Differential and method of operating same

Abstract

The invention discloses a differential mechanism and an operation method thereof. The differential mechanism comprises an input gear assembly, a gear assembly assembled in the input gear assembly, a disengaging selection assembly, a decoupling selection assembly and a differential mechanism connecting flange set, wherein the disengaging selection assembly and the decoupling selection assembly are matched with the gear assembly to achieve different functions. The differential mechanism can achieve the functions of normal differential, differential locking, power disengaging, independent power obtaining of the left wheel and the right wheel and the like, and is particularly suitable for being arranged on a four-wheel-drive vehicle driven by front and rear motors. Wherein the front-back disengagement function is realized on the basis of good road conditions, the vehicle supports a timely four-wheel drive mode, energy consumption is saved, and if a certain power system breaks down, the disengagement function is used for achieving fault cut-off, and it is guaranteed that the vehicle continues to run to a maintenance point; the differential lock function is realized based on insufficient adhesive force of a certain wheel of the vehicle, and the vehicle is helped to complete limit escape by locking the differential lock; the function of decoupling the left and right wheels is realized based on the rotating speeds of the wheels and the motor which obtain power through adjustment, so that the vehicle can turn around in a tank and in situ, and turning of the vehicle is completed under the limit condition.

Description

Technical Field

[0001] The present invention relates to the technical field of differentials and methods of operating the same. Background Art

[0002] The automotive differential is an important component in the automotive transmission system. Its main function is to make the left and right wheels rotate at different speeds when the car is turning or driving on uneven roads, thereby ensuring that the drive wheels on both sides perform pure rolling motion, avoiding sliding friction between the wheels and the ground, reducing tire wear, and improving the driving stability of the car.

[0003] In front-wheel drive vehicles, the differential is installed on the front drive axle, called the front differential. The differential of rear-wheel drive vehicles is installed on the rear drive axle, called the rear differential. In addition to the front and rear differentials, four-wheel drive vehicles are also equipped with a central differential to adjust the speed difference and torque of the front axle to adjust the speed of the front and rear wheels. The central differential can reasonably distribute power between the front and rear axles according to different road conditions and driving requirements, thereby improving the driving stability of the vehicle.

[0004] At present, most hybrid and new energy four-wheel drive models on the market are basically front and rear dual-motor four-wheel drive solutions, equipped with open differentials or differentials with differential locks, but these two types of differentials cannot maximize the advantages of the front and rear dual motors.

[0005] Based on this, a new type of differential is now studied, which can not only perform normal differential and locking, and allow the left and right wheels to obtain power independently, but also can disconnect the power. It is particularly suitable for equipping four-wheel drive models driven by front and rear dual motors to maximize the advantages of the front and rear dual motors. Summary of the invention

[0006] Purpose of the invention: The technical problem to be solved by the present invention is to study a new type of differential to integrate the open differential mode, differential lock mode, power disengagement mode, and left and right power decoupling modes to achieve full-scenario coverage.

[0007] Technical solution: The differential of the present invention comprises an input gear assembly meshing with a reducer gear, a gear assembly assembled in the input gear assembly, a disengagement selection assembly and a decoupling selection assembly cooperating with the gear assembly to realize different functions, and a differential connection flange assembly assembling the input gear assembly, the gear assembly, the disengagement selection assembly and the decoupling selection assembly into one body;

[0008] Wherein, the gear assembly includes a left planetary pinion, a left output key sleeve meshing with the left planetary pinion, a right planetary pinion and a right output key sleeve meshing with the right planetary pinion;

[0009] The decoupling selection assembly comprises a decoupling selector assembled with the left planetary pinion and the right planetary pinion, the end faces of the decoupling selector respectively connected with the left planetary pinion and the right planetary pinion are provided with meshing splines, and the left planetary pinion and the right planetary pinion are respectively provided with selection splines matched with the meshing splines;

[0010] The disengagement selection component includes a disengagement sliding gear assembled on the left planetary pinion, the disengagement sliding gear is meshed with the right planetary pinion, and the end surface of the disengagement sliding gear connected to the left planetary pinion is provided with a meshing spline, and the left planetary pinion is provided with a selection spline that matches the meshing spline.

[0011] Furthermore, the decoupling selection assembly of the differential also includes a decoupling slip ring for installing and fixing the decoupling selector, rotating a mode paddle arranged on the decoupling slip ring, and a mode diaphragm screw connected to the mode paddle, so as to realize the left and right movement of the mode paddle through the rotation of the mode diaphragm screw, and then drive the decoupling selector to move left and right, so that the decoupling selector is located at different positions of the left planetary pinion and the right planetary pinion, realizing different functional states.

[0012] Furthermore, the disengagement selection assembly of the differential also includes a disengagement selector clamped on the disengagement sliding gear, a disengagement selection slip ring for installing and fixing the disengagement selector, rotating a mode paddle arranged on the disengagement selection slip ring, and a mode paddle screw connected to the mode paddle, so as to realize the forward and backward movement of the mode paddle through the rotation of the mode paddle screw, thereby driving the disengagement selector to move forward and backward, so that the disengagement sliding gear is located at different positions of the left planetary pinion to realize different functional states.

[0013] Furthermore, the meshing splines on the left planetary pinion gear and the right planetary pinion gear of the differential are respectively located on the left and right sides of the decoupling selector assembled on the two.

[0014] Furthermore, the input gear assembly of the differential includes a gear set holder, an input gear located on the gear holder and meshing with the reducer gear.

[0015] Furthermore, a connecting flange connected to the input gear is provided on the gear set retaining frame of the differential, and a decoupling selector limit groove and a decoupling selector limit block, as well as a disengaging selector limit groove and a disengaging selector limit block are respectively provided on the left and right ends of the gear set retaining frame.

[0016] Furthermore, a spline connected and engaged with the left drive shaft is provided on the inner side wall of the left output key sleeve of the differential, and a spline connected and engaged with the right drive shaft is provided on the inner side wall of the right output key sleeve.

[0017] Furthermore, guide parts are provided at both ends of the selection spline of the differential to ensure smooth selection of different functional modes and avoid jamming.

[0018] The operating method of the differential of the present invention comprises the following steps:

[0019] (1) When the differential needs to realize the left and right wheel differential function, the meshing spline of the driving disengagement sliding gear meshes with the selection spline on the left planetary pinion, and the two do not rotate relative to each other; and the meshing spline of the driving decoupling selector does not mesh with the selection splines on the left planetary pinion and the right planetary pinion, and the left planetary pinion and the decoupling selector generate relative rotational motion, and at the same time, the right planetary pinion and the decoupling selector generate relative rotational motion;

[0020] (2) When the differential needs to realize the left and right wheel disengagement function, the meshing spline of the driving disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the driving decoupling selector does not mesh with the selection splines on the left planetary pinion and the right planetary pinion, and the left planetary pinion and the decoupling selector generate relative rotational motion, and at the same time, the right planetary pinion and the decoupling selector generate relative rotational motion;

[0021] (3) When the differential needs to realize the left and right wheel differential lock function, the meshing spline of the drive disengagement sliding gear meshes with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector meshes with the selection spline on the left planetary pinion, and the meshing spline of the decoupling selector does not mesh with the selection spline on the right planetary pinion; or the meshing spline of the drive disengagement sliding gear meshes with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the decoupling selector meshes with the selection spline on the right planetary pinion;

[0022] (4) When the differential needs to realize the left wheel decoupling function, the meshing spline of the drive disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector meshes with the selection spline of the left planetary pinion, and the meshing spline of the decoupling selector does not mesh with the selection spline on the right planetary pinion;

[0023] (5) When the differential needs to realize the right wheel decoupling function, the meshing spline of the drive disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector does not mesh with the selection spline of the left planetary pinion, and the meshing spline of the decoupling selector meshes with the selection spline on the right planetary pinion.

[0024] Beneficial effects: Compared with the prior art, the significant advantages of the present invention are: the differential can realize normal differential, differential lock, power disengagement and left and right wheels obtaining power separately, and is particularly suitable for equipping four-wheel drive models driven by front and rear dual motors. Among them, the front and rear disengagement functions are realized based on the vehicle supporting timely four-wheel drive mode under good road conditions to save energy consumption, and if a power system fails, the disengagement function is used to achieve fault cutoff to ensure that the vehicle continues to drive to the maintenance point; the differential lock function is realized based on the insufficient adhesion of a certain wheel of the vehicle, and the differential lock is locked to help the vehicle complete the extreme escape; the left and right wheel decoupling function is realized based on adjusting the speed of the wheel and motor that obtains power, so that the vehicle can achieve a tank U-turn and a U-turn on the spot, which is used to complete the vehicle turning under extreme conditions and improve the vehicle's ability to escape under extreme working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 Schematic diagram of the overall structure of the differential of the present invention;

[0026] Figure 2 It is a schematic diagram of the gear set retainer structure of the input gear assembly of the present invention;

[0027] Figure 3 is an exploded schematic diagram of the differential of the present invention;

[0028] Figure 4 It is a schematic diagram of the assembly of the gear assembly of the present invention;

[0029] Figure 5 is an exploded schematic diagram of the gear assembly of the present invention;

[0030] Figure 6 It is an exploded schematic diagram of the disengagement selection assembly of the present invention;

[0031] Figure 7 It is a schematic diagram of the structure of the decoupling selection component of the present invention. DETAILED DESCRIPTION

[0032] The technical solution of the present invention is further described in detail below in conjunction with the accompanying drawings.

[0033] The differential of the present invention can be installed in any reduction box that requires a differential function, and for a four-wheel drive vehicle, two groups can be provided, which are respectively integrated with the front and rear motor reducers. Since the focus of the present invention is on the differential itself, the corresponding drawings are no longer provided for the reducer and its assembly with the reducer, and it can be realized by using the operating means known in the art.

[0034] Specifically, the differential of the present invention is as follows: Figure 1As shown, it includes an input gear assembly I, which mainly includes an input gear, which is used to mesh with the reducer gear set, and transmits power through the reducer to the entire differential to drive the vehicle. Secondly, the input gear assembly I is hollow inside, which is used to integrate the gear assembly that realizes the differential, differential lock, and left and right decoupling functions, so as to improve the space utilization rate of the product. The differential connection flange assembly V assembles the entire differential and is connected to the reducer housing through a set of bearings. The disengagement selection assembly III performs power disengagement or differential function selection by executing the motor to respond to the vehicle command. This actuator can be used as a selection component to cooperate with the disengagement selection assembly III to complete the disengagement or differential function selection. The decoupling selection assembly IV is used to select the left wheel to obtain power, or the right wheel to obtain power, or both wheels to obtain power at the same time. The gear assembly II, the core functional component of the present invention, selects different gear meshing through the disengagement selection assembly III and the decoupling selection assembly IV to correspondingly realize different functional states of the differential.

[0035] Among them, Figure 2 and Figure 3 As shown, the input gear assembly I of the differential of the present invention includes a gear set holder 14 and an input gear 15 arranged on the gear set holder 14, and the input gear 15 is meshed with the reducer gear. A connecting flange 16 is provided on the gear set holder 14, and the input gear 15 is in surface contact with the connecting flange 16. The fixing bolts of the input gear 15 are installed in the screw holes of the input gear through the connecting flange mounting holes, so that the input gear 15 is rigidly connected to the gear holder 14. The differential connecting flange group V is installed using the mounting screws through the flange mounting holes, and the two end faces of the gear set holder 14 serve as the mounting limit surfaces of the differential connecting flange group V.

[0036] like Figure 3 , Figure 4 and Figure 5 As shown, the gear assembly II of the present invention includes several sets of planetary gear sets, which include a left planetary pinion 1, a left output key sleeve 2, a right planetary pinion 3 and a right output key sleeve 4. The reducer is meshed with the input gear 15, and the input gear 15 is rigidly connected to the gear set holder 14 to transmit power to the gear set holder 14. The gear holder 15 is rigidly connected to the differential connection flange set V. The left planetary pinion 1 and the right planetary pinion 3 can rotate relative to the differential connection flange set V, and the planetary gears also rotate around the axis of the input gear 15 together with the rotation of the flange, so the power is transmitted to the planetary gear set through the differential flange set V.

[0037] The left planetary pinion 1 is gear-engaged with the left output key sleeve 2, and the right planetary pinion 3 is gear-engaged with the right output key sleeve 4. The left planetary pinion 1 is provided with a left planetary pinion meshing tooth 22, a selection spline 7 located at the left end of the left planetary pinion meshing tooth 22, and a selection spline 7 located at the right end of the left planetary pinion meshing tooth 22. The smooth surface between the selection spline 7 at the left end of the left planetary pinion meshing tooth 22 and the left planetary pinion meshing tooth 22 is the cancellation decoupling mating surface 23, the smooth surface between the left planetary pinion meshing tooth 22 and the selection spline 7 located at the right end of the left planetary pinion meshing tooth 22 is the disengagement selection mating surface 29, and the end surface of the left end of the selection spline 7 located at the left end of the left planetary pinion meshing tooth 22 is the left planetary pinion 1 rotation mating surface. The left output key sleeve 2 is provided with left output key sleeve meshing teeth 24 meshing with the left planetary pinion meshing teeth 22, and the connecting inner side wall of the left output key sleeve 2 is provided with a spline 21 connected and meshed with the left drive shaft.

[0038] The right planetary pinion 3 is provided with a right planetary gear meshing tooth 25, and the left section of the right planetary gear meshing tooth 25 is provided with a selection spline 7, and the smooth surface at the left end of the selection spline 7 is the right decoupling cancellation mating surface 26, and the left end surface of the right decoupling cancellation mating surface 26 is set as the right planetary pinion rotation mating boss. The right output key sleeve 4 is provided with a right output key sleeve meshing tooth 27 meshing with the right planetary pinion meshing tooth 25, and the inner side wall of the right output key sleeve 4 is provided with a spline 21 connected and meshed with the right drive shaft.

[0039] Both ends of the selection spline 7 are provided with guide parts respectively, for example, a circular arc slope surface can be adopted to ensure smooth mode selection without jamming.

[0040] Based on the gear assembly II, the disengagement selection assembly III matched therewith includes a disengagement sliding gear 8 mounted on the left planetary pinion 22, such as Figure 5 and Figure 6As shown. A sliding gear sliding retaining ring 28 is extended on the disengaging sliding gear 8, and a meshing spline 6 is provided on the inner connecting surface of the disengaging sliding gear 8. A disengaging selector 12 is provided in the sliding gear sliding retaining ring 28, which can be a plate structure with a claw. Under the cooperation of the two, the disengaging sliding gear 8 can undergo relative rotational movement around the axis of the disengaging sliding gear 8 with the disengaging selector 12, but cannot undergo relative displacement movement. The number of disengaging selectors 12 is the same as the number of groups of the left planetary pinion 1. The disengaging selector 12 is connected and fixed by the disengaging selection slip ring 13, and the connection and fixation of the two can be bolted, that is, the disengaging selector 12 is installed in the fixing screw hole of the disengaging selection slip ring 13 with the disengaging selector fixing bolt, so that the disengaging selector slip ring 13 is rigidly connected to the disengaging selector 12. A mode paddle 10 is rotatably provided on the disengagement selection slip ring 13. The slip ring mating surface of the mode paddle 10 cooperates with the slideway of the disengagement selection slip ring 13. The two can rotate relative to the axis of the disengagement selection slip ring 13, but cannot move relative to the axis of the disengagement rotation slip ring 13. The disengagement rotation slip ring 13 is driven by the gear set retainer 14 to rotate leftward around itself. The disengagement selection slip ring 13 can move left and right under the driving force received by the mode paddle 10, and then drive the disengagement selector 12 to move left and right, so that the disengagement selector 12 is located at different positions on the left planetary pinion 1 to achieve different functions. The driving actuator of the mode paddle 10 can drive the mode paddle 10 through a screw rod, or through other power forms, such as an electromagnet form or a pneumatic form. The present invention adopts the driving method of rotating the screw rod to achieve movement, that is, a mode paddle screw rod 11 is connected to the mode paddle 10, and the mode paddle screw rod 11 can be driven to rotate by the execution motor, so that the mode paddle 10 can be moved forward and backward by the rotation of the mode paddle screw rod 11, and then the disengagement selector 12 is driven to move forward and backward, so that the disengagement sliding gear 8 is located at different positions of the left planetary pinion 1 to achieve the corresponding functional state.

[0041] The disengagement sliding gear 8 is always meshed with the right planetary gear meshing teeth 25, and the disengagement sliding gear 8 can be driven to move along the axis of the left planetary pinion 3 through the disengagement selector 12. Since the actuator carries position information, the disengagement sliding gear 8 has only two working states. The first is that the meshing spline 6 of the disengagement sliding gear 8 is meshed with the selection spline 7 of the left planetary pinion 1, and the two will not rotate relative to each other; the second is that the meshing spline 6 and the disengagement selection matching surface 29 are matched with each other, and the two are clearance clearance matched, so the two can produce free relative rotational motion.

[0042] Similarly, based on the gear assembly, the decoupling selection assembly IV matched therewith includes a decoupling selector 5 simultaneously mounted on the left planetary pinion 1 and the right planetary pinion 3, such as Figure 5 and Figure 7As shown. The decoupling selector 5 can be a connecting member provided with connecting holes connected to the left planetary pinion 1 and the right planetary pinion 3 respectively. The inner connecting end surface of the decoupling selector 5 and the left planetary pinion 1 is provided with a meshing spline 6, and the inner connecting end surface of the decoupling selector 5 and the right planetary pinion 3 is provided with a meshing spline 6. The decoupling selector 5 cooperates with the left planetary pinion 1 and the right planetary pinion 3 at the same time, and the decoupling selector 5 can move left and right along the axis direction of the planetary pinion, so that the power is transmitted to the left output key sleeve 2 and the right output key sleeve 4 through the planetary gear set, and is transmitted to the drive shaft through the left and right key sleeves. The number of decoupling selectors 4 is the same as the number of groups of left and right planetary pinions. The decoupling selector 5 is connected and fixed by a decoupling slip ring 9, and the connection and fixation of the two can be bolted, that is, the decoupling selector 5 is installed in the fixing screw hole of the decoupling slip ring with the decoupling selector fixing bolt, so that the decoupling slip ring 9 is rigidly connected to the decoupling selector 5. A mode paddle 10 is rotatably provided on the decoupling slip ring 9. The slip ring mating surface of the mode paddle 10 cooperates with the slideway of the decoupling slip ring 9. The two can rotate relative to the axis of the decoupling slip ring 9, but cannot move relative to the axis of the decoupling slip ring 9. The decoupling slip ring 9 is driven by the gear set retainer 14 to rotate leftward around itself. The decoupling slip ring 9 can move left and right under the driving force received by the mode paddle 10, and then drive the decoupling selector 5 to move left and right, so that the decoupling selector 5 is located at different positions on the left planetary pinion 1 and the right planetary pinion 3 to achieve different functions. The driving actuator of the mode paddle 10 can drive the mode paddle through a screw rod, or through other power forms, such as an electromagnet form or a pneumatic form, which is the same as the mechanism of the disengagement selection component.

[0043] The gear set holder 14 is provided with a connecting flange 16 connected to the input gear 15, and the left and right ends of the gear set holder 14 are respectively provided with a decoupling selector limit groove 17 and a decoupling selector limit block 18, and a disengaging selector limit groove 19 and a disengaging selector limit block 20.

[0044] The decoupling selector 5 is in a mating relationship with the left planetary pinion 1 and the right planetary pinion 3 at the same time. The decoupling selector 5 is in a mating relationship with the left planetary pinion 1 and the right planetary pinion 3 through the meshing spline 6 of the decoupling selector. The decoupling selector 5 produces three mating states by adjusting the axial positions different from the two planetary pinion shafts. In the first state, the left meshing spline 6 of the decoupling selector 5 is meshed with the left selection spline 7 of the left planetary pinion 1, and the two cannot have relative rotational motion. At the same time, the right meshing spline 6 of the decoupling selector 5 is in a mating relationship with the right decoupling mating surface 26, and the two are clearance fits, so the right planetary pinion 3 can produce relative rotational motion with the decoupling selector 5. The second type is that the left meshing spline 6 of the decoupling selector 5 is in a mating relationship with the left decoupling mating surface 23, and the two are clearance fit, so the left planetary pinion 1 can produce relative rotational motion with the decoupling selector 5, and at the same time, the right meshing spline 6 of the decoupling selector 5 is in a mating relationship with the right decoupling mating surface 26, and the two are clearance fit, so the right planetary pinion 3 can produce relative rotational motion with the decoupling selector 5. The third type is that the left meshing spline 6 of the decoupling selector 5 is in a mating relationship with the left decoupling mating surface 23, and the two are clearance fit, so the left planetary pinion 3 can produce relative rotational motion with the decoupling selector 5, and at the same time, the right meshing spline 6 of the decoupling selector 5 is meshed with the right selection spline 7, and the two cannot produce relative rotational motion.

[0045] The various functions of the differential of the present invention are defined by determining the different working states of the two selectors. The actuator motor used in the present invention will pre-set the working state, and no other state will be generated in the normal working mode unless the system fails.

[0046] 1. Differential function: The disengaged sliding gear 8 is in the first working state, and the decoupling selector 5 is in the second working state, that is, the meshing spline 6 of the disengaged sliding gear 8 is meshed with the selection spline 7 on the left planetary pinion 1, and the meshing spline 6 of the driving decoupling selector 5 is not meshed with the selection spline 7 on the left planetary pinion 1 and the right planetary pinion 3. The left planetary pinion 1 and the right planetary pinion 3 are in mutual meshing relationship. When there is a left and right wheel speed difference, the two planetary pinions rotate to balance the speed difference between the inner and outer wheels.

[0047] 2. Disengagement function: the disengagement sliding gear 8 is in the second working state, and the decoupling selector 5 is in the second working state, that is, the meshing spline 6 of the disengagement sliding gear 8 is not meshed with the selection spline 7 on the left planetary pinion 1, and the meshing spline 6 of the driving decoupling selector 5 is not meshed with the selection spline 7 on the left planetary pinion 1 and the right planetary pinion 3. The left planetary pinion 1 and the right planetary pinion 3 do not have a meshing relationship, the power transmission is interrupted, and the input gear does not generate driving force. During the vehicle driving process, the ground resistance is transmitted to the left output key sleeve 2 and the right output key sleeve 4 respectively through the wheels. Since the left planetary pinion 1 and the right planetary pinion 3 are not meshed with each other, the resistance of the road surface drives the two planetary pinions to rotate respectively, and the power will not be transmitted to the reducer in the reverse direction, thereby reversely dragging the motor to rotate, resulting in more energy consumption.

[0048] 3. Differential lock function, the disengaged sliding gear 8 is in the first working state, the decoupling selector 5 is in the first working state, that is, the meshing spline 6 of the disengaged sliding gear 5 is meshed with the selection spline 7 on the left planetary pinion 1, and the meshing spline 6 of the driving decoupling selector 5 is meshed with the selection spline 7 of the left planetary pinion 1, and the meshing spline 6 of the decoupling selector 5 is not meshed with the selection spline 7 on the right planetary pinion 3. The left planetary pinion 1 is in meshing relationship with the right planetary pinion 3, but the decoupling rotator 5 is in meshing relationship with the left planetary pinion 1, which limits the rotation of the left planetary pinion 1. Due to the meshing relationship between the left and right pinions, the rotation of the two planetary pinions is limited. The left and right wheels are rigidly connected, and there is no differential function. Similarly, the decoupling selector 5 in the third working state can also produce the differential locking function. The actual control system can choose a certain working state according to actual needs.

[0049] 4. The left wheel decoupling function, the disengaged sliding gear 8 is in the second working state, and the decoupling selector 5 is in the first working state, that is, the meshing spline 6 of the disengaged sliding gear 8 is not meshed with the selection spline 7 on the left planetary pinion 1, and the meshing spline 6 of the driving decoupling selector 5 is meshed with the selection spline 7 of the left planetary pinion 1, and the meshing spline 6 of the decoupling selector 5 is not meshed with the selection spline 7 on the right planetary pinion 3. The rotation of the left planetary pinion 1 is locked, and the right planetary pinion 3 does not have a meshing relationship with the left planetary pinion 1. The power is transmitted to the left output key sleeve 2 and then to the wheel through the input and output gears. Due to the resistance of the ground, the power of the input gear will drive the right planetary pinion to rotate, and will not transmit the power to the wheel. Only the left wheel obtains the power transmitted by the power system.

[0050] 5. Right wheel decoupling function, disengage sliding gear 8 is in the first working state, decoupling selector 5 is in the third working state, that is, the meshing spline 6 of disengage sliding gear 8 is not meshed with the selection spline 7 on the left planetary pinion 1, and the meshing spline 6 of driving decoupling selector 5 is not meshed with the selection spline 7 of the left planetary pinion 1, and the meshing spline 6 of decoupling selector 5 is meshed with the selection spline 7 on the right planetary pinion 3. Similarly, the left wheel structure function, only the right wheel obtains the power of the power system.

[0051] The present invention is based on the above differential operation method, comprising the following steps:

[0052] (1) When the differential needs to realize the left and right wheel differential function, the meshing spline of the drive disengagement sliding gear is meshed with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector is not meshed with the selection splines on the left planetary pinion and the right planetary pinion;

[0053] (2) When the differential needs to realize the left and right wheel disengagement function, the meshing spline of the drive disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector does not mesh with the selection splines on the left planetary pinion and the right planetary pinion;

[0054] (3) When the differential needs to realize the left and right wheel differential lock function, the meshing spline of the drive disengagement sliding gear meshes with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector meshes with the selection spline on the left planetary pinion, and the meshing spline of the decoupling selector does not mesh with the selection spline on the right planetary pinion; or the meshing spline of the drive disengagement sliding gear meshes with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the decoupling selector meshes with the selection spline on the right planetary pinion;

[0055] (4) When the differential needs to realize the left wheel decoupling function, the meshing spline of the drive disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector meshes with the selection spline of the left planetary pinion, and the meshing spline of the decoupling selector does not mesh with the selection spline on the right planetary pinion;

[0056] (5) When the differential needs to realize the right wheel decoupling function, the meshing spline of the drive disengagement sliding gear does not mesh with the selection spline on the left planetary pinion, and the meshing spline of the drive decoupling selector does not mesh with the selection spline of the left planetary pinion, and the meshing spline of the decoupling selector meshes with the selection spline on the right planetary pinion.

[0057] In addition to the above, it should be noted that other springs for eliminating gaps, gaskets for improving wear resistance and other related accessories in the differential of the present invention are not reflected one by one. Those skilled in the art can undoubtedly make adaptive settings based on the technical solution of the present invention, and thus they are not elaborated as the core points of the present invention.

[0058] In addition, the reason why the differential of this invention is particularly suitable for four-wheel drive models with front and rear dual motors is that the front and rear dual motor four-wheel drive, due to the complex and changeable actual road conditions, although the front and rear power is not mechanically coupled, there is electrical coupling. In actual form, the front and rear axles must have two working conditions, differential and synchronous, alternating. The control system cannot achieve perfect matching of the front and rear axle speeds, which will inevitably lead to speed oscillations of the front and rear drive motors and additional energy consumption. Therefore, the disengagement function is used, and the two-wheel drive mode is actually used for driving on general roads, and the four-wheel drive mode is used for sudden acceleration or off-road conditions. This will not reduce the performance of the wheels and can also achieve optimal energy consumption.

[0059] For vehicles with good road conditions, the decoupling component can be cancelled to reduce costs. The differential is only equipped with disengagement and differential functions to achieve timely four-wheel drive mode and full-time four-wheel drive function. For models with relatively high requirements for off-road performance, a decoupling selector is equipped. The differential lock function can be selected to complete the cross-axle escape under extreme escape conditions. For narrow road conditions with a very small turning radius, the diagonal wheels of the vehicle or the power of the front and rear axles can be selected, and then the steering wheel is turned in the required direction. The front motor rotates forward and the rear motor rotates reversely to complete the "on-site U-turn" function. There must be a corresponding control algorithm for "on-site U-turn" to enable the vehicle to cope with actual complex road conditions, which will not be introduced in this invention. At the same time, one of the front motors does not rotate and the other rotates, and different wheels are selected for decoupling to complete the vehicle around the wheels that do not rotate to complete a state similar to "tank U-turn" to cope with the actual difficulties faced by actual off-road or extreme rescue. Therefore, the invention mentions that the differential is particularly suitable for use on front and rear dual-motor models, so that the vehicle has some functions of four-motor drive at the cost of dual-motor drive.

[0060] In addition, the selection spline of the present invention is only a matching method, which can be used as a low-cost method to complete various mode switching at a relatively low speed or parking state. If the driving quality needs to be further improved, a position sensor can be added to the gear assembly, and a selection synchronizer can be added to the power disengagement function to cooperate with the fast and high-precision response of the motor to achieve full-speed intelligent timely four-wheel drive. Of course, various mode switching in the intelligent state will also have corresponding safety mechanisms. For example, the differential locking function cannot be performed when the vehicle speed is greater than a certain critical value. In a lower speed range, the front lock or the rear lock can be engaged, and at an even lower speed, two locks can be engaged. When the vehicle is detected to be out of trouble, the lock is automatically released, etc. The intelligent configuration can be upgraded based on this invention.

Claims

1. A differential, characterized in that: The differential comprises an input gear assembly (I) meshing with a reducer gear, a gear assembly (II) assembled in the input gear assembly (I), a disengagement selection assembly (III) and a decoupling selection assembly (IV) cooperating with the gear assembly (II) to realize different functions, and a differential connection flange assembly (V) assembling the input gear assembly (I), the gear assembly (II), the disengagement selection assembly (III) and the decoupling selection assembly (IV) into one body; The gear assembly (II) comprises a left planetary pinion (1), a left output key sleeve (2) meshing with the left planetary pinion (1), a right planetary pinion (3) and a right output key sleeve (4) meshing with the right planetary pinion (3); The decoupling selection assembly (IV) comprises a decoupling selector (5) assembled with the left planetary pinion (1) and the right planetary pinion (3); the end surfaces of the decoupling selector (5) respectively connected with the left planetary pinion (1) and the right planetary pinion (3) are provided with meshing splines (6); the left planetary pinion (1) and the right planetary pinion (3) are respectively provided with selection splines (7) matched with the meshing splines (6); The disengagement selection assembly (III) comprises a disengagement sliding gear (8) mounted on the left planetary pinion (1), the disengagement sliding gear (8) is always meshed with the right planetary pinion (3), and the end surface of the disengagement sliding gear (8) connected to the left planetary pinion (1) is provided with a meshing spline (6), and the left planetary pinion (1) is provided with a selection spline (7) matched with the meshing spline (6).

2. The differential according to claim 1, characterized in that: The decoupling selection assembly (IV) further comprises a decoupling slip ring (9) for mounting and fixing the decoupling selector (5), rotating a mode paddle (10) arranged on the decoupling slip ring (9), and a mode paddle screw (11) connected to the mode paddle (10), so that the mode paddle (10) can be moved left and right by rotating the mode paddle screw (11), thereby driving the decoupling selector (5) to move left and right, so that the decoupling selector (5) is located at different positions of the left planetary pinion (1) and the right planetary pinion (3), thereby realizing different functional states.

3. The differential according to claim 1, characterized in that: The disengagement selection assembly (III) further comprises a disengagement selector (12) mounted on the disengagement sliding gear (8), a disengagement selection slip ring (13) for mounting and fixing the disengagement selector (12), rotating a mode paddle (10) mounted on the disengagement selection slip ring (13), and a mode paddle screw (11) connected to the mode paddle (10), so that the mode paddle (10) can be moved left and right by rotating the mode paddle screw (11), thereby driving the disengagement selector (12) to move left and right, so that the disengagement sliding gear (8) is located at different positions of the left planetary pinion (1), thereby realizing different functional states.

4. The differential according to claim 1, characterized in that: The meshing splines (6) on the left planetary pinion (1) and the right planetary pinion (3) are respectively located on the left and right sides of a decoupling selector (5) mounted on the two.

5. The differential according to claim 2 or 3, characterized in that: The input gear assembly (I) comprises a gear set retainer (14) and an input gear (15) disposed on the gear retainer (14) and meshing with the reducer gear.

6. The differential according to claim 5, characterized in that: The gear set holder (14) is provided with a connecting flange (16) connected to the input gear (15), and the left and right ends of the gear set holder (14) are respectively provided with a decoupling selector limit groove (17) and a decoupling selector limit block (18), and a disengaging selector limit groove (19) and a disengaging selector limit block (20).

7. The differential according to claim 1, characterized in that: The inner side wall of the left output key sleeve (2) is provided with a spline (21) connected and engaged with the left drive shaft, and the inner side wall of the right output key sleeve (4) is provided with a spline (21) connected and engaged with the right drive shaft.

8. The differential according to claim 1, characterized in that: Both ends of the selection spline (7) are provided with guide parts respectively, so as to ensure smooth selection of different functional modes and avoid jamming.

9. The method for operating a differential according to claim 1, characterized in that: The steps include: (1) When the differential needs to realize the left and right wheel differential function, the meshing spline (6) of the driving disengagement sliding gear (8) is meshed with the selection spline (7) on the left planetary pinion (1), and the two do not rotate relative to each other; and the meshing spline (6) of the driving decoupling selector (5) is not meshed with the selection splines (7) on the left planetary pinion (1) and the right planetary pinion (3), and the left planetary pinion (1) and the decoupling selector (5) generate relative rotational motion, and at the same time, the right planetary pinion (3) and the decoupling selector (5) generate relative rotational motion; (2) When the differential needs to realize the function of disengaging the left and right wheels, the meshing spline (6) of the driving disengagement sliding gear (8) is not meshed with the selection spline (7) on the left planetary pinion (1), and the meshing spline (6) of the driving decoupling selector (5) is not meshed with the selection splines (7) on the left planetary pinion (1) and the right planetary pinion (3), and the left planetary pinion (1) and the decoupling selector (5) generate relative rotational motion, and at the same time, the right planetary pinion (3) and the decoupling selector (5) generate relative rotational motion; (3) When the differential needs to realize the left and right wheel differential lock function, the meshing spline (6) of the driving disengagement sliding gear (8) is meshed with the selection spline (7) on the left planetary pinion (1), and the meshing spline (6) of the driving decoupling selector (5) is meshed with the selection spline (7) of the left planetary pinion (1), and the meshing spline (6) of the decoupling selector (5) is not meshed with the selection spline (7) on the right planetary pinion (3); or the meshing spline (6) of the driving disengagement sliding gear (8) is meshed with the selection spline (7) on the left planetary pinion (1), and the meshing spline (6) of the driving decoupling selector (5) is not meshed with the selection spline (7) of the left planetary pinion (1), and the meshing spline (6) of the decoupling selector (5) is meshed with the selection spline (7) on the right planetary pinion (3); (4) When the differential needs to realize the left wheel decoupling function, the meshing spline (6) of the driving disengagement sliding gear (8) is not meshed with the selection spline (7) on the left planetary pinion (1), and the meshing spline (6) of the driving decoupling selector (5) is meshed with the selection spline (7) of the left planetary pinion (1), and the meshing spline (6) of the decoupling selector (5) is not meshed with the selection spline (7) on the right planetary pinion (3); (5) When the differential needs to realize the right wheel decoupling function, the meshing spline (6) of the driving disengagement sliding gear (8) is not meshed with the selection spline (7) on the left planetary pinion (1), and the meshing spline (6) of the driving decoupling selector (5) is not meshed with the selection spline (7) of the left planetary pinion (1), and the meshing spline (6) of the decoupling selector (5) is meshed with the selection spline (7) on the right planetary pinion (3).

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