Lubricating control device and method for multi-gear double-motor electric drive box and vehicle

Abstract

The invention relates to a lubrication control device and method for a multi-gear double-motor electric drive box and a vehicle, and the control device comprises an oil supply driving part which is used for providing circulation power for lubricating oil; an oil path; the control assembly comprises an acquisition unit, a calculation unit and an output unit, the acquisition unit is used for acquiring motion data of a to-be-lubricated part and gear data of a motor, and the calculation unit is used for calculating required flow according to the motion data and the gear data; and the output unit is used for sending a control signal to the oil supply driving part according to the required flow, so that the oil supply driving part supplies the lubricating oil with the required flow. According to the method, the required flow of the electric drive box under different working conditions is accurately calculated, accurate supply is achieved through the electric pump, and accurate matching of the cooling and lubricating flow requirement and supply is achieved; and the guarantee capability of the lubricating system on the reliability of the electric drive box system is improved, and sufficient lubrication can be provided under various working conditions.

Description

Technical Field

[0001] The present application relates to the field of vehicle lubrication technology, and in particular to a lubrication control device, a control method and a vehicle for a multi-speed dual-motor electric drive box. Background Art

[0002] In modern electric drive systems, lubrication and cooling of the drive assembly are key factors in ensuring efficient and stable operation. As a core component of the power system of new energy vehicles, the electric drive box has a high input speed and rapid power changes, which puts higher requirements on the lubrication and cooling system. Under such high-speed and high-power conditions, traditional lubrication and cooling methods often fail to meet the needs, and are prone to insufficient lubrication, resulting in failure due to high-temperature heat damage, which seriously affects the service life and reliability of the electric drive box.

[0003] At present, the cooling and lubrication system of the electric drive box assembly mainly adopts splash lubrication or mechanical pump forced lubrication. Splash lubrication relies on the rotation of gears to splash oil onto the surfaces of each friction pair to form an oil film, but its oil stirring loss is large, and the lubrication effect is poor at low speeds or low oil levels. Although mechanical pump forced lubrication can provide more sufficient lubrication, it usually requires limit boundary calculations to determine the required flow rate. In order to ensure the reliability of lubrication and cooling, the selected pump flow rate is often too large, which not only causes energy waste, but also in order to ensure that the oil is not sucked out, it is usually necessary to add more lubricating oil, which further increases the oil stirring loss. Summary of the invention

[0004] Based on this, in order to solve these problems, the present invention proposes a multi-speed dual-motor electric drive box precision lubrication device and method. The device accurately controls the flow and pressure of the lubricating oil, dynamically adjusts the lubrication strategy according to the actual working condition requirements of the electric drive box, so as to achieve a more efficient and economical lubrication and cooling effect. This precision lubrication device can reduce oil stirring loss and energy consumption, while ensuring that sufficient lubrication can be provided under various working conditions, effectively avoiding the problem of high temperature heat damage failure caused by insufficient lubrication.

[0005] In a first aspect, a lubrication control device for a multi-speed dual-motor electric drive box is provided, the control device comprising:

[0006] Oil supply drive, used to provide circulation power to the lubricating oil;

[0007] An oil circuit is provided between the oil supply drive member and the parts to be lubricated of the electric drive box; and

[0008] A control component, the control component includes an acquisition unit, a calculation unit and an output unit, the acquisition unit is used to obtain motion data of the parts to be lubricated and the gear data of the motor, the calculation unit is used to calculate the required flow rate according to the motion data and the gear data, and the output unit is used to send a control signal to the oil supply drive according to the required flow rate, so that the oil supply drive supplies lubricating oil of the required flow rate.

[0009] In one embodiment, the oil supply drive components are provided with two, the oil circuits are provided with two groups, and each group of oil circuits includes a shell oil circuit provided in the electric drive box and a pipeline oil circuit provided between the oil supply drive component and the shell oil circuit.

[0010] In one of the embodiments, the acquisition unit further includes a temperature sensor for acquiring the temperature of the electric drive box, and the calculation unit is used to calculate the required flow rate according to the temperature of the electric drive box.

[0011] In a second aspect, a lubrication control method for a multi-speed dual-motor electric drive box is provided, based on the above-mentioned control device, comprising the steps of:

[0012] Obtain the motion data of the parts to be lubricated and the gear position data of the motor;

[0013] Calculating the required flow rate according to the motion data and the gear data;

[0014] A control signal is sent to the oil supply driving component according to the required flow rate, so that the oil supply driving component supplies lubricating oil of the required flow rate.

[0015] In one embodiment, the motion data includes the rotation speed and torque of the part to be lubricated;

[0016] In one embodiment, the parts to be lubricated include gears and bearings, and the step of calculating the required flow rate according to the motion data and the gear data includes: calculating the loss of the parts to be lubricated:

[0017] The meshing power loss P of the gear is calculated by the following formula: Mi :

[0018] ,

[0019] Among them, fm is the meshing friction coefficient, T1 is the pinion torque, n1 is the pinion speed, and βw is the helix angle;

[0020] The power loss P of the bearing is calculated by the following formula: Bi :

[0021] ,

[0022] Wherein, M1 is the loss torque of the first bearing, M2 is the loss torque of the second bearing, and n is the rotational speed.

[0023] In one embodiment, the first bearing is a radial load bearing, and the second bearing is an axial cylindrical roller bearing;

[0024] The radial load bearing loss torque M1 is calculated by the following formula:

[0025] ,

[0026] Where f1 is the friction factor of the radial load bearing, p1 is the equivalent dynamic load of the bearing, d m is the average diameter of the bearing, a and b are correction coefficients;

[0027] The axial cylindrical roller bearing loss torque M2 is calculated by the following formula:

[0028] ,

[0029] Where f2 is the friction factor of the cylindrical roller bearing, F a is the axial load, d m is the average bearing diameter.

[0030] In one embodiment, the step of calculating the required flow rate according to the motion data and the gear data comprises:

[0031] Calculating the power loss of the parts to be lubricated according to the motion data and the gear data;

[0032] The required flow rate q is calculated according to the power loss of the parts to be lubricated by the following formula:

[0033]

[0034] Among them, P G is the power loss of the parts to be lubricated, C p is the specific heat capacity of the lubricating oil, ρ is the density of the lubricating oil, and Δt is the temperature difference between the inlet and outlet of the radiator;

[0035] Establish a matrix statistical table of required flow and parts to be lubricated.

[0036] In one embodiment, after establishing the matrix statistical table of required flow and parts to be lubricated, the step further includes:

[0037] Establish k standard working conditions, each of which corresponds to a different required flow range;

[0038] According to the location of the parts to be lubricated, the oil circuit and the parts to be lubricated on the oil circuit are divided into regions, and the lubricating oil is supplied to each region at a corresponding preset flow rate.

[0039] In a third aspect, a vehicle is provided, which is lubricated using the lubrication control method of the multi-speed dual-motor electric drive box mentioned above.

[0040] This application has the following technical effects:

[0041] (1) Accurately match lubrication and cooling requirements: The present invention achieves accurate matching of cooling and lubrication flow demand and supply by accurately calculating the required flow of the electric drive box under different working conditions and using an electric pump to accurately supply it. This method can not only meet the lubrication requirements of the electric drive box under different speeds, torques and gears, but also effectively reduce the risk of high-temperature heat damage failure caused by insufficient lubrication.

[0042] (2) Working condition identification and oil temperature monitoring: The present invention uses an algorithm to identify the working conditions of the electric drive box, including speed, torque, gear position and other factors, and monitors the operating oil temperature of the assembly to achieve self-adjustment. This intelligent monitoring and adjustment mechanism improves the lubrication system's ability to ensure the reliability of the electric drive box system and ensures that sufficient lubrication can be provided under various working conditions.

[0043] (3) Intelligent control strategy: The present invention may also include an intelligent control strategy, such as using an initial timing flow control strategy under low operating conditions to solve the problem of lack of lubrication of the distal bearing; and using a directional adjustment control strategy under high operating conditions to perform precise flow adjustment to take into account both cooling and lubrication requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] FIG1 is a schematic structural diagram of a lubrication control device for an electric drive box according to an embodiment of the present application.

[0045] FIG. 2 is a flow matrix table of gear and bearing requirements under different working conditions according to an embodiment of the present invention.

[0046] FIG. 3 is a schematic diagram of standard operating conditions according to an embodiment of the present invention.

[0047] FIG. 4 is a schematic diagram of regional stratification according to an embodiment of the present invention.

[0048] FIG. 5 is a flow comparison confirmation table according to an embodiment of the present invention. DETAILED DESCRIPTION

[0049] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0050] In the description of the present application, it should be understood that if the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. appear, the orientation or position relationship indicated by these terms is based on the orientation or position relationship shown in the accompanying drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application.

[0051] In addition, if the terms "first" or "second" appear, these terms are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of this application, if the term "plurality" appears, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0052] In this application, unless otherwise clearly specified and limited, if the terms "installed", "connected", "connected", "fixed" and the like appear, these terms should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integrated connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0053] In the present application, unless otherwise clearly specified and limited, if there is a description that a first feature is "above" or "below" a second feature, etc., or similar descriptions appear, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "above" and "above" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. The first feature being "below", "below" and "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0054] It should be noted that if an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. If an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. If any, the terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in this application are for illustrative purposes only and do not represent the only implementation method.

[0055] As shown in FIG1 , an electric drive box provided in one embodiment of the present application includes an oil supply drive, an oil circuit, and a control component. The oil supply drive is used to provide circulation power to the lubricating oil. The oil circuit is arranged between the oil supply drive and the parts to be lubricated of the electric drive box. The control component includes a collection unit, a calculation unit, and an output unit. The collection unit is used to obtain motion data of the parts to be lubricated and the gear data of the motor. The calculation unit is used to calculate the required flow rate based on the motion data and the gear data. The output unit is used to send a control signal to the oil supply drive according to the required flow rate, so that the oil supply drive supplies the required flow rate of lubricating oil.

[0056] The above lubrication control device can achieve accurate matching of cooling and lubrication flow demand and supply by accurately calculating the required flow of the electric drive box under different working conditions and using the electric pump to accurately supply it. This method can not only adapt to the lubrication needs of the electric drive box under different speeds, torques and gears, but also effectively reduce the risk of high-temperature heat damage failure caused by insufficient lubrication; the calculation unit can identify the operating conditions of the electric drive box, including speed, torque, gear and other factors, and monitor the operating oil temperature of the assembly to achieve self-adjustment; this intelligent monitoring and adjustment mechanism improves the lubrication system's ability to ensure the reliability of the electric drive box system and ensures that sufficient lubrication can be provided under various working conditions; the above device facilitates the implementation of oil quantity control strategies, such as using the initial timing flow control strategy under low working conditions to solve the problem of lack of lubrication of the distal bearing; under high working conditions, a directional adjustment control strategy is used to perform precise flow adjustment to take into account cooling and lubrication needs.

[0057] In one embodiment, the oil supply drive components are provided with two, the oil circuits are provided with two groups, and each group of oil circuits includes a shell oil circuit provided in the electric drive box and a pipeline oil circuit provided between the oil supply drive component and the shell oil circuit.

[0058] The electric drive box of the present application is based on a dual-motor vehicle configuration, and each motor corresponds to an oil supply drive and a set of oil circuits. The electric drive box also includes a housing, an oil tank, and a filter, etc. The housing is used to form a cavity for accommodating components such as the oil supply drive and the motor. The housing oil circuit is formed on the housing, and the housing oil circuit is connected between the filter and the pipeline oil circuit. The filter is arranged between the oil tank and the filter, and the filter is used to filter the lubricating oil.

[0059] Two oil supply drive components, filters, and oil circuits are set, and each oil supply drive component, filter, and oil circuit form a group. Each group is symmetrically arranged to ensure the lubrication position of the multi-speed double intermediate shaft structure. The layout structure is simple, the assembly is convenient, and the parts are highly universal. The lubricating oil passes through the filter, the housing oil circuit, and the pipeline oil circuit to accurately lubricate the required gears and bearing positions. The dual oil supply drive components provide accurate supply flow for the oil circuit.

[0060] In order to ensure low oil churning of the largest gear, an arc-shaped oil cover can be arranged on the lower side of the parts to be lubricated to ensure the lowest oil churning loss at different angles and under different working conditions.

[0061] In one of the embodiments, the acquisition unit further includes a temperature sensor for acquiring the temperature of the electric drive box, and the calculation unit is used to calculate the required flow rate according to the temperature of the electric drive box.

[0062] Specifically, the calculation unit is equipped with professional software, which can calculate the required flow rate according to the motion data and the gear data. The required flow rate is used as the basic value. After the temperature of the electric drive box is input into the calculation unit as a parameter, the required flow rate of the basic value is optimized to obtain the final value of the required flow rate. For example, if the temperature sensor detects that the warning temperature exceeds 120°C, the oil supply drive is controlled to increase the oil supply condition span for self-adjustment, mainly to ensure the normal application of the shaft gear system at the boundary of high heat or extremely poor heat dissipation conditions, and it is a special strategy that is generally not started.

[0063] The present application also provides a lubrication control method for a multi-speed dual-motor electric drive box, based on the above-mentioned control device, comprising the steps of:

[0064] S100, obtaining motion data of the parts to be lubricated and gear position data of the motor;

[0065] S200, calculating the required flow rate according to the motion data and the gear data;

[0066] S300, sending a control signal to an oil supply drive component according to the required flow rate, so that the oil supply drive component supplies lubricating oil of the required flow rate.

[0067] In one embodiment, the motion data includes the rotation speed and torque of the part to be lubricated.

[0068] Step S200 can build a power loss calculation model based on a formula or professional software. The calculated power loss includes gear loss, bearing loss, oil seal loss, friction pair loss, etc. The calculation model is introduced below using the loss of gears and bearings as an example.

[0069] In one embodiment, the parts to be lubricated include gears and / or bearings, and the step of calculating the required flow rate according to the motion data and the gear data includes: S210, calculating the loss of the parts to be lubricated:

[0070] The gear meshing power loss is a function of the gear meshing action and the friction coefficient. The gear meshing action includes some sliding of the meshing gears separated by the oil film. The meshing efficiency is a function of the sliding ratio and the meshing friction coefficient. The gear meshing power loss P is calculated by the following formula (1): Mi :

[0071] (1),

[0072] Among them, f m is the meshing friction coefficient, T1 is the small wheel torque, n1 is the small wheel speed, β w is the helix angle;

[0073] The power loss P of the bearing is calculated by the following formula (2): Bi :

[0074] (2),

[0075] M1 is the loss torque of the first bearing, M2 is the loss torque of the second bearing, and n is the rotational speed.

[0076] In one embodiment, the first bearing is a radial load bearing, and the second bearing is a cylindrical roller bearing;

[0077] The calculation methods for different types of bearings are also different. For radial load bearings, the loss torque is the equation of the bearing friction factor f1 and the calculated load P1. The radial load bearing loss torque M1 is calculated by the following formula (3):

[0078] (3)

[0079] Where f1 is the friction factor of the radial load bearing, p1 is the equivalent dynamic load of the bearing, dm is the average diameter of the bearing, a and b are correction coefficients;

[0080] For cylindrical roller bearings that bear axial loads, the total friction torque needs to be expanded by adding torque M2, which depends on the axial load. The loss torque M2 of the cylindrical roller bearing is calculated by the following formula (4):

[0081] (4)

[0082] Where f2 is the friction factor of the cylindrical roller bearing, F a is the axial load, d m is the average bearing diameter.

[0083] In one embodiment, the step S200 of calculating the required flow rate according to the motion data and the gear data further includes:

[0084] S211, calculating the power loss of the part to be lubricated according to the motion data and the gear data;

[0085] S220, based on different working conditions including speed, torque, gear and other factors, the system power loss calculation is completed, and the corresponding required flow rate q is calculated. The required flow rate q is calculated according to the power loss of the parts to be lubricated by the following formula (5):

[0086] (5)

[0087] Among them, P G is the power loss of the parts to be lubricated, C p is the specific heat capacity of the lubricating oil, ρ is the density of the lubricating oil, and Δt is the temperature difference between the inlet and outlet of the radiator;

[0088] S230. According to the calculation result of step S220, a matrix statistical table of required flow and parts to be lubricated is established. For example, the speed interval is 1000r / min, and the torque interval is 50Nm, and a matrix of required flow at different gears is obtained, as shown in FIG2 .

[0089] In one embodiment, after establishing the matrix statistical table of required flow and parts to be lubricated, the method further includes step S400:

[0090] S410, establishing k standard working conditions, each standard working condition corresponding to a different required flow range;

[0091] S420, dividing the oil circuit and the parts to be lubricated on the oil circuit into regions according to the positions of the parts to be lubricated, and supplying lubricating oil at a corresponding preset flow rate to each region.

[0092] Step S300 can be executed according to the rules formulated in S400. Specifically, the electric pump control strategy is formulated based on the demand flow matrix table, the electric pump performance and the system control capability, and the oil supply condition is finally determined to be 8 spans to ensure the total oil supply, that is, the k value of S410 is 8, and 8 standard conditions are established as shown in Figure 3, each standard condition corresponds to a q value, and each standard condition corresponds to a speed and torque range, so as to realize the division of the matrix statistical table.

[0093] In step S420, in order to ensure that the supply at each position in the demand flow matrix meets the demand, the system's total lubrication oil circuit is layered and grouped for optimization, and the oil circuit and the parts to be lubricated on the oil circuit are regionally layered according to the positions of the parts to be lubricated. Each regional module includes at least one part to be lubricated and the front and rear oil circuits. One or more regional modules are divided into an oil supply layer. The oil supply layer and the regional module are the regional layering scheme.

[0094] Furthermore, the specific characteristic index of the stratification method is: after the optimization of the previous layer is completed, the change of the design variables in the optimization process of the next layer will not cause a significant change in the flow rate that has been allocated in the previous layer. For example, in the regional stratification example shown in Figure 4, each branch is an oil supply layer. For example, the oil circuit where the output gear is located also includes a multi-layered structure. The output gear of the upper layer does not interfere with the reduction gear of the lower layer. A node of each branch is a region.

[0095] The hierarchical grouping optimization was experimentally verified based on the 1D-3D coupling simulation software. The simulation results based on the supply flow were compared with the target demand flow matrix table. The minimum difference was greater than 0, as shown in Figure 5. Finally, it was confirmed that the supply flow met the design requirements and ensured the reliability of the lubrication system.

[0096] The present application also provides a vehicle that is lubricated using the above-mentioned multi-speed dual-motor electric drive box lubrication control method, and the vehicle has dual-motor drive and adopts multi-speed control.

[0097] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0098] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be construed as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent application shall be subject to the attached claims.

Claims

1. A lubrication control device for a multi-speed dual-motor electric drive box, characterized in that: The control device comprises: Oil supply drive, used to provide circulation power to the lubricating oil; An oil circuit is provided between the oil supply drive member and the parts to be lubricated of the electric drive box; A control component, the control component includes an acquisition unit, a calculation unit and an output unit, the acquisition unit is used to obtain motion data of the parts to be lubricated and the gear data of the motor, the calculation unit is used to calculate the required flow rate according to the motion data and the gear data, and the output unit is used to send a control signal to the oil supply drive according to the required flow rate, so that the oil supply drive supplies lubricating oil of the required flow rate.

2. The lubrication control device for a multi-speed dual-motor electric drive box according to claim 1, characterized in that: There are two oil supply drive members, and two groups of oil circuits. Each group of oil circuits includes a shell oil circuit arranged in the electric drive box and a pipeline oil circuit arranged between the oil supply drive member and the shell oil circuit.

3. The lubrication control device for a multi-speed dual-motor electric drive box according to claim 1, characterized in that: The acquisition unit further includes a temperature sensor for acquiring the temperature of the electric drive box, and the calculation unit is used to calculate the required flow rate according to the temperature of the electric drive box.

4. A lubrication control method for a multi-speed dual-motor electric drive box, characterized in that: The control device according to any one of claims 1 to 3 comprises the steps of: Obtain the motion data of the parts to be lubricated and the gear position data of the electric drive box; Calculating the required flow rate according to the motion data and the gear data; A control signal is sent to the oil supply driving component according to the required flow rate, so that the oil supply driving component supplies lubricating oil of the required flow rate.

5. The lubrication control method for a multi-speed dual-motor electric drive box according to claim 4 is characterized in that: The motion data includes the rotation speed and torque of the part to be lubricated.

6. The lubrication control method for a multi-speed dual-motor electric drive box according to claim 4, characterized in that: The parts to be lubricated include gears and bearings, and the step of calculating the required flow rate according to the motion data and the gear data includes: calculating the loss of the parts to be lubricated: The meshing power loss P of the gear is calculated by the following formula: Mi : ， Among them, f m is the meshing friction coefficient, T1 is the small wheel torque, n1 is the small wheel speed, β w is the helix angle; The power loss P of the bearing is calculated by the following formula: Bi : ， Wherein, M1 is the loss torque of the first bearing, M2 is the loss torque of the second bearing, and n is the rotational speed.

7. The lubrication control method for a multi-speed dual-motor electric drive box according to claim 6, characterized in that: The first bearing is a radial load bearing, and the second bearing is an axial cylindrical roller bearing; The radial load bearing loss torque M1 is calculated by the following formula: ， Where f1 is the friction factor of the radial load bearing, p1 is the equivalent dynamic load of the bearing, d m is the average diameter of the bearing, a and b are correction coefficients; The axial cylindrical roller bearing loss torque M2 is calculated by the following formula: ， Where f2 is the friction factor of the cylindrical roller bearing, F a is the axial load, d m is the average bearing diameter.

8. The lubrication control method for a multi-speed dual-motor electric drive box according to claim 4, characterized in that: The step of calculating the required flow rate according to the motion data and the gear data comprises: Calculating the power loss of the parts to be lubricated according to the motion data and the gear data; The required flow rate q is calculated according to the power loss of the parts to be lubricated by the following formula: Among them, P G is the power loss of the parts to be lubricated, C p is the specific heat capacity of the lubricating oil, ρ is the density of the lubricating oil, and Δt is the temperature difference between the inlet and outlet of the radiator; Establish a matrix statistical table of required flow and parts to be lubricated.

9. The lubrication control method for a multi-speed dual-motor electric drive box according to claim 8, characterized in that: After the matrix statistical table of required flow and parts to be lubricated is established, the following steps are also included: Establish k standard working conditions, each of which corresponds to a different required flow range; According to the location of the parts to be lubricated, the oil circuit and the parts to be lubricated on the oil circuit are divided into regions, and the lubricating oil is supplied to each region at a corresponding preset flow rate.

10. A vehicle, characterized in that: Lubrication is performed using the lubrication control method for a multi-speed dual-motor electric drive box as described in any one of claims 4 to 9.

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