large sun gear. The second planetary gear 222 meshes with the third component 24, which is a left small sun gear. The first element 31 is a right planetary carrier, and the second element 34 is a right gear ring. The right planetary carrier is connected to the composite planetary carrier 11. The right planetary carrier is provided with a right planetary gear 32, which meshes with the right sun gear 33 and the right gear ring.

[0039] The working process of the third embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft 7 via the composite small gear ring 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21.

[0040] When the vehicle corners, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 operates, and its output shaft transmits power to the right planetary gears through the right ring gear. The right planetary gears then transmit power to the right planetary carrier 31 and the right sun gear 33. The right planetary carrier 31 transmits power to the compound planetary carrier 11, which in turn transmits power to the right half-shaft 5. The right sun gear 33 transmits power to the compound planetary gear 13, and the compound planetary carrier 11 transmits power to the right half-shaft 5. Simultaneously, the compound planetary gear 13 transmits power to the left half-shaft 7 through the compound small ring gear 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21. The torque transmitted to the left and right half-shafts, after being adjusted by the planetary gear ratio, forms a torque that is either positive on the left and negative on the right, or negative on the left and positive on the right, with equal magnitude but opposite direction, ultimately creating a "differential torque" effect between the two half-shafts.

[0041] like Figure 4 As shown in the fourth embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the compound small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 that rotate integrally with the same angular velocity on the left planetary carrier 21. The first planetary gear 221 meshes with the second component 23, which is a left large sun gear. The second planetary gear 222 meshes with the third component 24, which is a left small sun gear. The first element 31 is a right planetary carrier, and the second element 34 is a right gear ring. The right planetary carrier is connected to the composite planetary carrier 11. The right planetary carrier is provided with a right large planetary gear 321 and a right small planetary gear 322 that rotate together at the same angular velocity. The right large planetary gear 321 meshes with the right sun gear 33, and the right small planetary gear 322 meshes with the right gear ring.

[0042] The working process of this embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft 7 via the composite small gear ring 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21.

[0043] When the vehicle corners, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 operates, and its output shaft transmits power to the first element 32 through the right ring gear. The first element 32 transmits power to the right planetary carrier 31 and the right sun gear 33, respectively. The right planetary carrier 31 transmits power to the compound planetary carrier 11, which in turn transmits power to the right half-shaft 5. The right sun gear 33 transmits power to the compound planetary gear 13, and the compound planetary carrier 11 transmits power to the right half-shaft 5. Simultaneously, the compound planetary gear 13 transmits power to the left half-shaft 7 through the compound small ring gear 15, connecting shaft 25, left sun gear, first component 22, and left planetary carrier 21. The torque transmitted to the left and right half-shafts, after being adjusted by the planetary gear ratio, forms a torque that is either positive on the left and negative on the right, or negative on the left and positive on the right, with equal magnitudes but opposite directions, ultimately creating a "differential torque" effect between the two half-shafts.

[0044] In the first to fourth embodiments described above, the right planetary mechanism 3, through a reasonable speed ratio configuration, enables the right sun gear 33 and the first element 31 to act simultaneously as dual inputs when the left and right half-shafts rotate at the same speed. Calculations show that the speed ratio between the sun gear 33 and the planet carrier 31 is 4.26. In this example, when the characteristic value k3 of the right planetary mechanism is -4.26, the speed of the second element 34 is exactly 0 RPM, meaning the vector motor remains stationary.

[0045] Calculations show that the characteristic values ​​of the above-mentioned composite planetary mechanism are k1=-5.5, k2=2.182 for the left planetary mechanism, and k3=-4.26 for the right planetary mechanism. The characteristic values ​​k1, k2, and k3 are all within the ideal range that can be achieved by conventional structural design and manufacturing. Therefore, there are no problems with needle roller bearing selection, load sharing design, or poor manufacturing process. The development and manufacturing difficulty is lower, which is beneficial to the company's development.

[0046] like Figure 5As shown in the fifth embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the composite small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 mounted on the left planetary carrier 21. The first planetary gear 221 and the second planetary gear 222 mesh with each other. The first planetary gear 221 meshes with the second component 23, which is the left sun gear. The second planetary gear 222 meshes with the third component 24, which is the left gear ring. The second element 34 is a right planetary carrier, and the first element 31 is a right gear ring. The right gear ring is fixedly connected to the composite small gear ring 15. The right planetary carrier is provided with a right planetary gear 32, which meshes with the right sun gear 33 and the right gear ring.

[0047] The working process of the fifth embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft via the composite small gear ring 15, connecting shaft 25, left sun gear, second element 22, and left planetary carrier 21.

[0048] When the vehicle turns, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 operates, and its output shaft transmits power to the right ring gear and right sun gear 33 through the right planetary carrier and right planetary gears. The right ring gear transmits power to the right half-shaft 5 through the compound small sun gear 14 and the compound planetary carrier 11. At the same time, the right ring gear and the compound small ring gear 15 transmit power to the left half-shaft 7 through the connecting shaft 25, the left sun gear, the first component 22, and the left planetary carrier 21, respectively. The torque transmitted to the left and right half-shafts is divided into left positive and right negative torques, or left negative and right positive torques of equal magnitude but opposite direction, after the planetary gear ratio is adjusted. This ultimately creates a "differential torque" effect between the two half-shafts.

[0049] like Figure 6As shown in the sixth embodiment of this utility model, the left planetary gear mechanism 2 includes a left planetary carrier 21 and a first component 22. The first component 22 has a second component 23 and a third component 24 that mesh with it. The second component 23 is connected to the composite small gear ring 15 through the connecting shaft 25. The third component 24 is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier 21 is fixedly connected to the left half-shaft 7. The left half-shaft 7 is coaxial with the right half-shaft 5, the output shaft of the drive motor 4, and the output shaft of the vector motor 6. The first component 22 includes a first planetary gear 221 and a second planetary gear 222 mounted on the left planetary carrier 21. The first planetary gear 221 and the second planetary gear 222 mesh with each other. The first planetary gear 221 meshes with the second component 23, which is the left sun gear. The second planetary gear 222 meshes with the third component 24, which is the left gear ring. The second element 34 is a right planetary carrier, and the first element 31 is a right gear ring. The right planetary carrier is provided with a right major planetary gear 321 and a right minor planetary gear 322 that rotate together at the same angular velocity. The right minor planetary gear 322 meshes with the right gear ring, and the right major planetary gear 321 meshes with the right sun gear 33.

[0050] The working process of the fifth embodiment is briefly described below: When the vehicle is traveling in a straight line, the vector motor 6 is not working, but the drive motor 4 is working, transmitting power to the composite planetary gear 12 via the composite sun gear 16. Upon receiving power, the composite planetary gear 12 transmits it to the composite planetary carrier 11 and the composite planetary gear 13. The composite planetary carrier 11 then transmits power to the right half-shaft 5. Simultaneously, the composite planetary gear 13 transmits power to the left half-shaft via the composite small gear ring 15, connecting shaft 25, left sun gear, second element 22, and left planetary carrier 21.

[0051] When the vehicle turns, a speed difference occurs between the left and right half-shafts. At this time, the vector motor 6 operates, and its output shaft transmits power to the second planetary gear 222 and the right sun gear 33 through the right planetary carrier and the right small planetary gear 322. The right sun gear 33 then transmits power to the right half-shaft 5 through the compound small sun gear 14, the compound small planetary gear 13, and the compound planetary carrier 11. Simultaneously, the second planetary gear 222 and the compound small ring gear 15 transmit power to the left half-shaft 7 through the connecting shaft 25, the left sun gear, the first component 22, and the left planetary carrier 21, respectively. The torque transmitted to the left and right half-shafts is divided into positive on the left and negative on the right, or negative on the left and positive on the right, with equal magnitudes but opposite directions, ultimately creating a "differential torque" effect between the two half-shafts.

[0052] In the fifth and sixth embodiments described above, the right planetary mechanism 3, through a reasonable speed ratio configuration, allows the right sun gear 33 and the first element 31 to act simultaneously as dual inputs when the left and right half-shafts rotate at the same speed. Calculations show that the speed ratio between the sun gear 33 and the planet carrier 31 is 4.78. In this example, when the characteristic value k3 of the right planetary mechanism is -4.78, the speed of the second element 34 is exactly 0 RPM, meaning the vector motor remains stationary.

[0053] Calculations show that the characteristic values ​​of the aforementioned composite planetary mechanism are k1 = -5.5, the left planetary mechanism k2 = 2.182, and the right planetary mechanism k3 = -4.78. These characteristic values ​​are all within the ideal range achievable through conventional structural design and manufacturing. Therefore, there are no difficulties in selecting needle roller bearings, load-sharing design, or poor manufacturing processes. Development and manufacturing are significantly easier, which is beneficial for enterprise development. Where the connection of the various components is possible, a negative planetary gear set can be converted into a positive planetary gear set by adding a planetary gear between the planetary gears and the ring gear. In this case, the connection relationship between the ring gear and the planet carrier must be interchanged, and the static gear ratio must be increased by one, relative to the embodiment of the negative planetary gear set. Conversely, if the connection of the transmission components allows, a positive planetary gear set can also be replaced by a negative planetary gear set. In this case, with respect to the positive planetary gear set, the connection relationship between the ring gear and the planet carrier must also be interchanged, and the static gear ratio must be decreased by one and its sign must be changed. Those skilled in the art will understand that the same technical effect can be achieved in this way, with only differences in arrangement and connection method; such variations are also within the scope of this patent.

[0054] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0055] The detailed descriptions listed above are merely specific descriptions of feasible implementations of this utility model, and are not intended to limit the scope of protection of this utility model. All equivalent implementations or modifications made without departing from the spirit of this utility model should be included within the scope of protection of this utility model.

Claims

1. A planetary differential torque vectoring device, characterized in that: The system includes a composite planetary carrier (11) fixedly connected to the right half-shaft (5). The composite planetary carrier (11) is equipped with a composite large planetary gear (12) and a composite small planetary gear (13) that rotate integrally with the same angular velocity. The composite large planetary gear (12) receives the output torque of the drive motor (4). A left planetary mechanism (2) is located on the side of the composite large planetary gear (12) away from the composite small planetary gear (13). One end of the left planetary mechanism (2) is connected to the left half-shaft (7), and the other end is connected to the composite small gear ring (15) via a connecting shaft (25). The composite small gear ring (15) meshes with the composite small planetary gear (13), and the rotational torque introduced through the composite small planetary gear (13)... The torque is proportionally distributed on the compound small gear ring (15) and the compound planetary carrier (11); the compound small planetary gear (13) is provided with a right planetary mechanism (3) on the side away from the compound large planetary gear (12), the right planetary mechanism (3) has at least a first element (31), a second element (34) and a right sun gear (33), the right sun gear (33) is provided with a compound small sun gear (14) that rotates synchronously with it, the compound small sun gear (14) meshes with the compound small planetary gear (13), the first element (31) is drivenly connected to the compound planetary carrier (11) or the compound small gear ring (15), and the second element (34) is used to receive the output torque of the actuation component.

2. The planetary differential torque vectoring device according to claim 1, characterized in that: The left planetary mechanism (2) includes a left planetary carrier (21) and a first component (22). The first component (22) is provided with a second component (23) and a third component (24) that mesh with it. The second component (23) is connected to the compound small gear ring (15) through the connecting shaft (25). The third component (24) is fixedly mounted on the torque transfer mechanism housing. The left planetary carrier (21) is fixedly connected to the left half shaft (7). The left half shaft (7) is coaxial with the right half shaft (5), the output shaft of the drive motor (4), and the output shaft of the vector motor (6).

3. The planetary differential torque vectoring device according to claim 2, characterized in that: The first component (22) includes a first planetary gear (221) and a second planetary gear (222) disposed on the left planetary carrier (21), the first planetary gear (221) and the second planetary gear (222) meshing with each other; the first planetary gear (221) meshes with the second component (23), the second component (23) being the left sun gear; the second planetary gear (222) meshes with the third component (24), the third component (24) being the left gear ring.

4. The planetary differential torque vectoring device according to claim 2, characterized in that: The first component (22) includes a first planetary gear (221) and a second planetary gear (222) that rotate together at the same angular velocity on the left planetary carrier (21). The first planetary gear (221) meshes with the second component (23), which is the left large sun gear. The second planetary gear (222) meshes with the third component (24), which is the left small sun gear.

5. The planetary differential torque vectoring device according to claim 3 or 4, characterized in that: The first element (31) is a right planetary carrier, and the second element (34) is a right gear ring. The right planetary carrier is connected to the composite planetary carrier (11). The right planetary carrier is provided with a right planetary gear (32), which meshes with the right sun gear (33) and the right gear ring.

6. The planetary differential torque vectoring device according to claim 3 or 4, characterized in that: The first element (31) is a right planetary carrier, and the second element (34) is a right gear ring. The right planetary carrier is connected to the composite planetary carrier (11). The right planetary carrier is provided with a right large planetary gear (321) and a right small planetary gear (322) that rotate together at the same angular velocity. The right large planetary gear (321) meshes with the right sun gear (33), and the right small planetary gear (322) meshes with the right gear ring.

7. The planetary differential torque vectoring device according to claim 3, characterized in that: The second element (34) is a right planetary carrier, and the first element (31) is a right gear ring. The right gear ring is fixedly connected to the composite small gear ring (15). The right planetary carrier is provided with a right planetary gear (32), which meshes with the right sun gear (33) and the right gear ring.

8. The planetary differential torque vectoring device according to claim 3, characterized in that: The second element (34) is a right planetary carrier, and the first element (31) is a right gear ring. The right planetary carrier is provided with a right large planetary gear (321) and a right small planetary gear (322) that rotate together at the same angular velocity. The right small planetary gear (322) meshes with the right gear ring, and the right large planetary gear (321) meshes with the right sun gear (33).

9. The planetary differential torque vectoring device according to claim 1, characterized in that: The actuation assembly includes at least a vector motor (6), the output shaft of which is connected to the second element (34).

10. The planetary differential torque vectoring device according to claim 8, characterized in that: The vector motor (6) has a reducer (61) on its output shaft.

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