Dual-electric-motor powertrain with oil collection for differential lubrication, and vehicle

Abstract

A dual-electric-motor powertrain (10) with oil collection for differential lubrication, and a vehicle (1). The dual-electric-motor powertrain (10) comprises two electric motors (200) and a speed reducer (300). A powertrain housing (100) is used to form a speed reducer chamber (110) and two electric motor chambers (120). The speed reducer chamber (110) is used for accommodating a parallel-shaft gear set and a differential (320). The powertrain housing (100) comprises a differential shaft hole (130) and two electric motor shaft holes (140). A chamber wall of the speed reducer chamber (110) comprises a bearing groove (112) and an oil-collecting protrusion (111), the oil-collecting protrusion (111) being used for collecting lubricating oil and guiding the lubricating oil to the differential (320). The distance between the center of the bearing groove (112) and the other electric motor shaft hole (140) is greater than the distance between at least one of one electric motor shaft hole (140) or the differential shaft hole (130) and the other electric motor shaft hole (140); and the oil-collecting protrusion (111) is arranged between an intermediate gear (312a) or an output gear (314) of the parallel-shaft gear set and the chamber wall of the speed reducer chamber (110). In the case of a vertical speed reducer, integrating oil-collecting and oil-guiding functions into the oil-collecting protrusion (111) helps prolong the service life of the differential (320) and enhance the structural strength of the powertrain, thereby ensuring driving safety.

Description

Dual-motor powertrain and vehicle with oil-lubricated differential

[0001] This application claims priority to Chinese Patent Application No. 202421210213.2, filed on May 29, 2024, with the China National Intellectual Property Administration, entitled "Dual-motor powertrain and vehicle with oil-lubricating differential", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of powertrains, and in particular to a dual-motor powertrain and vehicle with an oil-lubricated differential. Background Technology

[0003] In the new energy vehicle industry, the powertrain is the primary power source for vehicles. Among its components, the differential, a crucial part of the powertrain, allows the left and right wheels to rotate at different speeds through the coordinated action of its internal transmission components when the vehicle is turning or driving on uneven surfaces. However, current differentials suffer from insufficient lubrication, which can lead to severe wear on the transmission components, reducing the differential's lifespan, damaging the structural strength of the powertrain, and ultimately affecting driving safety. Summary of the Invention

[0004] This application provides a dual-motor powertrain and vehicle with an oil-lubricated differential.

[0005] In a first aspect, embodiments of this application provide a dual-motor powertrain with an oil-lubricated differential. The dual-motor powertrain includes two motors and a reducer. The assembly housing of the dual-motor powertrain forms a reducer cavity and two parallel motor cavities. The two motor cavities are used to fix the stators of the two motors, respectively, and the reducer cavity accommodates a parallel shaft gear set of the reducer and a differential. The assembly housing includes a differential shaft hole and two motor shaft holes. One differential shaft hole passes through a wheel drive shaft, one motor shaft hole connects one motor cavity and one reducer cavity, and the other motor shaft hole connects another motor cavity and one reducer cavity. The cavity wall of one reducer cavity includes a bearing groove and an oil-collecting protrusion. The bearing groove is used to fix a bearing on an intermediate shaft of one parallel shaft gear set, and the oil-collecting protrusion is used to collect lubricating oil and guide it to the differential. The distance between the center of one bearing groove and the center of the other motor shaft hole is greater than the distance between the center of at least one of the motor shaft holes or the center of one differential shaft hole and the center of the other motor shaft hole. An oil collecting protrusion is arranged between an intermediate gear or an output gear of a parallel shaft gear set and the cavity wall of a reducer chamber.

[0006] In this embodiment, the parallel shaft gear set and the differential are located in the reducer cavity. The cavity wall of the reducer cavity includes an oil collecting protrusion. The differential receives lubricating oil collected from the oil collecting protrusion to prevent severe wear of the differential. One source of the lubricating oil collected by the oil collecting protrusion is oil thrown off by an intermediate gear or an output gear of the parallel shaft gear set.

[0007] In this application, the position of the oil collecting protrusion needs to coordinate with the parallel shaft gear set, and the gear arrangement of the parallel shaft gear set is affected by the layout of other internal components within the dual-motor powertrain. Therefore, the position of the oil collecting protrusion needs to be adjusted according to the layout of the internal components of the dual-motor powertrain; otherwise, it may negatively affect the oil collecting and guiding functions of the oil collecting protrusion, reducing the lubrication efficiency of the differential.

[0008] The positional relationship between the two motor cavities and the reducer cavity represents the positional relationship between the two motors and the reducer in a dual-motor powertrain, i.e., the two motors are arranged in parallel on one side of the reducer. The positional relationship between the two motor shaft holes, the differential shaft hole, and the bearing groove represents the layout characteristics of the reducer in the dual-motor powertrain. Specifically, the distance between the center of one bearing groove and the center of the other motor shaft hole is greater than the distance between the center of at least one of the motor shaft holes or the differential shaft hole and the center of the other motor shaft hole. This indicates that the parallel shaft gear set has a transmission connection with one motor. To avoid interference between the parallel shaft gear set, the differential, and the other motor, the other motor needs to be staggered from the reducer, so that the reducer in the dual-motor powertrain presents a vertical reducer structure. The main difference between a vertical reducer and a horizontal reducer is not the internal arrangement of the reducer, but rather the arrangement of the reducer as a whole within the powertrain.

[0009] Based on the layout of the internal components of the dual-motor powertrain and the structure of the vertical reducer, the oil collecting protrusion in this embodiment is located between an intermediate wheel or an output wheel of a parallel shaft gear set and the cavity wall of the reducer chamber. This is equivalent to the oil collecting protrusion being arranged in the overlapping area of ​​the projection of an intermediate wheel and an output wheel along the axial direction of the dual-motor powertrain, so that regardless of whether the differential protrudes towards or away from an intermediate wheel, the oil collecting protrusion can collect part of the lubricating oil thrown by the parallel shaft gear set and guide the lubricating oil to the differential.

[0010] In one embodiment, along the axial direction of the dual-motor powertrain, a motor shaft bore is used for alignment with an input gear of a parallel-shaft gear set, the input gear for meshing with an intermediate gear, and along the axial direction of the dual-motor powertrain, a differential shaft bore is used for alignment with a differential. The distance between the center of one motor shaft bore and the center of one differential shaft bore is less than the distance between the center of at least one of the motor shaft bores or the center of one differential shaft bore and the center of the other motor shaft bore. A collecting protrusion is arranged radially between one motor shaft bore and one differential shaft bore of the dual-motor powertrain.

[0011] In this embodiment, the oil collecting protrusions are arranged between a motor shaft hole and a differential shaft hole. The motor shaft hole is used to align with the input gear of the parallel shaft gear set, and the differential shaft hole is used to align with the differential. The positional relationship between the motor shaft hole and the differential shaft hole represents the positional relationship between the input gear and the differential. The distance between the center of one motor shaft hole and the center of one differential shaft hole is less than the distance between the center of one motor shaft hole or at least one differential shaft hole and the center of another motor shaft hole. This shortens the distance the lubricating oil travels between the input gear and the oil collecting protrusions, and between the oil collecting protrusions and the differential, thus improving the efficiency of oil collection and guidance by the oil collecting protrusions.

[0012] In one embodiment, the distance between an oil collection protrusion and the center of a differential shaft hole is less than the distance between an oil collection protrusion and the center of a motor shaft hole.

[0013] In this embodiment, the oil collecting protrusion is closer to the differential shaft hole than the motor shaft hole, which helps to shorten the movement path of lubricating oil from the oil collecting protrusion to the differential and improves the accuracy of lubricating oil flow to the differential.

[0014] In one embodiment, the cavity wall of a motor cavity includes an oil return hole for connecting a motor cavity and a reducer cavity. Specifically, along the radial direction of the dual-motor powertrain, an oil return hole is arranged between a motor shaft bore and an oil collection protrusion, and the distance between the center of the oil return hole and the oil collection protrusion is less than the distance between the center of the oil return hole and the center of the motor shaft bore.

[0015] In this embodiment, a motor shaft hole, an oil collection protrusion, and a differential shaft hole are arranged radially along the dual-motor powertrain, meaning there is a height difference between the motor, the oil collection protrusion, and the differential along the radial direction of the dual-motor powertrain. An oil return hole in the cavity wall of one motor chamber is located between the motor shaft hole and the oil collection protrusion, creating a height difference between the oil return hole, the oil collection protrusion, and the differential housing. Along the axial direction of the dual-motor powertrain, the two openings of the oil return hole connect the motor chamber and the reducer chamber, respectively. Due to the height difference, lubricating oil in one motor chamber can flow to the oil collection protrusion through the oil return hole, which helps increase the amount of lubricating oil collected by the oil collection protrusion and improves the utilization rate of the lubricating oil.

[0016] In this embodiment, the distance between the center of a motor shaft hole and the oil collecting protrusion is greater than the distance between the center of the oil collecting protrusion and the center of the differential shaft hole, providing sufficient space for opening an oil return hole between a motor shaft hole and the oil collecting protrusion, so that an oil return hole can be close to the bottom of a motor cavity, so that the lubricating oil deposited at the bottom of a motor cavity due to gravity can flow to the oil collecting protrusion through an oil return hole.

[0017] In this embodiment, the oil slinging of an output wheel and an intermediate wheel, as well as the oil return of an oil return hole, all belong to the passive oil collection method of the oil collection protrusion. Passive oil collection is greatly affected by the motor speed, that is, the lubricating oil needs to rely on the power brought by the high-speed rotation of the motor. When the motor speed is high, the oil collection protrusion can provide more lubricating oil to the differential through passive oil collection, which is beneficial for the differential to be fully lubricated under high-speed rotation.

[0018] In one embodiment, another intermediate gear of a parallel shaft gear set is used to mesh with an output gear, and a bearing groove along the axial direction of the dual-motor powertrain is used to align with one intermediate gear and the other intermediate gear. The distance between the center of an oil collection protrusion and the center of a bearing groove is less than the distance between the center of an oil collection protrusion and the center of either a motor shaft hole or a differential shaft hole.

[0019] In this embodiment, both intermediate gears are mounted on the intermediate shaft of the parallel shaft gear set, spaced apart from the output gear and meshing with it. Along the axial direction of the dual-motor powertrain, both intermediate gears are aligned with bearing grooves. The oil collecting protrusion is closer to the bearing groove than the motor shaft hole and differential shaft hole. When the oil collecting protrusion is located between the reducer cavity wall and the output gear, its proximity to the bearing groove facilitates the collection of some lubricating oil thrown out by the other intermediate gear. When the oil collecting protrusion is located between the reducer cavity wall and one intermediate gear, its proximity to the bearing groove facilitates the collection of some lubricating oil thrown out by one intermediate gear. This embodiment, by adjusting the distance between the oil collecting protrusion and the bearing groove, one motor shaft hole, and the differential shaft hole, can reduce the difficulty of oil collection in different scenarios.

[0020] In one embodiment, along the axial direction of the dual-motor powertrain, an oil collection protrusion faces an intermediate wheel protrusion, and the distance between the oil collection protrusion and the intermediate wheel is less than the distance between a differential shaft hole and the intermediate wheel.

[0021] In this embodiment, the protruding direction of the oil collecting protrusion is related to the arrangement of the differential in the reducer. When the differential protrudes towards an intermediate wheel, the protruding direction of the oil collecting protrusion also faces an intermediate wheel, facilitating the collection of some lubricating oil thrown out by an intermediate wheel and improving oil collection efficiency. The oil collecting protrusion is closer to an intermediate wheel than the differential shaft hole, shortening the movement path of the lubricating oil between the intermediate wheel and the oil collecting protrusion, and preventing the lubricating oil from flowing directly into the differential shaft hole. If the lubricating oil flows directly into the differential shaft hole, it may accumulate inside, causing oil churning loss.

[0022] In one embodiment, along the axial direction of the dual-motor powertrain, an oil collection protrusion faces an output wheel protrusion, and the distance between the oil collection protrusion and the output wheel is less than the distance between a differential shaft bore and the output wheel.

[0023] In this embodiment, when the differential is away from an intermediate wheel protrusion, the protruding direction of the oil collecting protrusion faces the output wheel, which facilitates the collection of some of the lubricating oil thrown out by the output wheel and improves the oil collection efficiency. The oil collecting protrusion is closer to the output wheel than the differential shaft hole, which can shorten the movement path of the lubricating oil between the output wheel and the oil collecting protrusion, and also prevent the lubricating oil in the oil collecting protrusion from flowing directly into the differential shaft hole.

[0024] In one embodiment, an oil collection protrusion includes two oil collection sections, one end of which intersects with one end of the other oil collection section, and the other ends of which are spaced apart. The opening of the oil collection section and the other oil collection section at the included angle along the radial direction of the dual-motor powertrain faces a motor shaft hole and is away from a differential shaft hole.

[0025] In this embodiment, one oil collecting section and another oil collecting section form a V-shape. The opening of the angle between the two oil collecting sections faces away from the differential shaft hole, meaning the intersecting end of the two oil collecting sections faces the differential, thus collecting and guiding the lubricating oil to the differential. The opening of the angle between the two oil collecting sections faces a motor shaft hole, meaning the other end of the separated oil collecting sections faces the input wheel and a return oil hole, which improves the efficiency of the oil collecting protrusion in collecting lubricating oil from the input wheel and the return oil hole. In this embodiment, both sides of the oil collecting section along the circumference of the dual-motor powertrain can be used to collect lubricating oil.

[0026] In one embodiment, the distance between the other end of one oil collecting section and the center of a bearing groove is less than the distance between the other end of another oil collecting section and the center of another motor shaft hole.

[0027] In the embodiments of this application, the other end of one oil collecting section is spaced apart from the other end of another oil collecting section. The distance between the other end of one oil collecting section and the bearing groove is less than the distance between the other end of another oil collecting section and another motor shaft hole. That is, the oil collecting protrusion is closer to the bearing groove than the other motor shaft hole, which makes it easier for the oil collecting protrusion to collect part of the lubricating oil thrown out by one intermediate wheel or the other intermediate wheel.

[0028] In one embodiment, an oil collection protrusion includes a flow hole extending through one end of the oil collection protrusion, and the distance between the center of the flow hole and the center of a differential shaft hole is less than the distance between the other end of the oil collection protrusion and the center of a differential shaft hole.

[0029] In this embodiment, along the radial direction of the dual-motor powertrain, a flow passage extends through one end of the oil collecting protrusion. The distance between the flow passage and the differential shaft hole is less than the distance between the other end of the oil collecting protrusion and the differential shaft hole. This allows the lubricating oil collected by the oil collecting protrusion to tend to move to the flow passage first and then be guided to the differential, improving the accuracy of oil guidance and achieving directional lubrication of the differential. If the oil collecting protrusion did not include a flow passage, the lubricating oil might flow out before reaching one end of the oil collecting protrusion, making it impossible to ensure that the lubricating oil collected by the oil collecting protrusion can flow directly into the differential, which is detrimental to improving the lubrication effect on the differential.

[0030] In this embodiment, the two ends of the oil collecting protrusion cooperate with the flow holes to achieve simultaneous oil collection and guidance, reducing the accumulation of lubricating oil on the oil collecting protrusion and ensuring that the oil collecting protrusion has sufficient space for collecting lubricating oil. If the oil collecting protrusion does not include flow holes, lubricating oil may need to accumulate to a certain extent before overflowing from the oil collecting protrusion, thereby reducing the efficiency of oil collection and guidance.

[0031] In one embodiment, a differential includes a planetary shaft and a differential gear set, wherein the planetary shaft is drive-connected to the differential gear set. A flow passage along the radial direction of the dual-motor powertrain is at least partially aligned with a planetary shaft, the inner diameter of the flow passage being less than or equal to the outer diameter of the planetary shaft, the flow passage guiding lubricating oil to the planetary shaft, and the planetary shaft discharging lubricating oil to the differential gear set.

[0032] In this embodiment, the radial alignment of a flow orifice along the dual-motor powertrain with a planetary shaft at least partially means that the projection of the radial flow orifice of the dual-motor powertrain at least partially overlaps with the projection of the planetary shaft, so that the oil collecting protrusion can guide the collected lubricating oil to the planetary shaft. The inner diameter of the flow orifice is less than or equal to the outer diameter of the planetary shaft, improving the accuracy of the flow orifice in guiding the lubricating oil to the planetary shaft.

[0033] In this embodiment, the planetary shaft is connected to the differential gear set. When the planetary shaft rotates, lubricating oil is thrown onto the differential gear set, thereby lubricating it. This embodiment uses the planetary shaft as an intermediate medium for lubricating the differential gear set. By guiding lubricating oil to the planetary shaft, the rotation of the planetary shaft expands the coverage area of ​​the lubricating oil, achieving a redistribution of the lubricating oil within the differential housing. If the oil collection protrusion directly guides the lubricating oil to a single gear in the differential gear set, although the lubricating oil has a better lubricating effect on that single gear, the coverage area of ​​the lubricating oil is limited to that single gear and its adjacent gears, which may lead to localized insufficient lubrication of some gears in the differential.

[0034] In one embodiment, an oil collecting protrusion forms an oil collecting groove with the cavity wall of the reducer chamber, with the groove opening facing an intermediate wheel or an output wheel along the axial direction of the dual-motor powertrain. The distance between a flow passage and a differential housing along the radial direction of the dual-motor powertrain is less than the distance between the bottom of the oil collecting groove and the differential housing of a differential. A differential housing is used to fix to an output wheel and to house a planetary shaft and a differential gear set.

[0035] In this embodiment, the bottom and opening of the oil collection groove along the axial direction of the dual-motor powertrain are opposite each other, and the bottom of the oil collection groove is part of the cavity wall of the reducer chamber. The flow hole is closer to the differential housing than the bottom of the oil collection groove, so that the lubricating oil at the bottom of the oil collection groove tends to flow towards the flow hole, avoiding excessive lubricating oil accumulation at the bottom of the oil collection groove and improving the utilization rate of lubricating oil.

[0036] In one embodiment, the distance between a flow passage and a differential housing along the radial direction of the dual-motor powertrain is equal to the distance between the bottom of an oil collection trough and a differential housing. This embodiment of the application can reduce the processing difficulty and cost of the oil collection trough without increasing lubricating oil flow resistance.

[0037] In one embodiment, along the axial direction of the dual-motor powertrain, a flow passage is adjacent to and connected to the opening of an oil collection trough.

[0038] In this embodiment, the axial flow hole and the groove of the oil collection groove along the dual-motor powertrain are both located at the end of the oil collection protrusion facing the oil collection protrusion of the parallel shaft gear set. The connection between the flow hole and the groove of the oil collection groove is beneficial to accelerating the output of lubricating oil.

[0039] In one embodiment, along the axial direction of the dual-motor powertrain, a flow passage is spaced apart from the opening of an oil collection groove, and along the radial direction of the dual-motor powertrain, the distance between the opening of an oil collection groove and a differential housing is less than the distance between a flow passage and a differential housing.

[0040] In this embodiment, although the axial flow passage of the dual-motor powertrain is spaced apart from the opening of the oil collection groove, the flow passage is closer to the differential housing than the opening of the oil collection groove. This allows some of the lubricating oil flowing to the opening of the oil collection groove to flow back to the flow passage, thereby providing directional lubrication to the differential. In one embodiment, the flow passage is closer to the differential housing than both the opening and bottom of the oil collection groove. This embodiment helps to reduce the accumulation of lubricating oil in the oil collection groove.

[0041] In one embodiment, the cavity wall of a reducer chamber further includes an oil injection hole for fixing a nozzle, and the nozzle for spraying lubricating oil onto an oil collecting protrusion. The oil injection hole is arranged between an oil collecting protrusion and another motor shaft hole, and the distance between the center of the oil injection hole and the oil collecting protrusion is less than the distance between the center of the oil injection hole and the center of the other motor shaft hole.

[0042] In this embodiment, the spray nozzle is used to spray lubricating oil onto the oil collecting protrusion via a nozzle. The spray nozzle is closer to the oil collecting protrusion than the center of the motor shaft hole, which helps reduce the difficulty of spraying lubricating oil onto the protrusion. The oil collecting protrusion collects the lubricating oil sprayed by the nozzle, which is an active oil collection method. Compared to passive oil collection, active oil collection is less affected by the motor speed; the nozzle can actively spray oil onto the oil collecting protrusion under both high-speed and low-speed motor operating conditions.

[0043] Secondly, embodiments of this application provide a vehicle, which includes a frame and a dual-motor powertrain as described in any embodiment of the first aspect. The frame is used to mount the dual-motor powertrain, and a differential of the dual-motor powertrain is used to drive the wheels of the vehicle. An oil collection protrusion is higher than the differential along the direction of gravity.

[0044] In this embodiment, when the dual-motor powertrain is applied to a vehicle, the flow of lubricating oil is affected by gravity. Therefore, it is necessary to set an oil collection protrusion higher than the differential along the direction of gravity so that the flow path of lubricating oil between the oil collection protrusion and the differential is in line with the direction of gravity, which helps to reduce flow resistance.

[0045] In one embodiment, the minimum angle between an oil collecting protrusion and the ground is greater than or equal to 20 degrees and less than or equal to 35 degrees.

[0046] In this embodiment, the minimum angle between the oil collecting protrusion and the ground is set to 20 to 35 degrees. This effectively reduces the risk of backflow of lubricating oil from the oil collecting protrusion, avoids negative impacts on the differential's lubrication effect under special operating conditions, and thus improves vehicle safety performance and ensures smooth vehicle operation. If the minimum angle between the side of the oil collecting protrusion that acts as an oil-blocking element and the ground is too small, when the vehicle is going uphill or downhill, the lubricating oil falling on this side will have difficulty flowing to the differential, and may even backflow on the oil collecting protrusion, impairing the lubrication effect on the differential. If the minimum angle between the side that acts as an oil-blocking element and the ground is too large, although it will not affect the oil collecting and guiding effect of the oil collecting protrusion when the vehicle is going uphill or downhill, when the vehicle is driving on level ground, it will reduce the angle between the oil collecting sections of the protrusion, thereby reducing the space available for oil collection in the oil collecting groove, and thus reducing the amount of lubricating oil that the oil collecting protrusion can collect. Attached Figure Description

[0047] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the embodiments of this application will be described below.

[0048] Figure 1 is a structural schematic diagram of the vehicle provided in an embodiment of this application;

[0049] Figure 2 is a schematic diagram of the dual-motor powertrain provided in an embodiment of this application;

[0050] Figure 3 is a schematic diagram of the dual-motor powertrain provided in an embodiment of this application;

[0051] Figure 4 is a structural schematic diagram of the assembly housing provided in an embodiment of this application;

[0052] Figure 5 is a partial structural schematic diagram of the assembly housing provided in an embodiment of this application;

[0053] Figure 6 is a partial enlarged view of part M1 in the assembly housing shown in Figure 4;

[0054] Figure 7 is a partial structural schematic diagram of the assembly housing provided in an embodiment of this application;

[0055] Figure 8 is a partial structural schematic diagram of the assembly housing provided in an embodiment of this application;

[0056] Figure 9 is a partial exploded view of the dual-motor powertrain provided in an embodiment of this application;

[0057] Figure 10 is a partial enlarged view of the M2 part in the dual-motor powertrain shown in Figure 9;

[0058] Figure 11 is a partial structural schematic diagram of the dual-motor powertrain provided in an embodiment of this application. Detailed Implementation

[0059] The technical solutions of the embodiments of this application will be described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments.

[0060] Current differentials suffer from insufficient lubrication. This application provides a dual-motor powertrain with an oil-lubricated differential. The dual-motor powertrain includes two motors and a reducer. The assembly housing of the dual-motor powertrain forms a reducer cavity and two parallel motor cavities. The two motor cavities respectively fix the stators of the two motors. The reducer cavity accommodates a parallel shaft gear set of the reducer and a differential. The assembly housing includes a differential shaft hole and two motor shaft holes. One differential shaft hole passes through a wheel drive shaft, one motor shaft hole connects one motor cavity and the reducer cavity, and the other motor shaft hole connects the other motor cavity and the reducer cavity. The cavity wall of one reducer cavity includes a bearing groove and an oil-collecting protrusion. The bearing groove fixes a bearing on an intermediate shaft of the parallel shaft gear set, and the oil-collecting protrusion collects lubricating oil and guides it to the differential. The distance between the center of one bearing groove and the center of the other motor shaft hole is greater than the distance between the center of at least one of the motor shaft holes or the center of one differential shaft hole and the center of the other motor shaft hole. An oil collecting protrusion is arranged between an intermediate gear or an output gear of a parallel shaft gear set and the cavity wall of a reducer chamber.

[0061] In the case of a vertical reducer, this application integrates the functions of oil collection and oil guiding into a single oil collection protrusion to lubricate the differential. This helps to improve the service life of the differential and the structural strength of the powertrain, thereby ensuring driving safety.

[0062] The powertrain provided in this application embodiment can be applied to vehicles.

[0063] Please refer to Figure 1, which is a structural schematic diagram of vehicle 1 provided in an embodiment of this application. In this embodiment, vehicle 1 refers to a wheeled device driven or towed by a power unit. In this embodiment, vehicle 1 includes a frame 20, a battery pack 30, and a dual-motor powertrain 10. The frame 20 is the structural skeleton of vehicle 1, used to mount the battery pack 30 and the dual-motor powertrain 10, and can withstand the loads from the internal and external environment of vehicle 1. The battery pack 30 is used to supply power to the dual-motor powertrain 10; the battery pack 30 can also be referred to as a power battery. The dual-motor powertrain 10 is the power source of vehicle 1, and is used to drive the wheels 40 of vehicle 1.

[0064] Please refer to Figures 2 and 3. Figure 2 is a schematic diagram of the structure of the dual-motor powertrain 10 provided in an embodiment of this application, and Figure 3 is a schematic diagram of the structure of the dual-motor powertrain 10 provided in an embodiment of this application. In this embodiment, the dual-motor powertrain 10 includes two motors 200 and a reducer 300. The reducer 300 includes a parallel shaft gear set 310 and a differential 320. At least one of the two motors 200 transmits power to the differential 320 through the parallel shaft gear set 310. Exemplarily, as shown in Figures 2 and 3, in one embodiment, the parallel shaft gear set 310 includes an input gear 311, an intermediate gear 312a, another intermediate gear 312b, and an output gear 314. The input gear 311 is connected to the motor 200 and meshes with the intermediate gear 312a. The intermediate gear 312a and the other intermediate gear 312b are both mounted on an intermediate shaft 313, and the other intermediate gear 312b meshes with the output gear 314. An output wheel 314 is driven to a differential 320. Referring to Figures 2 and 3, in one embodiment, the differential 320 protrudes toward either an intermediate wheel 312a or an output wheel 314.

[0065] As shown in Figures 2 and 3, in one embodiment, the vehicle further includes two wheel drive shafts 50. Each wheel drive shaft 50 is connected to a differential 320 and a wheel drive, respectively. The power generated by the dual-motor powertrain 10 can be sequentially transmitted to the wheel drive shafts 50 and the wheels to enable the vehicle to move. When the vehicle is turning or driving on uneven surfaces, the differential 320 can enable the left and right wheel drive shafts 50 to rotate at different speeds, thereby causing the left and right wheels to rotate at different speeds and ensuring that the wheels perform rolling motion.

[0066] In one embodiment, the dual-motor powertrain 10 is a pure electric power system, and both motors 200 are electric motors. The electric motors are used to convert electrical energy into mechanical energy and transmit the mechanical energy to the differential 320 through the parallel shaft gear set 310.

[0067] As shown in Figures 2 and 3, in one embodiment, the dual-motor powertrain 10 is a hybrid power system. The dual-motor powertrain 10 further includes an engine 400, one of the two motors 200 being an electric motor, and the other motor 200 being a generator. The engine 400 is used to convert other forms of energy into kinetic energy; exemplarily, the engine 400 can be a combustion engine used to convert chemical energy into kinetic energy. The engine 400 is drive-connected to the generator, providing power to the generator, which converts the kinetic energy output by the engine 400 into electrical energy. In one embodiment, the generator can charge the battery pack 30.

[0068] As shown in Figures 2 and 3, in one embodiment, the dual-motor powertrain 10 further includes a power supply device 500, which is electrically connected to the generator, battery pack 30, and motor. The power supply device 500 is used to control and switch the power mode of the powertrain. In one embodiment, the power supply device 500 includes at least one of a motor controller, an on-board charging device, a DC-DC converter, a DC power supply device, and a vehicle controller.

[0069] In a dual-motor powertrain, the differential is the core component used to achieve different speeds for the left and right wheels. The differential typically contains complex transmission components. If there is severe wear among these contacting transmission components, its service life may be shortened, and in severe cases, it can lead to safety accidents.

[0070] This application embodiment improves the layout of the oil collection component in the dual-motor powertrain, thereby enhancing the lubrication effect on the differential and improving the safety performance of the dual-motor powertrain and the vehicle.

[0071] Please refer to Figures 4 to 6. Figure 4 is a structural schematic diagram of the assembly housing 100 provided in an embodiment of this application. Figure 5 is a partial structural schematic diagram of the assembly housing 100 provided in an embodiment of this application. Figure 6 is a partial enlarged view of part M1 in the assembly housing 100 shown in Figure 4. In particular, to clearly show the arrangement of the oil collecting protrusions 111 in the assembly housing 100, Figure 5 only retains a part of the structure of the assembly housing 100.

[0072] As shown in Figures 4 and 5, the assembly housing 100 of the dual-motor powertrain 10 forms a reducer cavity 110 and two parallel motor cavities 120. The two motor cavities 120 are used to fix the stators of the two motors 200, respectively, and the reducer cavity 110 is used to accommodate a parallel shaft gear set and a differential of a reducer 300. As shown in Figures 4 and 5, the assembly housing 100 includes a differential shaft hole 130 and two motor shaft holes 140. One differential shaft hole 130 passes through a wheel drive shaft, one motor shaft hole 140 connects one motor cavity 120 and one reducer cavity 110, and the other motor shaft hole 140 connects the other motor cavity 120 and one reducer cavity 110.

[0073] As shown in Figure 6, the cavity wall of a reducer chamber 110 includes a bearing groove 112 and an oil collecting protrusion 111. The bearing groove 112 is used to fix a bearing on an intermediate shaft of a parallel shaft gear set, and the oil collecting protrusion 111 is used to collect lubricating oil and guide it to a differential. As shown in Figure 5, the distance between the center of a bearing groove 112 and the center of another motor shaft hole 140 is greater than the distance between the center of at least one of the motor shaft holes 140 or the center of a differential shaft hole 130 and the center of the other motor shaft hole 140. An oil collecting protrusion 111 is arranged between an intermediate gear 312a or an output gear 314 of a parallel shaft gear set 310 and the cavity wall of the reducer chamber 110.

[0074] In this embodiment of the application, for ease of description, as shown in Figures 2 and 3, the two motors 200 are referred to as one motor 200a and the other motor 200b, respectively. As shown in Figure 4, the two motor cavities 120 of the assembly housing 100 are referred to as one motor cavity 120a and the other motor cavity 120b, respectively, and the two motor shaft holes 140 of the assembly housing 100 are referred to as one motor shaft hole 140a and the other motor shaft hole 140b, respectively. One motor shaft hole 140a is used to connect one motor cavity 120a with one reducer cavity 110, and the other motor shaft hole 140b is used to connect the other motor cavity 120b with one reducer cavity 110. Wherein, the parallel arrangement of one motor cavity 120a and another motor cavity 120b means that the two are arranged in parallel relative to one reducer cavity 110, that is, the arrangement direction of one motor cavity 120a and another motor cavity 120b intersects with the arrangement direction of one motor cavity 120a and one reducer cavity 110, and the arrangement direction of another motor cavity 120b and one reducer cavity 110.

[0075] In this embodiment, the parallel shaft gear set 310 and the differential 320 are located in the reducer cavity 110. The cavity wall of the reducer cavity 110 includes an oil collecting protrusion 111. The differential 320 receives lubricating oil collected from the oil collecting protrusion 111 to prevent severe wear of the differential 320. One source of lubricating oil collected by the oil collecting protrusion 111 is oil jetting from an intermediate gear 312a or an output gear 314 of the parallel shaft gear set 310. In one embodiment, an intermediate gear 312a and an output gear 314 are arranged at an axial distance O along the dual-motor powertrain 10. The output gear 314 is drivenly connected to the differential 320, and the differential 320 protrudes toward or away from an intermediate gear 312a.

[0076] In this application, the position of the oil collecting protrusion 111 needs to cooperate with the parallel shaft gear set 310, and the gear arrangement of the parallel shaft gear set 310 is affected by the layout of other internal components within the dual-motor powertrain. Therefore, the position of the oil collecting protrusion 111 needs to be adjusted according to the layout of the internal components of the dual-motor powertrain; otherwise, it may negatively affect the oil collecting and guiding functions of the oil collecting protrusion 111, reducing the lubrication efficiency of the differential 320.

[0077] The positional relationship between motor cavities 120a, 120b, and reducer cavity 110 represents the positional relationship between motors 200a, 200b, and reducer 300 in the dual-motor powertrain, i.e., motors 200a and 200b are arranged in parallel on one side of reducer 300. The positional relationship between motor shaft holes 140a, 140b, differential shaft hole 130, and bearing groove 112 represents the layout characteristics of reducer 300 in the dual-motor powertrain 10. Specifically, as shown in Figure 5, the distance between the center of bearing groove 112 and the center of motor shaft hole 140b is denoted as L1, the distance between the center of motor shaft hole 140a and the center of motor shaft hole 140b is denoted as L2, and the distance between the center of differential shaft hole 130 and the center of motor shaft hole 140b is denoted as L3. If L1 is greater than at least one of L2 or L3, it indicates that the parallel shaft gear set 310 and the motor 200a have a transmission connection. To avoid interference between the parallel shaft gear set 310 and the differential 320 of the reducer 300 and the motor 200b, the motor 200b and the reducer 300 need to be staggered, so that the reducer 300 presents a vertical reducer structure in the dual-motor powertrain 10. The main difference between a vertical reducer and a horizontal reducer is not the internal layout of the reducer, but rather the arrangement of the reducer as a whole within the powertrain.

[0078] Based on the layout of the internal components of the dual-motor powertrain 10 and the structure of the vertical reducer, the oil collecting protrusion 111 in this embodiment is located between an intermediate gear 312a or an output gear 314 of a parallel shaft gear set 310 and the cavity wall of the reducer cavity 110. This means the oil collecting protrusion 111 is arranged in the overlapping area of ​​the projections of the intermediate gear 312a and the output gear 314 along the axial direction O of the dual-motor powertrain 10. This ensures that regardless of whether the differential 320 protrudes towards or away from an intermediate gear 312a, the oil collecting protrusion 111 can collect a portion of the lubricating oil thrown by the parallel shaft gear set 310 and guide the lubricating oil to the differential 320. If the layout of the oil collecting protrusion in this embodiment is applied to a horizontal reducer, i.e., the oil collecting protrusion is arranged in the overlapping area of ​​the axial projections of an intermediate gear and an output gear in the horizontal reducer, it will increase the difficulty of oil collection and guidance, thus hindering the lubrication of the differential.

[0079] In one embodiment, an oil collection protrusion 111 is higher than a differential 320 along the direction of gravity.

[0080] In this embodiment, when the dual-motor powertrain 10 is applied to the vehicle 1, the flow of lubricating oil is affected by gravity. Therefore, it is necessary to set the oil collection protrusion 111 to be higher than the differential 320 along the direction of gravity, so that the flow path of lubricating oil between the oil collection protrusion 111 and the differential 320 is in line with the direction of gravity, which helps to reduce flow resistance.

[0081] Please refer to Figure 7, which is a partial structural schematic diagram of the assembly housing 100 provided in an embodiment of this application. Figure 7 omits some parts of the assembly housing 100. In one embodiment, a motor shaft hole 140a along the axial direction O of the dual-motor powertrain 10 is used for alignment with an input gear of a parallel shaft gear set, and a differential shaft hole 130 along the axial direction O of the dual-motor powertrain 10 is used for alignment with a differential. The distance between the center of one motor shaft hole 140a and the center of one differential shaft hole 130 is less than the distance between the center of at least one of the motor shaft hole 140a or one differential shaft hole 130 and the center of another motor shaft hole 140b. An oil collecting protrusion 111 is arranged between one motor shaft hole 140a and one differential shaft hole 130 along the radial direction R of the dual-motor powertrain 10.

[0082] In this embodiment, the oil collecting protrusion 111 is arranged between the motor shaft hole 140a and the differential shaft hole 130. The motor shaft hole 140a is used to align with the input wheel 311 of the parallel shaft gear set 310, and the differential shaft hole 130 is used to align with the differential 320. The positional relationship between the motor shaft hole 140a and the differential shaft hole 130 represents the positional relationship between the input wheel 311 and the differential 320.

[0083] In this embodiment of the application, as shown in FIG7, the distance between the center of the motor shaft hole 140a and the center of the differential shaft hole 130 is denoted as L4. L4 is less than at least one of L2 or L3, which can shorten the distance of lubricating oil flowing between the input wheel 311 and the oil collecting protrusion 111 and between the oil collecting protrusion 111 and the differential 320, which is beneficial to improving the efficiency of oil collecting and guiding of the oil collecting protrusion 111.

[0084] Please refer to Figure 8, which is a partial structural schematic diagram of the assembly housing 100 provided in an embodiment of this application. Figure 8 omits some parts of the structure of the assembly housing 100. In one embodiment, the distance between the center of an oil collecting protrusion 111 and the center of a differential shaft hole 130 is less than the distance between the center of an oil collecting protrusion 111 and the center of a motor shaft hole 140a.

[0085] In this embodiment of the application, as shown in FIG8, the distance between an oil collecting protrusion 111 and the center of a differential shaft hole 130 is denoted as L5, and the distance between an oil collecting protrusion 111 and the center of a motor shaft hole 140a is denoted as L6. L5 is less than L6, and the oil collecting protrusion 111 is closer to the differential shaft hole 130 relative to the motor shaft hole 140a. This helps to shorten the movement path of lubricating oil from the oil collecting protrusion 111 to the differential 320, and can improve the accuracy of lubricating oil flow to the differential 320.

[0086] Please refer to Figure 6. In one embodiment, the cavity wall of a motor cavity 120a includes an oil return hole 121, which connects the motor cavity 120a and a reducer cavity 110. Specifically, along the radial direction R of the dual-motor powertrain 10, an oil return hole 121 is arranged between a motor shaft hole 140a and an oil collecting protrusion 111. The distance between the center of an oil return hole 121 and the oil collecting protrusion 111 is less than the distance between the center of an oil return hole 121 and the center of a motor shaft hole 140a.

[0087] In this embodiment, the motor shaft hole 140a, the oil collecting protrusion 111, and the differential shaft hole 130 are arranged radially R along the dual-motor powertrain 10, meaning there is a height difference between the motor 200a, the oil collecting protrusion 111, and the differential 320 along the radial R of the dual-motor powertrain 10. An oil return hole 121 on the cavity wall of the motor cavity 120a is located between the motor shaft hole 140a and the oil collecting protrusion 111, resulting in a height difference between the oil return hole 121, the oil collecting protrusion 111, and the differential housing 323. For ease of description, the oil return hole 121 is referred to as oil return hole 121a. Along the axial direction of the dual-motor power assembly 10, the two openings of the oil return hole 121a are respectively connected to the motor cavity 120a and the reducer cavity 110. Under the action of the height difference, the lubricating oil in the motor cavity 120a can flow to the oil collecting protrusion 111 through the oil return hole 121a, which is beneficial to increase the amount of lubricating oil collected by the oil collecting protrusion 111 and improve the utilization rate of lubricating oil.

[0088] In this embodiment of the application, as shown in FIG8, the distance L6 between the center of the motor shaft hole 140a and the oil collecting protrusion 111 is greater than the distance L5 between the oil collecting protrusion 111 and the center of the differential shaft hole 130. This provides sufficient space for opening the oil return hole 121a between the motor shaft hole 140a and the oil collecting protrusion 111, so that the oil return hole 121a can be close to the bottom of the motor cavity 120a, making it easier for the lubricating oil deposited at the bottom of the motor cavity 120a due to gravity to flow to the oil collecting protrusion 111 through the oil return hole 121a.

[0089] In this embodiment, the oil slinging of an output wheel 314 and an intermediate wheel 312a, as well as the oil return of the return hole 121a, all belong to the passive oil collection method of the oil collecting protrusion 111. Passive oil collection is greatly affected by the motor speed, that is, the lubricating oil needs to rely on the power brought by the high-speed rotation of the motor. When the motor speed is high, the oil collecting protrusion 111 can provide more lubricating oil to the differential 320 through passive oil collection, which is beneficial for the differential 320 to be fully lubricated under high-speed rotation.

[0090] Please refer to Figure 6. In one embodiment, the cavity wall of a motor cavity 120a further includes another oil return hole 121, which connects a motor cavity 120a and a reducer cavity 110. The other oil return hole 121 is spaced apart from an oil collecting protrusion 111 along the circumferential direction C of the dual-motor powertrain 10. The inner diameter of one oil return hole 121 along the circumferential direction C of the dual-motor powertrain 10 is smaller than the inner diameter of the other oil return hole 121.

[0091] In this embodiment, for ease of description, the other oil return hole 121 is referred to as the other oil return hole 121b. The oil return holes 121a and 121b work together to achieve a reasonable distribution of lubricating oil within the reducer 300. Specifically, the oil return holes 121b and the oil collecting protrusions 111 are arranged alternately along the circumferential C direction of the dual-motor power assembly 10, thus the lubricating oil flowing through the oil return holes 121b is unlikely to flow directly to the oil collecting protrusions 111. The inner diameter of the oil return hole 121b is larger than that of the oil return hole 121a, resulting in a higher oil return efficiency for the oil return hole 121b than for the oil return hole 121a. In the lubricating oil flowing from the motor cavity 120a into the reducer cavity 110, a small portion of the lubricating oil flows to the differential 320 through the oil return hole 121a and the oil collecting protrusion 111, while most of the lubricating oil flows to the bottom of the reducer cavity 110 through the oil return hole 121b, providing oil reserves for the parallel shaft gear set 310. When the reducer 300 is working, the parallel shaft gear set 310 shakes the lubricating oil located at the bottom of the reducer cavity 110, which helps reduce the wear of the parallel shaft gear set 310. The shaken lubricating oil can also be collected by the oil collecting protrusion 111.

[0092] Referring to Figure 8, in one embodiment, a bearing groove 112 is provided along the axial direction O of the dual-motor powertrain 10 for alignment with one intermediate wheel and the other intermediate wheel. As shown in Figure 8, the distance between the center of an oil collection protrusion 111 and the center of a bearing groove 112 is less than the distance between the center of an oil collection protrusion 111 and the center of either a motor shaft hole 140a or a differential shaft hole 130.

[0093] In the embodiments of this application, as shown in Figures 2 and 3, intermediate gears 312a and 312b are both sleeved on the intermediate shaft 313 of the parallel shaft gear set 310. Intermediate gear 312a is spaced apart from output gear 314, and intermediate gear 312b meshes with output gear 314. Intermediate gear 312a can also be referred to as the intermediate driven gear, and intermediate gear 312b can also be referred to as the intermediate driving gear.

[0094] In this embodiment, the intermediate wheels 312a and 312b along the axial direction O of the dual-motor powertrain 10 are aligned with the bearing groove 112. As shown in Figure 8, the distance between the oil collecting protrusion 111 and the center of the bearing groove 112 is denoted as L7. L7 is less than L5 and less than L6, indicating that the oil collecting protrusion 111 is closer to the bearing groove 112 than the motor shaft hole 140a and the differential shaft hole 130. When the oil collecting protrusion 111 is located between the cavity wall of the reducer cavity 110 and the output wheel 314, the proximity of the oil collecting protrusion 111 to the bearing groove 112 facilitates the collection of some of the lubricating oil thrown out by the intermediate wheel 312b. When the oil collecting protrusion 111 is located between the cavity wall of the reducer cavity 110 and the intermediate wheel 312a, the proximity of the oil collecting protrusion 111 to the bearing groove 112 facilitates the collection of some of the lubricating oil thrown out by the intermediate wheel 312a. This application embodiment can reduce the difficulty of oil collection by adjusting the distance between the oil collecting protrusion 111 and the bearing groove 112, the motor shaft hole 140a and the differential shaft hole 130 in different scenarios.

[0095] In one embodiment, an oil collection protrusion 111 protrudes toward an intermediate wheel 312a along the axial direction O of the dual-motor powertrain 10. The distance between the oil collection protrusion 111 and the intermediate wheel 312a is less than the distance between a differential shaft bore 130 and the intermediate wheel 312a.

[0096] In this embodiment, the protrusion direction of the oil collecting protrusion 111 is related to the arrangement of the differential 320 in the reducer 300. When the differential 320 protrudes towards the intermediate wheel 312a, the protrusion direction of the oil collecting protrusion 111 also faces the intermediate wheel 312a, which facilitates the oil collecting protrusion 111 in collecting some of the lubricating oil thrown out by the intermediate wheel 312a, thus improving oil collection efficiency. The oil collecting protrusion 111 is closer to the intermediate wheel 312a than the differential shaft hole 130, which can shorten the movement path of the lubricating oil between the intermediate wheel 312a and the oil collecting protrusion 111, and also prevent the lubricating oil in the oil collecting protrusion 111 from flowing directly into the differential shaft hole 130. If the lubricating oil flows directly into the differential shaft hole 130, it may cause the lubricating oil to accumulate in the differential shaft hole 130, resulting in oil churning loss.

[0097] In one embodiment, an oil collection protrusion 111 protrudes toward an output wheel 314 along the axial direction of the dual-motor powertrain 10. The distance between the oil collection protrusion 111 and the output wheel 314 is less than the distance between a differential shaft bore 130 and the output wheel 314.

[0098] In this embodiment, when the differential 320 protrudes away from the intermediate wheel 312a, the protruding direction of the oil collecting protrusion 111 faces the output wheel 314, which facilitates the collection of some of the lubricating oil thrown out by the output wheel 314, thus improving the oil collection efficiency. The oil collecting protrusion 111 is closer to the output wheel 314 than the differential shaft hole 130, which shortens the movement path of the lubricating oil between the output wheel 314 and the oil collecting protrusion 111, and also prevents the lubricating oil in the oil collecting protrusion 111 from flowing directly into the differential shaft hole 130.

[0099] Please continue to refer to Figure 6. In one embodiment, an oil collecting protrusion 111 includes two oil collecting segments 1111. One end of one oil collecting segment 1111 intersects with one end of the other oil collecting segment 1111, and the other ends of one oil collecting segment 1111 are spaced apart from the other ends of the other oil collecting segment 1111. The opening of the oil collecting segment 1111 and the other oil collecting segment 1111 along the radial direction R of the dual motor powertrain 10 faces a motor shaft hole 140a and is away from a differential shaft hole 130.

[0100] In this embodiment, for ease of description, the two oil collecting sections 1111 are referred to as oil collecting section 1111a and oil collecting section 1111b, respectively. Oil collecting sections 1111a and 1111b are V-shaped. The opening of the angle between oil collecting sections 1111a and 1111b faces away from the differential shaft hole 130, meaning that one end of oil collecting sections 1111a and 1111b intersects towards the differential 320, thus serving to collect and guide lubricating oil to the differential 320. The opening of the angle between oil collecting sections 1111a and 1111b faces towards the motor shaft hole 140a, meaning that the other end of oil collecting sections 1111a and 1111b faces towards the input wheel 311 and the return oil hole 121a, which improves the efficiency of the oil collecting protrusion 111 in collecting lubricating oil from the input wheel 311 and the return oil hole 121a.

[0101] In this embodiment, both sides of the oil collecting sections 1111a and 1111b along the circumferential C of the dual-motor powertrain 10 can be used to collect lubricating oil. When the vehicle 1 is under different operating conditions, the movement path of the lubricating oil between the parallel shaft gear set 310 and the oil collecting protrusion 111 changes, and the two sides of the oil collecting sections 1111a and 1111b can play a complementary role in oil collection.

[0102] Assuming the output wheel 314 rotates clockwise, the two sides of the oil collecting section 1111a along the circumference C of the dual-motor powertrain 10 are designated as the first side and the second side, respectively. The two sides of the oil collecting section 1111b along the circumference C of the dual-motor powertrain 10 are designated as the third side and the fourth side, respectively. The second and third sides along the circumference C of the dual-motor powertrain 10 are located between the first and second sides. In one embodiment, when the vehicle is traveling forward on a level road, the output wheel 314 rotates clockwise, causing the lubricating oil swung by the output wheel 314 to tend to move clockwise to the first and third sides. In another embodiment, when the vehicle is reversing on a level road, the output wheel 314 needs to reverse, and the lubricating oil swung by the output wheel 314 tends to move counterclockwise to the second and fourth sides. In one embodiment, when the vehicle goes uphill, the oil collecting sections 1111a and 1111b rotate counterclockwise relative to the horizontal ground, allowing the second and fourth sides to collect the falling lubricating oil. In another embodiment, when the vehicle goes downhill, the oil collecting sections 1111a and 1111b rotate clockwise relative to the horizontal ground, allowing the first and third sides to collect the falling lubricating oil.

[0103] Please continue to refer to Figure 4. In one embodiment, the distance between the other end of one oil collecting section 1111a and the center of one bearing groove 112 is less than the distance between the other end of another oil collecting section 1111b and the center of another motor shaft hole 140b.

[0104] In this embodiment, the other end of the oil collecting section 1111a is spaced apart from the other end of the oil collecting section 1111b. The distance between the other end of the oil collecting section 1111a and the bearing groove 112 is less than the distance between the other end of the oil collecting section 1111b and the other motor shaft hole 140b. That is, the oil collecting protrusion 111 is closer to the bearing groove 112 than the motor shaft hole 140b, which makes it easier for the oil collecting protrusion 111 to collect part of the lubricating oil thrown out by the intermediate wheel 312a or the intermediate wheel 312b.

[0105] In one embodiment, the minimum angle between an oil collecting protrusion 111 and the ground is greater than or equal to 20 degrees and less than or equal to 35 degrees.

[0106] In this embodiment, if the minimum angle between the side of the oil collecting protrusion 111 that acts as an oil-blocking element and the ground is too small, when the vehicle 1 is going uphill or downhill, the lubricating oil will have difficulty flowing to the differential 320 after falling on this side. In some cases, the lubricating oil may even backflow onto the oil collecting protrusion 111, impairing the lubrication effect on the differential 320. If the minimum angle between the side of the oil-blocking element and the ground is too large, although it will not affect the oil collecting and guiding effect of the oil collecting protrusion 111 when the vehicle 1 is going uphill or downhill, when the vehicle 1 is traveling on level ground, it will reduce the angle between the oil collecting sections 1111a and 1111b of the oil collecting protrusion 111, thereby reducing the space in the oil collecting groove 1113 for oil collection and decreasing the amount of lubricating oil that the oil collecting protrusion 111 can collect. For example, the minimum angle between an oil collecting protrusion 111 and the ground can be any angle among 20 degrees, 22 degrees, 25 degrees, 27 degrees, 30 degrees, 32 degrees, or 35 degrees.

[0107] Please continue to refer to Figures 4 and 6. In one embodiment, an oil collecting protrusion 111 includes a flow hole 1112. The flow hole 1112 passes through one end of the oil collecting protrusion 111. The distance between the center of the flow hole 1112 and the center of a differential shaft hole 130 is less than the distance between the other end of the oil collecting protrusion 111 and the center of a differential shaft hole 130.

[0108] In this embodiment, along the radial direction R of the dual-motor powertrain 10, the flow hole 1112 penetrates one end of the oil collecting protrusion 111. The distance between the flow hole 1112 and the differential shaft hole 130 is less than the distance between the other end of the oil collecting protrusion 111 and the differential shaft hole 130. This causes the lubricating oil collected by the oil collecting protrusion 111 to tend to move to the flow hole 1112 first, and then be guided to the differential 320, improving the accuracy of oil guiding and achieving directional lubrication of the differential 320. If the oil collecting protrusion 111 does not include the flow hole 1112, the lubricating oil may flow out before reaching one end of the oil collecting protrusion 111, making it impossible to ensure that the lubricating oil collected by the oil collecting protrusion 111 can flow directly into the differential 320, which is not conducive to improving the lubrication effect on the differential 320.

[0109] In this embodiment, the two ends of the oil collecting protrusion 111 cooperate with the flow hole 1112 to achieve simultaneous oil collection and guidance, reducing the accumulation of lubricating oil in the oil collecting protrusion 111 and ensuring that the oil collecting protrusion 111 has sufficient space for collecting lubricating oil. If the oil collecting protrusion 111 does not include the flow hole 1112, the lubricating oil may need to accumulate to a certain extent before overflowing from the oil collecting protrusion 111, thereby reducing the efficiency of oil collection and guidance.

[0110] Please refer to Figures 9 and 10. Figure 9 is a partial exploded view of the dual-motor powertrain 10 provided in an embodiment of this application, and Figure 10 is a partial enlarged view of the M2 portion of the dual-motor powertrain 10 shown in Figure 9. In one embodiment, a differential 320 includes a planetary shaft 321 and a differential gear set 322. The planetary shaft 321 is used for transmission connection with the differential gear set 322. A flow passage 1112 is at least partially aligned with a planetary shaft 321 along the radial direction R of the dual-motor powertrain 10. The inner diameter of the flow passage 1112 is less than or equal to the outer diameter of the planetary shaft 321. The flow passage 1112 is used to guide lubricating oil to the planetary shaft 321, and the planetary shaft 321 is used to throw lubricating oil to the differential gear set 322.

[0111] In this embodiment, the planetary shaft 321 of the differential 320 is used for transmission connection with the differential gear set 322. Exemplarily, in one embodiment, the differential gear set 322 includes planetary gears and half-shaft gears. The planetary gears are fitted onto the planetary shaft 321 and mesh with the half-shaft gears, while the half-shaft gears are fitted onto the wheel drive shaft 50. The planetary gears and half-shaft gears surround the circumference of the planetary shaft 321. The output wheel 314 transmits power to the planetary shaft 321 and the planetary gears. The rotation of the planetary gears drives the half-shaft gears to rotate, which in turn drives the wheel 40 to rotate via the wheel drive shaft 50.

[0112] In this embodiment, a flow orifice 1112 along the radial direction R of the dual-motor powertrain 10 is at least partially aligned with a planetary shaft 321. This means that the projection of the flow orifice 1112 along the radial direction R of the dual-motor powertrain 10 at least partially overlaps with the projection of the planetary shaft 321, so that the oil collecting protrusion 111 can guide the collected lubricating oil to the planetary shaft 321. The inner diameter of the flow orifice 1112 is less than or equal to the outer diameter of the planetary shaft 321, improving the accuracy of the flow orifice 1112 in guiding the lubricating oil to the planetary shaft 321. In one embodiment, a differential housing 323 includes a window 3231 extending through the differential housing 323, a planetary shaft 321 exposed to the window 3231, and an oil collection protrusion 111 at least partially aligned with the window 3231 along the radial direction R of the dual-motor powertrain 10, the oil collection protrusion 111 being used to guide lubricating oil through the window 3231 to the planetary shaft 321.

[0113] In this embodiment, the planetary shaft 321 is connected to the differential gear set 322. When the planetary shaft 321 rotates, lubricating oil is thrown onto the differential gear set 322 by the planetary shaft 321, thereby lubricating the differential gear set 322. This embodiment uses the planetary shaft 321 as an intermediate medium for lubricating the differential gear set 322. By guiding the lubricating oil to the planetary shaft 321, the rotation of the planetary shaft 321 expands the coverage of the lubricating oil, achieving a redistribution of the lubricating oil within the differential housing 323. If the oil collecting protrusion 111 directly guides the lubricating oil to a single gear in the differential 320, although the lubricating oil has a better lubricating effect on that single gear, the coverage of the lubricating oil is limited to that single gear and its adjacent gears, which may lead to insufficient lubrication of certain gears in the differential 320.

[0114] Please refer to Figures 6 and 10. In one embodiment, the oil collecting protrusion 111 forms an oil collecting groove 1113 with the cavity wall of the reducer chamber 110, with the opening of the oil collecting groove 1113 facing an intermediate wheel or an output wheel along the axial direction O of the dual-motor powertrain 10. The distance between a flow passage 1112 and a differential housing 323 along the radial direction R of the dual-motor powertrain 10 is less than the distance between the bottom of the oil collecting groove 1113 and the differential housing 323 of the differential 320. The differential housing 323 is fixed to an output wheel 314 and accommodates a planetary shaft 321 and a differential gear set 322.

[0115] In this embodiment, the bottom and opening of the oil collection groove 1113 along the axial direction of the dual-motor powertrain 10 are opposite each other, and the bottom of the oil collection groove 1113 is part of the cavity wall of the reducer cavity 110. The flow hole 1112 is closer to the differential housing 323 than the bottom of the oil collection groove 1113, so that the lubricating oil at the bottom of the oil collection groove 1113 tends to flow towards the flow hole 1112, avoiding excessive lubricating oil accumulation at the bottom of the oil collection groove 1113 and improving the utilization rate of lubricating oil.

[0116] In one embodiment, the distance between a flow passage 1112 and a differential housing 323 along the radial direction R of the dual-motor powertrain 10 is equal to the distance between the bottom of an oil collection groove 1113 and a differential housing 323. This embodiment of the application can reduce the processing difficulty and cost of the oil collection groove 1113 without increasing the lubricating oil flow resistance.

[0117] Please refer to Figures 6 and 10. In one embodiment, along the axial direction O of the dual-motor powertrain 10, a flow passage 1112 is adjacent to and communicates with the opening of an oil collection groove 1113.

[0118] In this embodiment, the axial flow hole 1112 and the groove of the oil collection groove 1113 along the dual motor power assembly 10 are both located at one end of the oil collection protrusion 111 facing the parallel shaft gear set 310. The connection between the flow hole 1112 and the groove of the oil collection groove 1113 is beneficial to accelerating the output of lubricating oil.

[0119] In one embodiment, along the axial direction O of the dual-motor powertrain 10, a flow passage 1112 is spaced apart from the slot of an oil collection groove 1113, and along the radial direction R of the dual-motor powertrain 10, the distance between the slot of an oil collection groove 1113 and a differential housing 323 is less than the distance between a flow passage 1112 and a differential housing 323.

[0120] In this embodiment, although the flow passage 1112 along the axial direction of the dual-motor powertrain 10 is spaced apart from the opening of the oil collection groove 1113, the flow passage 1112 is closer to the differential housing 323 than the opening of the oil collection groove 1113. This allows some of the lubricating oil flowing to the opening of the oil collection groove 1113 to flow back to the flow passage 1112, thereby providing directional lubrication for the differential 320. In one embodiment, the flow passage 1112 is closer to the differential housing 323 than both the opening and bottom of the oil collection groove 1113. This embodiment helps to reduce the accumulation of lubricating oil in the oil collection groove 1113.

[0121] Please refer to Figures 4 and 11. Figure 11 is a partial structural schematic diagram of the dual-motor powertrain 10 provided in an embodiment of this application. To clearly show the positional relationship between the oil collecting protrusion 111 and the nozzle 600, Figure 11 omits the structures in the dual-motor powertrain other than the oil collecting protrusion 111 and the nozzle 600.

[0122] In one embodiment, as shown in FIG4, the cavity wall of a reducer cavity 110 further includes an oil injection hole 113. Referring to FIGS. 4 and 11, the oil injection hole 113 is used to fix a nozzle 600, and the nozzle 600 is used to spray lubricating oil onto an oil collecting protrusion 111. The oil injection hole 113 is arranged between an oil collecting protrusion 111 and another motor shaft hole 140, and the distance between the center of the oil injection hole 113 and the oil collecting protrusion 111 is less than the distance between the center of the oil injection hole 113 and the center of the other motor shaft hole 140.

[0123] In this embodiment, the spray nozzle 113 is used to spray lubricating oil onto the oil collecting protrusion 111 via the nozzle 600. The spray nozzle 113 is closer to the oil collecting protrusion 111 than the center of the motor shaft hole 140, which helps reduce the difficulty of spraying lubricating oil onto the oil collecting protrusion 111. The oil collecting protrusion 111 collects the lubricating oil sprayed by the nozzle 600, which is an active oil collecting method. Compared to passive oil collecting, active oil collecting is less affected by the rotational speed of the motor 200. The nozzle 600 can actively spray oil onto the oil collecting protrusion 111 under both high-speed and low-speed operating conditions of the motor 200. Exemplarily, in one embodiment, the dual-motor powertrain 10 also includes an oil pump, which is connected to the spray nozzle 113, and the power for the nozzle 600 to spray lubricating oil comes from the oil pump.

[0124] Please continue to refer to Figure 11. In one embodiment, along the axial direction O of the dual-motor powertrain 10, the distance between a nozzle 600 and the bottom of an oil collection tank 1113 is less than the distance between a flow passage 1112 and the bottom of an oil collection tank 1113.

[0125] In this embodiment, the nozzle 600 is closer to the bottom of the oil collection groove 1113 than the flow hole 1112, that is, the nozzle 600 extends into the oil collection groove 1113, which can improve the accuracy of the nozzle 600 spraying lubricating oil onto the oil collection protrusion 111 and improve the efficiency of the oil collection protrusion 111 in actively collecting oil.

[0126] In one embodiment, the oil collecting protrusion 111 is integrally die-cast into the assembly housing 100.

[0127] In one embodiment, the oil collecting protrusion 111 and the assembly housing 100 are separate structures, and the oil collecting protrusion 111 is fixedly connected to the assembly housing 100 by welding, gluing or other means.

[0128] The foregoing has provided a detailed description of the dual-motor powertrain and vehicle with an oil-lubricated differential provided in the embodiments of this application. Specific examples have been used to illustrate the principles and embodiments of this application. The descriptions of the embodiments above are merely for the purpose of helping to understand the method and core ideas of this application. Furthermore, those skilled in the art will recognize that, based on the ideas of this application, there will be changes in specific embodiments and application scope. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A dual motor powertrain incorporating an oil-collecting lubricated differential, characterized by, The dual-motor power assembly comprises two motors and one reducer, an assembly housing of the dual-motor power assembly is used to form one reducer cavity and two motors cavities arranged in parallel, the two motors cavities are used to fix stators of the two motors respectively, the one reducer cavity is used to accommodate one parallel shaft gear set and one differential of the one reducer, wherein: The assembly housing comprises one differential shaft hole and two motor shaft holes, the one differential shaft hole is used to pass through one wheel drive shaft, one of the motor shaft holes is used to connect one of the motor cavities and the one reducer cavity, the other of the motor shaft holes is used to connect the other of the motor cavities and the one reducer cavity; A cavity wall of the one reducer cavity comprises one bearing groove and one oil collecting protrusion, the one bearing groove is used to fix a bearing of an intermediate shaft of the one parallel shaft gear set, the one oil collecting protrusion is used to collect lubricating oil and guide the one differential, a distance between a center of the one bearing groove and a center of the other motor shaft hole is greater than a distance between a center of at least one of the one motor shaft hole or the one differential shaft hole and the center of the other motor shaft hole, the one oil collecting protrusion is arranged between one intermediate wheel or one output wheel of the one parallel shaft gear set and the cavity wall of the one reducer cavity.

2. The dual-motor powertrain of claim 1, wherein, In an axial direction of the dual-motor power assembly, the one motor shaft hole is used to align with one input wheel of the one parallel shaft gear set, the one input wheel is used to mesh with the one intermediate wheel, in the axial direction of the dual-motor power assembly, the one differential shaft hole is used to align with the one differential, wherein: A distance between a center of the one motor shaft hole and a center of the one differential shaft hole is less than the distance between the center of at least one of the one motor shaft hole or the one differential shaft hole and the center of the other motor shaft hole, in a radial direction of the dual-motor power assembly, the one oil collecting protrusion is arranged between the one motor shaft hole and the one differential shaft hole.

3. The dual-motor powertrain of claim 2, wherein, A distance between the one oil collecting protrusion and the center of the one differential shaft hole is less than a distance between the one oil collecting protrusion and the center of the one motor shaft hole.

4. The dual-motor powertrain of claim 3, wherein, A cavity wall of the one motor cavity comprises one oil return hole, the one oil return hole is used to connect the one motor cavity and the one reducer cavity, wherein: In the radial direction of the dual-motor power assembly, the one oil return hole is arranged between the one motor shaft hole and the one oil collecting protrusion, a distance between a center of the one oil return hole and the one oil collecting protrusion is less than a distance between the center of the one oil return hole and the center of the one motor shaft hole.

5. The dual-motor powertrain of claim 1, wherein, The other intermediate wheel of the one parallel shaft gear set is used to mesh with the one output wheel, in the axial direction of the dual-motor power assembly, the one bearing groove is used to align with the one intermediate wheel and the other intermediate wheel, wherein: A distance between the one oil collecting protrusion and a center of the one bearing groove is less than a distance between the one oil collecting protrusion and a center of any one of the one motor shaft hole or the one differential shaft hole.

6. The dual electric motor powertrain of claim 1, wherein, The one oil collection protrusion is closer to the one intermediate wheel than the one differential axle hole along an axial direction of the dual-motor power assembly.

7. The dual electric motor powertrain of claim 1, wherein, The one oil collection protrusion is closer to the one output wheel than the one differential axle hole along an axial direction of the dual-motor power assembly.

8. The dual electric motor powertrain of any one of claims 1-7, wherein, The one oil collection protrusion comprises two oil collection sections, one end of one oil collection section intersects with one end of another oil collection section, another end of the one oil collection section is spaced apart from another end of the another oil collection section, an opening of an included angle between the one oil collection section and the another oil collection section along a radial direction of the dual-motor power assembly faces the one motor axle hole and is away from the one differential axle hole.

9. The dual electric motor powertrain of claim 8, wherein, The another end of the one oil collection section is closer to the center of the one bearing groove than the another end of the another oil collection section is to the center of the another motor axle hole.

10. The dual electric motor powertrain of any one of claims 1-7, wherein, The one oil collection protrusion comprises one through hole, the one through hole penetrates one end of the one oil collection protrusion, a center of the one through hole is closer to the center of the one differential axle hole than another end of the one oil collection protrusion is to the center of the one differential axle hole.

11. The dual electric motor powertrain of claim 10, wherein, The one differential comprises one planetary axle and one differential gear set, the one planetary axle is used to be in driving connection with the one differential gear set, wherein: The one through hole is at least partially aligned with the one planetary axle along a radial direction of the dual-motor power assembly, an inner diameter of the one through hole is less than or equal to an outer diameter of the one planetary axle, the one through hole is used to guide lubricating oil to the one planetary axle, the one planetary axle is used to throw the lubricating oil to the one differential gear set.

12. The dual electric motor powertrain of any one of claims 1-7, wherein, The cavity wall of the one reducer cavity further comprises one oil injection hole, the one oil injection hole is used to fix one nozzle, the one nozzle is used to spray lubricating oil to the one oil collection protrusion, wherein: The one oil injection hole is arranged between the one oil collection protrusion and the another motor axle hole, a center of the one oil injection hole is closer to the one oil collection protrusion than the center of the one oil injection hole is to the center of the another motor axle hole.

13. A vehicle characterized by comprising: The vehicle comprises a frame and the dual-motor power assembly according to any one of claims 1-12, the frame is used to mount the dual-motor power assembly, the one differential of the dual-motor power assembly is used to drive wheels of the vehicle, the one oil collection protrusion is higher than the one differential along a direction of gravity.

14. The vehicle of claim 13, wherein, The minimum included angle between the one oil collection protrusion and the ground is greater than or equal to 20 degrees and less than or equal to 35 degrees.

Images