Differential torque system and vehicle

Abstract

The utility model provides a differential torque system and a vehicle, relates to the technical field of vehicle wheel train control, and enables left and right wheels of a driving shaft to drive the vehicle with different torques when the vehicle runs, so as to improve the steering flexibility of the vehicle and ensure the power performance of the vehicle on different road surfaces. The utility model provides a differential torque system which comprises a power output mechanism, a main shaft, a planetary speed reducing mechanism, a first planetary row mechanism, a second planetary row mechanism and a torque control mechanism. One end of the main shaft is connected with the output end of the power output mechanism, the other end of the main shaft is connected with the input end of the planetary reducing mechanism, the planetary reducing mechanism transmits power to the first planetary row mechanism and the second planetary row mechanism, the first planetary row mechanism is connected with a first half shaft of a vehicle, and the second planetary row mechanism is connected with a second half shaft of the vehicle; the torque control mechanism comprises a driving component and a meshing component, the meshing component is connected with the output end of the driving component, and the meshing component is meshed with the first gear ring and the second gear ring at the same time.

Description

TECHNICAL FIELD

[0001] The utility model relates to vehicle wheel train control technical field especially differential torque system and vehicle. BACKGROUND

[0002] The differential can realize the differential rotation of left and right wheels, thereby realizing the smooth steering of the vehicle or further realizing the function of getting out of trouble. But the differential function of the existing vehicle is passive, when the vehicle is steering, the speed of the left and right wheels is automatically adapted according to the steering requirement, so as to realize the steering function.

[0003] When the ground friction coefficients of the left and right wheels are different, the output torque must be reduced to ensure the stability of the vehicle, and the output capacity of the power system cannot be fully exerted. In recent years, the independent driving mode of the left and right wheels by using double-motor driving system is gradually increasing, but the cost of using two motors and system to realize the different torque output of the two wheels is high.

[0004] Therefore, it is necessary to provide a differential torque system and vehicle to solve the problems in the prior art. SUMMARY

[0005] The purpose of the present application is to provide a differential torque system and vehicle, so that the left and right wheels of the driving shaft drive the vehicle with different torques when the vehicle is running, so as to improve the steering flexibility of the vehicle and ensure the power performance of the vehicle on different roads.

[0006] The differential torque system provided by the utility model is used for vehicle, including power output mechanism, main shaft, planetary reduction mechanism, first planetary gear mechanism, second planetary gear mechanism and torque control mechanism, one end of the main shaft is connected with the output end of the power output mechanism, the other end is connected with the input end of the planetary reduction mechanism, the output end of the planetary reduction mechanism is connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism, the output end of the first planetary gear mechanism is connected with the first axle half of the vehicle, the output end of the second planetary gear mechanism is connected with the second axle half of the vehicle, the torque control mechanism includes driving member and meshing member, the first planetary gear mechanism includes first gear ring, the second planetary gear mechanism includes second gear ring, the meshing member is connected with the output end of the driving member, and the meshing member is engaged with the first gear ring and the second gear ring simultaneously.

[0007] The planetary reduction mechanism comprises a first sun gear, a first planetary gear, a third ring gear and a first planetary carrier; the main shaft is connected with the first sun gear, the first planetary gear is located between the third ring gear and the first sun gear and is in mesh with the inner teeth of the first sun gear and the third ring gear, and the first planetary carrier is connected with the first planetary gear; the first planetary carrier is formed with an output shaft, and the output shaft is connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism.

[0008] Specifically, the first planetary gear mechanism further comprises a second sun gear, a second planetary gear and a second planetary carrier; the second sun gear is connected with the output shaft, the second planetary gear is located between the first ring gear and the second sun gear and is in mesh with the inner teeth of the second sun gear and the first ring gear, and the output end of the second planetary carrier is connected with the first half shaft; the outer teeth of the first ring gear are in mesh with the meshing member.

[0009] Further, the second planetary gear mechanism further comprises a third sun gear, a third planetary gear and a third planetary carrier; the third sun gear is connected with the output shaft, the third planetary gear is located between the second ring gear and the third sun gear and is in mesh with the inner teeth of the third sun gear and the second ring gear, and the output end of the third planetary carrier is connected with the second half shaft; the outer teeth of the second ring gear are in mesh with the meshing member.

[0010] The power output mechanism comprises a driving motor, the driving motor comprises a stator and a rotor, and the main shaft is connected with the rotor.

[0011] Specifically, the meshing member is a bevel gear, and the outer teeth of the first ring gear and the second ring gear are bevel teeth.

[0012] Further, the meshing member is a first transmission shaft or a helical gear; when the meshing member is a first transmission shaft, the torque control mechanism further comprises a second transmission shaft, a third transmission shaft, a first transmission bevel gear and a second transmission bevel gear; the first transmission shaft is located between the second transmission shaft and the third transmission shaft and is in contact with the second transmission shaft and the third transmission shaft, the first transmission bevel gear is connected with the second transmission shaft and is in mesh with the outer ring of the first ring gear, and the second transmission bevel gear is connected with the third transmission shaft and is in mesh with the outer ring of the second ring gear; when the meshing member is a helical gear, the first ring gear and the second ring gear are both helical gears.

[0013] The planetary reduction mechanism comprises a first reduction assembly and a second reduction assembly, the first reduction assembly and the second reduction assembly are oppositely arranged on two sides of the power output mechanism, the first reduction assembly is connected with the first planetary gear set, and the second reduction assembly is connected with the second planetary gear set.

[0014] Specifically, the torque control mechanism further comprises a first transmission member and a second transmission member, the first transmission member is matched with the first ring gear, the second transmission member is matched with the second ring gear, and the first transmission member and the second transmission member are simultaneously engaged with the engaging member.

[0015] Compared with the prior art, the differential torque system has the following advantages:

[0016] The differential torque system is used for a vehicle and comprises a power output mechanism, a main shaft, a planetary reduction mechanism, a first planetary gear set, a second planetary gear set and a torque control mechanism. The output end of the planetary reduction mechanism is connected with the input end of the first planetary gear set and the input end of the second planetary gear set. The output end of the first planetary gear set is connected with a first half shaft of the vehicle, and the output end of the second planetary gear set is connected with a second half shaft of the vehicle. The torque control mechanism comprises a driving member and an engaging member, the first planetary gear set comprises a first ring gear, the second planetary gear set comprises a second ring gear, the engaging member is connected with the output end of the driving member, and the engaging member is simultaneously engaged with the first ring gear and the second ring gear.

[0017] According to the analysis, the power output mechanism can output power to the whole system.

[0018] The output end of the planetary reduction mechanism is connected with the input end of the first planetary gear set and the input end of the second planetary gear set. The output end of the first planetary gear set is connected with a first half shaft of the vehicle, and the output end of the second planetary gear set is connected with a second half shaft of the vehicle.

[0019] When the differential torque function needs to be realized, since the meshing member capable of meshing with the outer ring of the first ring gear and the outer ring of the second ring gear is further provided, and the meshing member is connected with the driving member, when the driving member drives the meshing member to rotate, the first ring gear and the second ring gear located on both sides of the meshing member and simultaneously meshing with the meshing member can rotate, but the rotating directions are opposite.

[0020] It can be understood that since the inputs of the first planetary gear mechanism and the second planetary gear mechanism both rely on the output end of the planetary reduction mechanism, the power inputs obtained by the first planetary gear mechanism and the second planetary gear mechanism are consistent, and since the rotating directions of the first ring gear and the second ring gear are opposite, when the driving member drives the meshing member to rotate, the output torques of the first planetary gear mechanism and the second planetary gear mechanism will inevitably be different, thus not only the function of simultaneously driving the first planetary gear mechanism and the second planetary gear mechanism by using one driving member is realized, but also the torque adjustment is realized, and since the torque adjustment is realized under the action of the driving member, the initiative of the torque adjustment is simultaneously realized.

[0021] In addition, the utility model provides a kind of vehicle, including above-mentioned differential torque system.

[0022] The vehicle using the differential torque system provided by the present application can simultaneously realize active adjustment of torque, and only one driving member is used to realize torque adjustment, greatly saving the overall production cost, and correspondingly, the required control system logic is more simplified, reducing the cost of design and later maintenance. At the same time, according to the different needs of left and right wheels and the ground friction coefficient input, the output torque of one side wheel is further increased without affecting the main output power of the power output mechanism, so that the steering of the whole vehicle is more smooth, the energy consumption is lower, and the vehicle also has good escape ability. BRIEF DESCRIPTION OF DRAWINGS

[0023] In order to more clearly illustrate the specific embodiments of the utility model or the technical solutions in the prior art, the following will briefly introduce the drawings needed to be used in the specific embodiments or prior art description. Obviously, the drawings in the following description are some embodiments of the utility model, and those skilled in the art can also obtain other drawings according to these drawings without creating any creative labor.

[0024] Figure 1 The layout schematic diagram of the first embodiment of the differential torque system provided by the utility model embodiment is shown in the figure.

[0025] Figure 2 The layout schematic diagram of the second embodiment of the differential torque system provided by the utility model embodiment is shown in the figure.

[0026] Figure 3 A layout schematic diagram of a third implementation of the differential torque system according to the embodiments of the present application is provided.

[0027] Figure 4 A layout schematic diagram of a fourth implementation of the differential torque system according to the embodiments of the present application is provided.

[0028] In the figure: 1 - driving motor; 101 - stator; 102 - rotor; 2 - main shaft; 3 - first sun gear; 4 - first planetary gear; 5 - third ring gear; 6 - first carrier; 7 - second sun gear; 8 - second planetary gear; 9 - first ring gear; 10 - second carrier; 11 - third sun gear; 12 - third planetary gear; 13 - second ring gear; 14 - third carrier; 15 - driving member; 16 - meshing member; 17 - first transmission member; 18 - second transmission member; 19 - first speed reduction assembly; 20 - second speed reduction assembly; 21 - first half shaft; 22 - second half shaft. DETAILED DESCRIPTION

[0029] The technical solutions of the present application will be described clearly and completely below in combination with the drawings. Obviously, the described embodiments are only some of the embodiments of the present application, but not all the embodiments of the present application.

[0030] The components of the embodiments of the present application generally described and shown in the drawings herein can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present application provided in the drawings is not intended to limit the scope of the claimed present application, but only represents selected embodiments of the present application.

[0031] Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0032] In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, the terms "first", "second", "third" are only for the purpose of description, and cannot be understood as indicating or implying relative importance.

[0033] In the description of the utility model, it is necessary to explain that, unless there is definite stipulation and limitation, the term "installation", "connection" should be broad sense understanding, for example, it can be fixed connection, also can be detachable connection, or integrally connected;It can be mechanical connection, also can be electrical connection;It can be directly connected, also can be indirectly connected through intermediate medium, it can be the communication inside two elements.For ordinary skilled person in the art, the specific meaning of the above-mentioned term in the utility model can be understood according to specific circumstances.

[0034] As Figure 1 The utility model provides differential torque system for vehicle, including power output mechanism, main shaft 2, planetary reduction mechanism, first planetary gear mechanism, second planetary gear mechanism and differential torque control mechanism, one end of main shaft 2 is connected with the output end of power output mechanism, the other end is connected with the input end of planetary reduction mechanism, the output end of planetary reduction mechanism is connected with the input end of first planetary gear mechanism and the input end of second planetary gear mechanism, the output end of first planetary gear mechanism is connected with the first axle half 21 of vehicle, and the output end of second planetary gear mechanism is connected with the second axle half 22 of vehicle;Differential torque control mechanism includes driving member 15 and meshing member 16, first planetary gear mechanism includes first ring gear 9, and second planetary gear mechanism includes second ring gear 13, and meshing member 16 is connected with the output end of driving member 15, and meshing member 16 is engaged with first ring gear 9 and second ring gear 13 simultaneously.

[0035] Compared with the prior art, the differential torque system provided by the utility model has the following advantages:

[0036] The differential torque system provided by the utility model can output power to the overall system through the power output mechanism, and since one end of the main shaft 2 is connected with the power output mechanism in the application, the power can be further transmitted outward by the main shaft 2, accordingly, by connecting the other end of the main shaft 2 with the planetary reduction mechanism, the power can be transmitted to the planetary reduction mechanism, and one-stage reduction is realized through the planetary reduction mechanism.

[0037] Since the output end of the planetary reduction mechanism is connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism, and the output end of the first planetary gear mechanism is connected with the first axle half 21 of the vehicle, and the output end of the second planetary gear mechanism is connected with the second axle half 22 of the vehicle, the first axle half 21 and the second axle half 22 can be driven to rotate synchronously through the first planetary gear mechanism and the second planetary gear mechanism, thereby realizing the synchronous rotation of the left and right wheels of the vehicle.

[0038] When the differential torque function needs to be realized, since the meshing member 16 capable of meshing with the outer ring of the first ring gear 9 and the outer ring of the second ring gear 13 is further provided in the application, and the meshing member 16 is connected with the driving member 15, when the driving member 15 drives the meshing member 16 to rotate, the first ring gear 9 and the second ring gear 13 located on both sides of the meshing member 16 and simultaneously meshing with the meshing member 16 can rotate, but the rotating directions are opposite. When the differential control function is not needed, the meshing member 16 is in a free state, and the driving member 15 has no torque output to the meshing member 16.

[0039] It can be understood that since the inputs of the first planetary gear mechanism and the second planetary gear mechanism both rely on the output end of the planetary reduction mechanism, the power rotating speeds obtained by the first planetary gear mechanism and the second planetary gear mechanism are consistent, and since the rotating directions of the first ring gear 9 and the second ring gear 13 are opposite, when the driving member 15 drives the meshing member 16 to rotate, the output torques of the first planetary gear mechanism and the second planetary gear mechanism will inevitably be different, thus not only the function of simultaneously driving the first planetary gear mechanism and the second planetary gear mechanism by using one driving member 15 is realized, but also the torque adjustment is realized, and since the torque adjustment is realized under the action of the driving member 15, the initiative of the torque adjustment is simultaneously realized.

[0040] Embodiment 1

[0041] As shown in Figure 1 the planetary reduction mechanism in the application includes a first sun gear 3, a first planet gear 4, a third ring gear 5, and a first planet carrier 6; the main shaft 2 is connected with the first sun gear 3, the first planet gear 4 is located between the third ring gear 5 and the first sun gear 3 and simultaneously meshes with the inner teeth of the first sun gear 3 and the third ring gear 5, and the first planet carrier 6 is connected with the first planet gear 4; the first planet carrier 6 forms an output shaft, and the output shaft is connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism.

[0042] By arranging the planetary reduction mechanism at the output end of the main shaft 2, the first-stage reduction function can be realized, and by connecting the main shaft 2 with the first sun gear 3, the power can be transmitted to the first sun gear 3, and when the first sun gear 3 rotates, the first planet gear 4 can be driven to rotate. It can be understood that the third ring gear 5 is fixedly arranged in the application, and the first planet gear 4 is a plurality of, preferably three, and the three first planet gears 4 are commonly connected with the first planet carrier 6, and when the first sun gear 3 rotates, the first planet gear 4 can be driven to rotate under the common action of the third ring gear 5, so as to move along the circumferential direction of the first sun gear 3 and drive the first planet carrier 6 to rotate.

[0043] The first planet carrier 6 is formed with an output shaft, and in this embodiment, the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism are both connected to the output shaft of the first planet carrier 6, so that the first planetary gear mechanism and the second planetary gear mechanism are coaxially synchronized, so that when the driving member 15 inputs power to the meshing member 16, the power can be coupled through the first ring gear 9 and the second ring gear 13 and the power input by the output shaft, and since the rotational speeds of the first ring gear 9 and the second ring gear 13 are the same and the directions are opposite, the actual power input is one increase and one decrease, that is, if the power output by the output shaft is X, the power obtained by the first ring gear 9 is Y, and the power obtained by the second ring gear 13 is -Y, so that the actual power output by the first planetary gear mechanism is X+Y, and the actual power output by the second planetary gear mechanism is X-Y, so as to realize different power outputs of the first half shaft 21 and the second half shaft 22, and further realize differential differential torsional motion of the left and right wheels.

[0044] It should be noted here that the driving member 15 in the present application is a motor, which can output a rotational speed matching the output shaft of the first planet carrier 6 in an extreme case, so that the output torque of the second planetary gear mechanism is converted to the first planetary gear mechanism through the ring gear transmission, so that the actual output power of the first planetary gear mechanism is 2X, and the actual output power of the second planetary gear mechanism is 0, that is, a wheel rotates and the other wheel does not rotate, or further, the vehicle can have a certain degree of escape ability in some extreme road conditions.

[0045] Correspondingly, since the differential differential torsional motion of the wheels in the present application is realized by further adding the driving member 15, the meshing member 16 and the corresponding first ring gear 9 and second ring gear 13, the power input of the power input mechanism is not affected, so as to ensure that the power input mechanism can exert maximum power, and further realize greater output torque to the wheel with greater adhesion.

[0046] Moreover, when the conventional scheme controls the vehicle to slip, it always causes a sudden change in rotational speed or causes a decrease in adhesion of the wheels to the ground or after the sudden change in rotational speed, the efficiency of the vehicle is reduced. The power input by the driving member 15 in the present application can make the change in rotational speed more stable, and even when a single wheel slips, the output torque can be automatically adjusted to improve the driving experience.

[0047] As Figures 1-4As shown, the first planetary gear mechanism in the application further comprises a second sun gear 7, a second planetary gear 8 and a second planetary carrier 10; the second sun gear 7 is connected with the output shaft, the second planetary gear 8 is located between the first ring gear 9 and the second sun gear 7 and is engaged with the second sun gear 7 and the inner teeth of the first ring gear 9 at the same time, the output end of the second planetary carrier 10 is connected with the first half shaft 21 through gear engagement; the outer teeth of the first ring gear 9 are engaged with the engagement member 16.

[0048] The second planetary gear mechanism comprises a third sun gear 11, a third planetary gear 12 and a third planetary carrier 14; the third sun gear 11 is connected with the output shaft, the third planetary gear 12 is located between the second ring gear 13 and the third sun gear 11 and is engaged with the third sun gear 11 and the inner teeth of the second ring gear 13 at the same time, the output end of the third planetary carrier 14 is connected with the second half shaft 22; the outer teeth of the second ring gear 13 are engaged with the engagement member 16.

[0049] In the embodiment, as shown, Figure 1 the output shaft of the first planetary carrier 6 is connected with the second sun gear 7 and the third sun gear 11, so as to synchronously drive the second sun gear 7 and the third sun gear 11 to rotate, when the second sun gear 7 rotates, the second planetary gear 8 can be driven to rotate, when the third sun gear 11 rotates, the third planetary gear 12 can be driven to rotate.

[0050] It can be understood that, since the engagement member 16 is engaged with the first ring gear 9 and the second ring gear 13, when the driving member 15 does not input power, the engagement member 16 has no driving torque, so that the first ring gear 9 and the second ring gear 13 can be in a free linkage state through the engagement member 16, and when the driving member 15 inputs power, the engagement member 16 can drive the first ring gear 9 and the second ring gear 13 to rotate, so as to affect the rotation of the second planetary gear 8 and the third planetary gear 12. Since the second planetary gear 8 is connected with the second planetary carrier 10 and the third planetary gear 12 is connected with the third planetary carrier 14, the power output by the second planetary carrier 10 and the power output by the third planetary carrier 14 can be affected. When the driving member 15 does not input power, the power output by the first planetary carrier 6 is evenly transmitted to the second sun gear 7 and the third sun gear 11, so that the second planetary carrier 10 and the third planetary carrier 14 output the same power; when the driving member 15 inputs power, the power output by the second planetary carrier 10 and the third planetary carrier 14 is different, under the action of the driving member 15, one of the planetary carriers outputs decreased power and the other planetary carrier outputs increased power, here the power refers to the same numerical value of the amount of decrease and increase of the torque, so as to realize the differential torque rotation of the first half shaft 21 and the second half shaft 22.

[0051] Optionally, as shown, Figures 1-4As shown, the power output mechanism in the present application comprises a driving motor 1, the driving motor 1 comprises a stator 101 and a rotor 102, and a main shaft 2 is connected with the rotor 102.

[0052] It should be noted here that, in the embodiment shown in the figure, Figures 1-3 In the embodiment shown in the figure, the main shaft 2 in the present application is a hollow shaft, the first half shaft 21 is a right half shaft, the second half shaft 22 is a left half shaft, and the second half shaft 22 is connected with the third planet carrier 14 and then passes through the main shaft 2 to be connected with the left wheel.

[0053] In the embodiment shown in the figure, Figure 1 As shown, the meshing member 16 is a bevel gear, and the outer teeth of the first ring gear 9 and the second ring gear 13 are all bevel teeth.

[0054] The power can be reversed by the bevel gear, so as to realize the purpose of transmitting power to the first ring gear 9 and the second ring gear 13.

[0055] Embodiment 2

[0056] As shown in the figure, Figure 2 The meshing member 16 in the present application is a first transmission shaft or a helical gear; when the meshing member 16 is a first transmission shaft, the torque control mechanism further comprises a second transmission shaft, a third transmission shaft, a first transmission bevel gear and a second transmission bevel gear; the first transmission shaft is located between the second transmission shaft and the third transmission shaft and is in contact with the second transmission shaft and the third transmission shaft, the first transmission bevel gear is connected with the second transmission shaft and is in meshing engagement with the outer ring of the first ring gear 9, and the second transmission bevel gear is connected with the third transmission shaft and is in meshing engagement with the outer ring of the second ring gear 13; when the meshing member 16 is a helical gear, the first ring gear 9 and the second ring gear 13 are both helical gears.

[0057] Based on the structure provided in Embodiment 1, in Embodiment 2, only the torque control mechanism is optimized, and it can be understood that, since the torque control mechanism only provides control torque power input, the meshing member 16 can be a first transmission shaft, and the second transmission shaft and the third transmission shaft are simultaneously in abutment with the first transmission shaft, so as to realize the transfer of power through friction, and correspondingly, the second transmission shaft and the third transmission shaft have the same speed and opposite directions. Since the first transmission bevel gear is further connected to the second transmission shaft and the second transmission bevel gear is connected to the third transmission shaft in the present application, the first transmission bevel gear and the second transmission bevel gear can be correspondingly meshed with the first ring gear 9 and the second ring gear 13 to realize power transmission.

[0058] When the meshing member 16 adopts a helical gear, the side wall of the first ring gear 9 and the second ring gear 13 in the present application is formed with helical gear teeth, so as to cooperate with the meshing member 16 to realize the rotation of the first ring gear 9 and the second ring gear 13.

[0059] It should be noted that, in addition to the above embodiments, as shown in Figure 3 The torque control mechanism provided by the present application can also adopt a two-stage parallel shaft gear structure to achieve power transmission, which is another deformation of the power transmission mechanism, and will not be described here.

[0060] Embodiment 3

[0061] In this embodiment, as shown in Figure 4 The planetary reduction mechanism includes a first reduction assembly 19 and a second reduction assembly 20, which are arranged on the two sides of the power output mechanism, and the first reduction assembly 19 is connected with the first planetary row mechanism, and the second reduction assembly 20 is connected with the second planetary row mechanism.

[0062] In this embodiment, the planetary reduction mechanism in Embodiments 1 and 2 is divided into two halves, and accordingly, the first half shaft 21 and the second half shaft 22 are respectively located on the two sides of the power output mechanism, so that the main shaft 2 can adopt any form, and accordingly, the structure is more clearly and symmetrically distributed.

[0063] In this embodiment, the first reduction assembly 19 and the second reduction assembly 20 each include the first sun gear 3, the first planetary gear 4, the third ring gear 5, and the first planet carrier 6 described above, and the two ends of the main shaft 2 protrude from the rotor 102, so as to achieve connection with the first sun gear 3 of the first reduction assembly 19 and the second sun gear 7 of the second reduction assembly 20.

[0064] Correspondingly, in this embodiment, the third ring gear 5 is also in a fixed state, and when the first sun gear 3 rotates, it can transmit power to the first planetary gear 4, thereby driving the first planet carrier 6 to rotate. At the same time, the output shaft formed by the first planet carrier 6 can be connected with the corresponding second sun gear 7 and third sun gear 11 on the corresponding side, thereby achieving power transmission.

[0065] In this embodiment, as shown in Figure 4 Since the first planetary row mechanism and the second planetary row mechanism are also arranged on the two sides of the power output mechanism, in order to ensure power transmission of the torque control mechanism, the size of the torque control mechanism of this embodiment needs to be increased. Therefore, as shown in Figure 4 In this embodiment, the torque control mechanism further includes a first transmission member 17 and a second transmission member 18, the first transmission member 17 is matched with the first ring gear 9, the second transmission member 18 is matched with the second ring gear 13, and the first transmission member 17 and the second transmission member 18 are simultaneously engaged with the meshing member 16.

[0066] The first transmission member 17 and the second transmission member 18 in the embodiment can be one or more, and the first transmission member 17 and the second transmission member 18 are bevel gears, which are increased or decreased according to specific added sizes, the transmission processes are consistent with the transmission processes described above, and power coupling is realized by transmitting the power output by the motor to the first gear ring 9 and the second gear ring 13 through the meshing member 16, which will not be described here.

[0067] In addition, the utility model still provides a vehicle, including the differential torque system above.

[0068] The vehicle adopting the differential torque system provided by the application can simultaneously realize active adjustment of differential torque, and the differential torque adjustment can be realized by only using one driving member 15, thereby greatly saving the overall production cost, and correspondingly, the required control system logic is more simplified, and the design and later maintenance cost is reduced. Meanwhile, the differential torque system can further increase the output torque of one side wheel according to the different requirements of the left and right wheels and the ground friction coefficient input without affecting the main output power of the power output mechanism, so that the steering of the overall vehicle is more smooth, the energy consumption is lower, and the vehicle also has good escape ability.

[0069] When the vehicle is steering, the differential torque system provided by the application can realize different rotation torques of the left and right wheels, so that the steering is smoothly realized, and the vehicle does not need a steering assist system; in addition, on the road surface with different friction coefficients, the wheels can be driven with different torques to fully adapt to the ground state, and the driving anti-skid does not need to borrow the braking system, and the vehicle can be provided with more technical solutions.

[0070] It should be noted here that the differential torque system provided by the application can more easily realize four-wheel drive of the vehicle, and only two sets of front and rear electric drive systems are needed to realize the four-wheel drive. However, on the traditional oil vehicle, higher technology is often needed to realize the four-wheel drive, so that the four-wheel drive vehicle is expensive, and even up to now, the oil consumption problem has not been solved, which seriously wastes fuel and causes high vehicle use cost. The new energy vehicle needs four motors and four systems to realize the four-wheel drive, and the cost is considerable. Even on the two-wheel drive vehicle, the application scheme is obviously better than the current double-motor system, which obviously reduces the vehicle price and improves the use economy.

[0071] Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the utility model, and not to limit them; although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that: the technical solutions recorded in the foregoing embodiments can still be modified, or some or all of the technical features can be replaced equivalently; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the utility model.

Claims

1. A differential torque system for a vehicle, characterized by, The power output mechanism, the main shaft, the planetary reduction mechanism, the first planetary gear mechanism, the second planetary gear mechanism and the torque control mechanism are arranged in series. One end of the main shaft is connected with the output end of the power output mechanism, and the other end is connected with the input end of the planetary reduction mechanism. The output end of the planetary reduction mechanism is connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism.

2. The differential torque system of claim 1, wherein, The output end of the first planetary gear mechanism is connected with the first half axle of the vehicle, and the output end of the second planetary gear mechanism is connected with the second half axle of the vehicle. The torque control mechanism comprises a driving member and an engaging member. The first planetary gear mechanism comprises a first ring gear, and the second planetary gear mechanism comprises a second ring gear.

3. The differential torque system of claim 2, wherein, The engaging member is connected with the output end of the driving member and simultaneously engaged with the first ring gear and the second ring gear. The planetary reduction mechanism comprises a first sun gear, a first planetary gear, a third ring gear and a first planetary carrier. The main shaft is connected with the first sun gear.

4. The differential torque system of claim 2, wherein, The first planetary gear is located between the third ring gear and the first sun gear and simultaneously engaged with the inner teeth of the first sun gear and the third ring gear. The first planetary carrier is connected with the first planetary gear. The first planetary carrier is formed with an output shaft connected with the input end of the first planetary gear mechanism and the input end of the second planetary gear mechanism.

5. The differential torque system of claim 1, wherein, The first planetary gear mechanism further comprises a second sun gear, a second planetary gear and a second planetary carrier.

6. The differential torque system of claim 1, wherein, The second sun gear is connected with the output shaft.

7. The differential torque system of claim 1, wherein, The second planetary gear is located between the first ring gear and the second sun gear and simultaneously engaged with the inner teeth of the second sun gear and the first ring gear. The output end of the second planetary carrier is connected with the first half axle. The outer teeth of the first ring gear are engaged with the engaging member. The second planetary gear mechanism further comprises a third sun gear, a third planetary gear and a third planetary carrier. The third sun gear is connected with the output shaft. The third planetary gear is located between the second ring gear and the third sun gear and simultaneously engaged with the inner teeth of the third sun gear and the second ring gear. The output end of the third planetary carrier is connected with the second half axle. The outer teeth of the second ring gear are engaged with the engaging member. The power output mechanism comprises a driving motor. The driving motor comprises a stator and a rotor. The main shaft is connected with the rotor. The engaging member is a bevel gear. The outer teeth of the first ring gear and the second ring gear are bevel teeth. The engaging member is a first transmission shaft or a helical gear. When the engaging member is a first transmission shaft, the torque control mechanism further comprises a second transmission shaft, a third transmission shaft, a first transmission bevel gear and a second transmission bevel gear. The first transmission shaft is located between the second transmission shaft and the third transmission shaft and in contact with the second transmission shaft and the third transmission shaft. The first transmission bevel gear is connected with the second transmission shaft and engaged with the outer ring of the first ring gear. The second transmission bevel gear is connected with the third transmission shaft and engaged with the outer ring of the second ring gear. When the engaging member is a helical gear, the first ring gear and the second ring gear are both helical gears.

8. The differential torque system of claim 1, wherein, The planetary reduction mechanism comprises a first reduction assembly and a second reduction assembly, the first reduction assembly and the second reduction assembly are oppositely arranged on two sides of the power output mechanism, and the first reduction assembly is connected with the first planetary gear set, and the second reduction assembly is connected with the second planetary gear set.

9. The differential torque system of claim 8, wherein, The torque control mechanism further comprises a first transmission member and a second transmission member, the first transmission member is matched with the first ring gear, the second transmission member is matched with the second ring gear, and the first transmission member and the second transmission member are simultaneously engaged with the engaging member.

10. A vehicle characterized by comprising: The differential torque system comprises the differential torque system according to any one of claims 1-9.

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