Drive assembly and vehicle

Abstract

A drive assembly and a vehicle. The drive assembly comprises a reduction gearbox, an oil guide structure and a structure to be lubricated. The oil guide structure is connected between the reduction gearbox and the structure to be lubricated.

Description

Drive assembly and vehicle

[0001] This application claims priority to Chinese Patent Application No. 202411233657.2, filed on September 3, 2024, the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0002] The present disclosure relates to the technical field of vehicles, and in particular, to a drive assembly and a vehicle. BACKGROUND

[0003] The mainstream new energy vehicles on the market at present include pure electric vehicles, hybrid electric vehicles and extended range electric vehicles. Pure electric vehicles have a growing share in the automotive field due to their environmental protection, low noise and low use cost.

[0004] With the continuous development of new energy vehicles, the requirements for the safety, power, energy consumption, noise and other related performance of vehicles are becoming higher and higher. In order to enable vehicles to adapt to various complex road conditions, the electric drive assembly of the vehicle needs to have the technical characteristics of high power, high torque, high speed and high efficiency, and higher requirements are put forward for the lubrication and cooling of the electric drive assembly. SUMMARY

[0005] The present disclosure provides a drive assembly and a vehicle to solve the problem that the gear oil throwing structure of the related art cannot meet the oil amount requirements of each lubrication structure in the electric drive assembly when the motor rotates at high speed.

[0006] In a first aspect, a drive assembly is provided, comprising a reduction gearbox, an oil guide structure and a lubrication structure; the oil guide structure is connected between the reduction gearbox and the lubrication structure.

[0007] The drive assembly of some embodiments of the present disclosure connects the oil guide structure between the reduction gearbox and the lubrication structure, so that the oil in the reduction gearbox can flow to the lubrication structure through the lubrication structure to lubricate the lubrication structure. Compared with the gear oil throwing structure in the related art, the lubrication structure of some embodiments of the present disclosure can guide the oil in the reduction gearbox into multiple lubrication structures of the drive assembly, meet the oil amount requirements of each lubrication structure in the electric drive assembly when the motor rotates at high speed, and improve the lubrication effect of each lubrication structure of the drive assembly.

[0008] In some embodiments of the present disclosure, the driving assembly further comprises a reduction assembly and a main shaft bearing, the reduction assembly is arranged in the reduction box; the reduction assembly comprises a main shaft, the reduction box is provided with a main shaft mounting hole, a part of the main shaft is accommodated in the main shaft mounting hole, and the main shaft bearing is arranged between the main shaft and the inner wall surface of the main shaft mounting hole, and the main shaft bearing forms at least part of the structure to be lubricated; the oil guide structure comprises an oil guide channel, the oil guide channel is provided with an oil inlet and a first oil outlet, the oil inlet is communicated with the reduction box, and the first oil outlet is opposite to the main shaft bearing. In this way, the oil in the reduction box can enter the oil guide channel through the oil inlet, and then flow out from the first oil outlet to the main shaft bearing, so as to realize the lubrication of the main shaft bearing.

[0009] In some embodiments of the present disclosure, the oil guide channel comprises a first oil guide channel segment, the first oil guide channel segment and the first oil outlet are arranged in the reduction box, and the first oil outlet is arranged in the first oil guide channel segment. In this way, some embodiments of the present disclosure reduce the arrangement space of the oil circuit by arranging the first oil outlet and the first oil guide channel segment on the reduction box, thereby saving valuable space for the whole vehicle design.

[0010] In some embodiments of the present disclosure, the main shaft bearing and the first oil outlet are arranged along the axial direction of the main shaft bearing, and the axial direction of the first oil outlet is consistent with the axial direction of the main shaft bearing. Since the axial direction of the first oil outlet is consistent with the axial direction of the main shaft bearing, it can be ensured that the oil flowing out of the first oil outlet flows towards the main shaft bearing, thereby improving the lubrication effect of the main shaft bearing.

[0011] In some embodiments of the present disclosure, the main shaft bearing comprises a first inner ring, a first outer ring and at least one first rolling body, the first inner ring is sleeved on the main shaft, the first outer ring is located between the first inner ring and the inner wall surface of the main shaft mounting hole, and the at least one first rolling body is arranged between the first inner ring and the first outer ring; along the radial direction of the main shaft bearing, the central axis of the first oil outlet is located between the outer wall surface of the first inner ring and the inner wall surface of the first outer ring.

[0012] Since the central axis of the first oil outlet is located between the outer wall surface of the first inner ring and the inner wall surface of the first outer ring, it can be better ensured that the oil sprayed out of the first oil outlet falls between the first outer ring and the first inner ring, so as to realize the lubrication of the first rolling body and ensure reliable and efficient lubrication of the main shaft bearing.

[0013] In some embodiments of the present disclosure, the driving assembly further comprises a first valve, which is arranged in the first oil guiding passage segment and located between the first oil injection port and the oil inlet. In this way, by controlling the opening and closing of the first valve, whether the first oil injection port is in communication with the oil inlet can be controlled, thereby controlling whether the first oil injection port flows out oil, and realizing controllable lubrication of the main shaft bearing.

[0014] In some embodiments of the present disclosure, the driving assembly further comprises a motor box and a motor bearing, the motor comprises an output shaft, the motor box is provided with an output shaft mounting hole, part of the output shaft is accommodated in the output shaft mounting hole, and the motor bearing is arranged between the output shaft and the inner wall surface of the output shaft mounting hole, and the motor bearing forms at least part of the structure to be lubricated; the oil guiding structure comprises an oil guiding passage, the oil guiding passage is provided with an oil inlet and a second oil injection port, the oil inlet is in communication with the reduction box, and the second oil injection port is opposite to the motor bearing.

[0015] In this way, the oil in the reduction box can enter the oil guiding passage through the oil inlet, and then flow out from the second oil injection port to the motor bearing, so as to realize lubrication of the motor bearing.

[0016] In some embodiments of the present disclosure, the oil guiding passage comprises a second oil guiding passage segment, the second oil guiding passage segment and the second oil injection port are arranged in the motor box, and the second oil injection port is arranged in the second oil guiding passage segment. In this way, some embodiments of the present disclosure arrange the second oil injection port and the second oil guiding passage segment on the motor box, thereby reducing the arrangement space of the oil circuit, making the structure of the driving assembly more compact, and saving space for the design of the whole vehicle.

[0017] In some embodiments of the present disclosure, the driving assembly further comprises a motor bearing seat, which is arranged in the motor box, arranged between the motor bearing and the inner wall surface of the output shaft mounting hole, and connected with the motor bearing; the motor bearing seat is provided with a first avoiding port facing the motor bearing, and the second oil injection port is arranged towards the first avoiding port. Since the first avoiding port is arranged on the motor bearing seat, and the second oil injection port is arranged towards the first avoiding port, in this way, the oil sprayed out of the second oil injection port can be sprayed into the motor bearing through the first avoiding port, so as to realize lubrication of the motor bearing.

[0018] In some embodiments of the present disclosure, the driving assembly further comprises a main shaft, a main shaft bearing and a main shaft bearing seat, all of which are arranged in the reduction box; the reduction box is provided with a main shaft mounting hole, part of the main shaft is accommodated in the main shaft mounting hole, and the main shaft bearing is arranged between the main shaft and the inner wall surface of the main shaft mounting hole, and the main shaft bearing seat is arranged between the main shaft bearing and the inner wall surface of the main shaft mounting hole; the main shaft bearing seat is provided with a second avoiding opening facing the main shaft bearing, and the first avoiding opening and the second avoiding opening are oppositely arranged; the second oil injection opening is arranged between the first avoiding opening and the second avoiding opening, and is used for injecting oil to the motor bearing seat and the main shaft bearing seat.

[0019] The second oil injection opening can be provided with two, and the two second oil injection openings can be integrally and through arranged, one of the two second oil injection openings faces the motor bearing, and the other faces the main shaft bearing.

[0020] In this way, the oil injected by the second oil injection opening can flow into the first avoiding opening and the second avoiding opening respectively, and be sprayed to the motor bearing and the main shaft bearing through the first avoiding opening and the second avoiding opening respectively, so that the motor bearing and the main shaft bearing can be simultaneously lubricated.

[0021] In some embodiments of the present disclosure, the main shaft bearing comprises a first inner ring and a first outer ring, the first inner ring is sleeved on the main shaft, and the first outer ring is located between the first inner ring and the inner wall surface of the main shaft mounting hole; the motor bearing comprises a second inner ring and a second outer ring, the second inner ring is sleeved on the motor output shaft, and the second outer ring is located between the second inner ring and the inner wall surface of the output shaft mounting hole; along the radial direction of the main shaft bearing, the central axis of the second oil injection opening is located between the outer wall surface of the first inner ring and the inner wall surface of the second outer ring. In this way, it can be ensured that the oil injected from the second oil injection opening is located between the outer wall surface of the first inner ring and the inner wall surface of the second outer ring, so as to effectively lubricate the main shaft bearing and the motor bearing, and improve the lubrication effect of the main shaft bearing and the motor bearing.

[0022] In some embodiments of the present disclosure, a filler is arranged between the main shaft bearing seat and the motor bearing seat, the horizontal height of the filler gradually increases along a first direction, and the first direction is from the motor bearing to the reduction gear bearing; the side of the filler close to the motor bearing is flush with the second inner ring, and the side of the filler close to the main shaft bearing is flush with the first inner ring. In this way, it can be prevented that the injected lubricating oil flows into the gap between the main shaft bearing seat and the motor bearing seat, causing waste of lubricating oil and affecting the lubrication effect of the motor bearing and the main shaft bearing.

[0023] In some embodiments of the present disclosure, the motor case and the reduction case are integrated. In this way, the motor case and the reduction case are integrated, which is conducive to the miniaturization of the drive assembly and saves space for the overall vehicle design.

[0024] In some embodiments of the present disclosure, the drive assembly further comprises a second valve, which is arranged in the second oil guide passage section and located between the second oil injection port and the oil inlet. In this way, by controlling the opening and closing of the second valve, whether the second oil injection port and the oil inlet are in communication can be controlled, thereby controlling whether the second oil injection port flows out of oil, and realizing controllable lubrication of the main shaft bearing and the motor bearing.

[0025] In some embodiments of the present disclosure, the drive assembly further comprises a main shaft, a secondary shaft, a differential shaft and an oil guide arranged in the reduction case, the main shaft and the secondary shaft are in transmission connection, the secondary shaft is arranged between the main shaft and the differential shaft and in transmission connection with the differential shaft; the secondary shaft is provided with a secondary shaft gear, and the differential shaft is provided with a differential gear; the oil guide is arranged between the differential shaft and the main shaft, and comprises a first oil guide part, which is configured to, when the differential gear and the secondary shaft gear operate to splash oil, splash part of the oil onto the first oil guide part and transfer the oil to the main shaft through the first oil guide part.

[0026] In this way, when the differential gear and the secondary shaft gear operate to splash oil in the reduction case, part of the oil can be splashed onto the first oil guide part and transferred to the main shaft through the first oil guide part. In this way, splashing lubrication of the main shaft is realized, which is conducive to improving the lubrication effect of the main shaft.

[0027] In some embodiments of the present disclosure, the oil guide part further comprises a second oil guide part; the second oil guide part is used to, when the differential gear and the secondary shaft gear operate to splash oil, splash part of the oil onto the second oil guide part and transfer the oil to the secondary shaft through the second oil guide part. In this way, when the differential gear and the secondary shaft gear operate to splash oil in the reduction case, part of the oil can be splashed onto the second oil guide part and transferred to the secondary shaft through the second oil guide part. In this way, splashing lubrication of the secondary shaft is realized, which is conducive to improving the lubrication effect of the secondary shaft.

[0028] In some embodiments of the present disclosure, the oil guide portion further comprises a third oil guide portion; the third oil guide portion is configured to guide part of the oil splashed by the differential gear and the pinion gear to the differential shaft when the differential gear and the pinion gear are in operation. In this way, when the differential gear and the pinion gear are in operation, part of the oil splashed in the reduction gearbox can be guided to the third oil guide portion and then to the differential shaft through the third oil guide portion. In this way, the splashing lubrication of the differential shaft is realized, which is conducive to improving the lubrication effect of the differential shaft.

[0029] In some embodiments of the present disclosure, the oil guide structure comprises an oil guide channel provided with an oil inlet and an oil outlet; the oil inlet is in communication with the reduction gearbox; the drive assembly further comprises an oil pump and an oil cooler arranged in the oil guide channel in sequence; the oil outlet is in communication with the oil cooler; and the oil outlet is opposite to the structure to be lubricated. In this way, the oil in the reduction gearbox can be pumped out from the oil inlet by the oil pump and then flow into the oil cooler through the oil guide channel and the oil pump, and then flow into the structure to be lubricated after being cooled by the oil cooler, so as to ensure that the temperature of the oil is low and the cooling of some components can be realized.

[0030] In some embodiments of the present disclosure, the oil cooler is provided with a heat exchange pipeline; the drive assembly further comprises a bypass pipeline and a multi-way valve; the multi-way valve comprises a first inlet, a first outlet and a second outlet; the first inlet is in communication with the first outlet and the second outlet; the first inlet is in communication with the oil outlet of the oil pump; the first outlet is in communication with one end of the heat exchange pipeline; the second outlet is in communication with one end of the bypass pipeline; and the other ends of the heat exchange pipeline and the bypass pipeline are in communication with the oil outlet of the oil cooler.

[0031] In this way, when the oil temperature of the drive assembly does not reach the heat exchange threshold, the first inlet is in communication with the second outlet, the oil enters through the first inlet, and then directly flows into the oil outlet of the oil cooler through the second outlet and the bypass pipeline, so as to reduce the flow resistance of the oil circuit and reduce the power of the oil pump. When the oil temperature of the drive assembly reaches the heat exchange threshold, the first inlet is in communication with the first outlet, the oil enters through the first inlet, and then flows into the heat exchange pipeline of the oil cooler through the first outlet, so as to realize the heat exchange and cooling of the oil.

[0032] In some embodiments of the present disclosure, the driving assembly comprises a motor and a motor box, the motor is arranged in the motor box; the motor comprises a stator and a rotor, the stator and the rotor are coaxially arranged, and the stator is nested outside the rotor; the oil guide structure comprises an oil guide channel, the oil guide channel is provided with an oil inlet and an oil outlet, and the oil inlet is communicated with the reduction box; the oil guide structure further comprises a rotor heat exchange oil channel, the rotor heat exchange oil channel is communicated with the oil outlet; the rotor heat exchange oil channel is configured to exchange heat with the rotor to carry away the heat of the rotor. In this way, the oil in the reduction box can flow into the oil guide channel through the oil inlet and flow into the rotor heat exchange oil channel through the oil outlet to exchange heat with the rotor to carry away the heat of the rotor, thereby achieving cooling of the rotor.

[0033] In some embodiments of the present disclosure, the oil guide channel comprises a third oil guide channel segment, the third oil guide channel segment and the oil outlet are arranged in the motor box, and the oil outlet is arranged in the third oil guide channel segment. In this way, the third oil guide channel and the oil outlet are integrated on the motor box, which reduces the space occupied by the connecting pipeline and facilitates the miniaturization of the driving assembly.

[0034] In some embodiments of the present disclosure, the driving assembly further comprises a third valve, the third valve is arranged in the third oil guide channel segment, and the third valve is located between the oil outlet and the oil inlet. In this way, by controlling the opening and closing of the third valve, whether the oil outlet and the oil inlet are communicated can be controlled, thereby controlling whether the oil outlet flows out of oil, and achieving controllable cooling of the rotor and the stator.

[0035] In some embodiments of the present disclosure, the oil guide structure further comprises a stator heat exchange oil channel, the stator heat exchange oil channel is communicated with the oil outlet, and the stator heat exchange oil channel is used to exchange heat with the stator to carry away the heat of the stator.

[0036] In some embodiments of the present disclosure, the stator comprises a stator core and a first winding end and a second winding end arranged at two ends of the stator core; the stator heat exchange oil channel comprises a first winding end heat exchange oil channel, the first winding end heat exchange oil channel is provided with a third oil injection port, and the third oil injection port is arranged towards the first winding end; the second winding end heat exchange oil channel is provided with a fourth oil injection port, and the fourth oil injection port is arranged towards the second winding end.

[0037] In some embodiments of the present disclosure, the first winding end heat exchange oil channel and the second winding end heat exchange oil channel are annular and coaxially arranged with the stator core; the first winding end heat exchange oil channel is provided with a plurality of third oil injection ports around the central axis, and the second winding end heat exchange oil channel is provided with a plurality of fourth oil injection ports around the central axis.

[0038] In some embodiments of the present disclosure, the plurality of third oil injection ports are evenly spaced around the central axis of the first winding end heat exchange oil channel; and the plurality of fourth oil injection ports are evenly spaced around the central axis of the first winding end heat exchange oil channel.

[0039] In some embodiments of the present disclosure, the third oil injection port comprises a plurality of first sub-oil injection ports and a plurality of second sub-oil injection ports; the plurality of first sub-oil injection ports are evenly spaced around the central axis of the first winding end heat exchange oil channel; and the plurality of second sub-oil injection ports are also evenly spaced around the central axis of the first winding end heat exchange oil channel, and the plurality of second sub-oil injection ports surround the outer circle of the plurality of first sub-oil injection ports.

[0040] In some embodiments of the present disclosure, the extension line of the first sub-oil injection port intersects with the extension line of the second sub-oil injection port.

[0041] In some embodiments of the present disclosure, the stator heat exchange oil channel further comprises a stator core heat exchange oil channel, at least part of the stator core heat exchange oil channel is arranged in the stator core, and the stator core heat exchange oil channel is arranged along the radial direction of the stator core.

[0042] In some embodiments of the present disclosure, the stator core heat exchange oil channel is provided in plurality, and the plurality of stator core heat exchange oil channels are evenly spaced along the axial direction of the stator core.

[0043] In some embodiments of the present disclosure, the stator core heat exchange oil channel is provided in plurality, and the plurality of stator core heat exchange oil channels are evenly spaced along the axial direction of the stator core, and any one of the plurality of stator core heat exchange oil channels comprises a plurality of stator core heat exchange oil channels evenly spaced along the radial direction of the stator core.

[0044] In some embodiments of the present disclosure, the drive assembly further comprises an oil sump and a reduction assembly; the oil sump is arranged in the reduction box, an oil storage space is formed in the oil sump, the reduction assembly is arranged in the reduction box, at least part of the reduction assembly is located in the oil storage space, the bottom wall of the oil sump is provided with at least one through hole; the at least part of the reduction assembly forms at least part of the structure to be lubricated; and the at least one through hole forms at least part of the oil guide structure.

[0045] In some embodiments of the present disclosure, the reduction assembly comprises a differential gear, a first auxiliary shaft driven gear and a second auxiliary shaft driven gear; the differential gear is engaged with the first auxiliary shaft driven gear, and the first auxiliary shaft driven gear is coaxially connected with the second auxiliary shaft driven gear.

[0046] The oil sump comprises a first oil sump and a second oil sump, both of which are arranged in the reduction gearbox; the bottom of the first oil sump is formed with a first oil storage space, and the bottom of the first oil sump is provided with a first through hole; the differential gear is arranged in the reduction gearbox and located in the first oil storage space; the bottom of the second oil sump is formed with a second oil storage space, and the bottom of the second oil sump is provided with a second through hole; the second countershaft driven gear is arranged in the reduction gearbox and located in the second oil storage space.

[0047] In some embodiments of the present disclosure, the first oil sump comprises a first partition plate, a second partition plate and a first bottom plate, the first partition plate and the second partition plate are arranged at intervals; the first bottom plate is connected with the first partition plate and the second partition plate, the first bottom plate is arranged around the circumference of the differential gear, and the first oil storage space is arranged between the first partition plate, the second partition plate and the first bottom plate; the first through hole is arranged on the first bottom plate.

[0048] In some embodiments of the present disclosure, the second oil sump comprises a third partition plate, a fourth partition plate and a second bottom plate, the third partition plate and the fourth partition plate are arranged at intervals; the second bottom plate is connected with the third partition plate and the fourth partition plate, the second bottom plate is arranged around the circumference of the second countershaft driven gear, and the second oil storage space is arranged between the third partition plate, the fourth partition plate and the second bottom plate; the second through hole is arranged on the second bottom plate.

[0049] In some embodiments of the present disclosure, the first partition plate, the first bottom plate and the fourth partition plate are an integral structure, and the second partition plate, the second bottom plate and the third partition plate are an integral structure.

[0050] In some embodiments of the present disclosure, the first partition plate, the first bottom plate and the fourth partition plate constitute a front box oil sump; the second partition plate, the second bottom plate and the third partition plate constitute a rear box oil sump; the reduction gearbox comprises a front box and a rear box, the rear box is located on the side of the front box away from the motor; the front box oil sump is connected with the front box, and the rear box oil sump is connected with the rear box.

[0051] In some embodiments of the present disclosure, the second partition plate and the fourth partition plate are located in the same plane, and the first partition plate is located on the side of the second partition plate away from the third partition plate along the axial direction of the differential gear.

[0052] In some embodiments of the present disclosure, the driving assembly further comprises a differential housing and a differential assembly arranged in the differential housing, the differential housing is coaxially connected with the differential gear, and the differential housing is located on the side of the differential gear away from the rear box; a circumferential wall surface of the differential housing is provided with at least one second inlet communicated with the differential assembly, and a second bottom plate is provided with an oil guide hole between the second oil storage space and the second inlet and communicated with the second oil storage space, so that the oil in the second oil storage space is stirred by the second pinion gear and flows into the second inlet through the oil guide hole.

[0053] In some embodiments of the present disclosure, the oil guide hole is arranged towards a first rotation center point, and the first rotation center point is a rotation center point of the second inlet on the differential housing.

[0054] In some embodiments of the present disclosure, an accommodation space is defined in the differential housing.

[0055] The differential assembly is arranged in the accommodation space, and the differential assembly comprises a first planetary shaft, a first planetary gear, a first gasket and a half shaft gear, the first planetary shaft is fixed on the differential housing to rotate synchronously with the differential housing; the first planetary gear is arranged on the first planetary shaft and is rotatable relative to the first planetary shaft, the first gasket is arranged on the first planetary shaft and located between the first planetary gear and the differential housing, a surface of the first gasket facing the first planetary gear is provided with a first oil inlet hole; and the half shaft gear is arranged in the accommodation space and engaged with the first planetary gear.

[0056] In some embodiments of the present disclosure, a first limiting portion is arranged on a circumferential wall surface of the first planetary shaft, and an inner ring of the first gasket is matched with the first limiting portion to limit the circumferential rotation of the first gasket around the first planetary shaft.

[0057] In some embodiments of the present disclosure, a first elastic pin hole is arranged on the differential housing, and a second elastic pin hole is arranged on the first planetary shaft; the differential assembly further comprises a first elastic pin matched with the second elastic pin hole and the first elastic pin hole to fix the first planetary shaft.

[0058] In some embodiments of the present disclosure, the differential assembly further comprises a retainer arranged on the side of the first gasket away from the first planetary gear, the retainer is provided with a through hole, and the first limiting portion of the first planetary shaft is at least partially located in the through hole; the first limiting portion is matched with the through hole to limit the rotation of the first planetary shaft around the axis direction thereof.

[0059] In some embodiments of the present disclosure, the differential assembly further comprises a second planetary shaft, a second planetary gear and a second spacer, the second planetary shaft is arranged perpendicularly to the first planetary shaft, and the second planetary shaft is also fixed on the differential housing to rotate synchronously with the differential housing; the second spacer is sleeved on the second planetary shaft and located between the second planetary gear and the differential housing, and a second oil inlet hole is arranged on a surface of the second spacer facing the second planetary gear.

[0060] In some embodiments of the present disclosure, a second limiting portion is arranged on a circumferential wall surface of the second planetary shaft, and an inner ring of the second spacer is matched with the second limiting portion to limit circumferential rotation of the second spacer around the second planetary shaft.

[0061] In some embodiments of the present disclosure, the differential assembly further comprises a retainer, the retainer is arranged on a side of the second spacer away from the second planetary gear, a connecting hole is arranged on the retainer, and the second limiting portion of the second planetary shaft is at least partially located in the connecting hole; the second limiting portion is matched with the connecting hole to limit rotation of the second planetary shaft around an axial direction thereof.

[0062] In some embodiments of the present disclosure, the drive assembly further comprises an oil pan and an oil suction pipe, a space for storing oil is formed in the oil pan, and the oil suction pipe is arranged on the oil pan; an oil suction port is arranged on the oil suction pipe, and oil in the reduction gearbox is drawn into the oil suction pipe and then flows into the oil guide structure.

[0063] In some embodiments of the present disclosure, the oil suction port comprises a first oil suction port and a second oil suction port, the first oil suction port is arranged perpendicularly to a bottom wall in the reduction gearbox, and an included angle between the first oil suction port and the second oil suction port is greater than or equal to 73.5° and less than or equal to 147°.

[0064] In some embodiments of the present disclosure, the first oil suction port and the second oil suction port are both arranged close to the bottom wall in the reduction gearbox.

[0065] In some embodiments of the present disclosure, a concave oil storage groove is arranged on the bottom wall of the reduction gearbox, and the concave oil storage groove is arranged directly below the oil suction port.

[0066] In some embodiments of the present disclosure, the concave oil storage groove comprises a first concave oil storage groove and a second concave oil storage groove, the first concave oil storage groove is arranged directly below the first oil suction port, and the second concave oil storage groove is arranged directly below the second oil suction port.

[0067] In some embodiments of the present disclosure, the drive assembly further comprises a suction filter, and the suction filter is arranged in the oil suction pipe.

[0068] In some embodiments of the present disclosure, the drive assembly further comprises a fine filter, which is arranged on the oil guide channel and between the oil pump and the oil cooler.

[0069] In some embodiments of the present disclosure, the reduction gearbox is provided with a fine filter accommodating cavity, and is further provided with an opening, which is in communication with the fine filter accommodating cavity.

[0070] The fine filter comprises a fine filter element and a cover, the fine filter element is connected with the cover, the fine filter element is arranged in the fine filter accommodating cavity, and the cover is used for plugging the opening; the cover is provided with an oil inlet and an oil outlet, the oil inlet is in communication with the oil pump, and the oil outlet is in communication with the oil cooler.

[0071] In some embodiments of the present disclosure, the fine filter further comprises a sealing ring, which is arranged between the cover and the wall surface surrounding the opening.

[0072] In some embodiments of the present disclosure, the drive assembly further comprises a motor; the reduction gearbox comprises a front gearbox and a rear gearbox, the rear gearbox is located on the side of the front gearbox away from the motor; the oil cooler, the oil pump and the fine filter accommodating cavity are arranged on the front gearbox.

[0073] In some embodiments of the present disclosure, the oil guide channel comprises an integrated oil pipe, which sequentially connects the oil pump, the fine filter and the oil cooler.

[0074] In some embodiments of the present disclosure, the drive assembly comprises a motor; the reduction gearbox comprises a front gearbox and a rear gearbox, the rear gearbox is located on the side of the front gearbox away from the motor; the multi-way valve is arranged on the front gearbox.

[0075] In some embodiments of the present disclosure, a plurality of suspension holes are arranged on the front gearbox and the rear gearbox, and the plurality of suspension holes are used for connecting with different types of suspensions.

[0076] The second aspect of the present disclosure provides a vehicle, which comprises the drive assembly described in the first aspect.

[0077] It should be noted that the technical effects brought by the implementation manners of the second aspect can refer to the technical effects brought by the corresponding implementation manners of the first aspect, which will not be described herein again. BRIEF DESCRIPTION OF DRAWINGS

[0078] The accompanying drawings are used to further understand the technical solutions of the present disclosure, and constitute a part of the specification, which are used together with the embodiments of the present disclosure to explain the technical solutions of the present disclosure, and do not constitute a limitation on the disclosed technical solutions.

[0079] FIG. 1 is a schematic view of a vehicle according to some embodiments of the present disclosure;

[0080] FIG. 2 is a structural view of a drive assembly according to some embodiments of the present disclosure;

[0081] FIG. 3 is another structural view of a drive assembly according to some embodiments of the present disclosure;

[0082] FIG. 4 is an exploded view of a partial structure of the drive assembly in FIG. 2;

[0083] FIG. 5 is a partial structural view of the drive assembly in FIG. 2;

[0084] FIG. 6 is another sectional view of a partial structure of the drive assembly in FIG. 2;

[0085] FIG. 7 is yet another sectional view of a partial structure of the drive assembly in FIG. 2;

[0086] FIG. 8 is yet another sectional view of a partial structure of the drive assembly in FIG. 2;

[0087] FIG. 9 is a schematic view of splash lubrication of a rear case according to some embodiments of the present disclosure;

[0088] FIG. 10 is a schematic view of splash lubrication of a front case according to some embodiments of the present disclosure;

[0089] FIG. 11 is another partial structural view of the drive assembly in FIG. 2;

[0090] FIG. 12 is yet another sectional view of a partial structure of the drive assembly in FIG. 2;

[0091] FIG. 13 is yet another sectional view of a partial structure of the drive assembly in FIG. 2;

[0092] FIG. 14 is a schematic view of flow of oil in a drive assembly according to some embodiments of the present disclosure;

[0093] FIG. 15 is a sectional view of an oil cooler communication flow passage according to some embodiments of the present disclosure;

[0094] FIG. 16 is another sectional view of an oil cooler communication flow passage according to some embodiments of the present disclosure;

[0095] FIG. 17 is a structural view of an outer side of a front case of a reducer according to some embodiments of the present disclosure;

[0096] FIG. 18 is a side view of the outer side of the front case of the reducer in FIG. 17;

[0097] FIG. 19 is a sectional view along line AA in FIG. 18;

[0098] FIG. 20 is a structural view of an inner side of the front case of the reducer according to some embodiments of the present disclosure;

[0099] Figure 21 is a structural diagram of the arrangement of the temperature sensor of the rear case of the reducer according to some embodiments of the present disclosure;

[0100] Figure 22 is a schematic diagram of the circuit connection of the drive assembly according to some embodiments of the present disclosure;

[0101] Figure 23 is another schematic diagram of the circuit connection of the drive assembly according to some embodiments of the present disclosure;

[0102] Figure 24 is a structural diagram of the oil guide channel according to some embodiments of the present disclosure;

[0103] Figure 25 is a structural diagram of the stator heat exchange oil channel according to some embodiments of the present disclosure;

[0104] Figure 26 is a diagram of the motor heat exchange oil channel according to some embodiments of the present disclosure;

[0105] Figure 27 is a structural diagram of the oil sump in Figure 4;

[0106] Figure 28 is a structural diagram of the oil sump and the gear according to some embodiments of the present disclosure;

[0107] Figure 29 is an exploded view of a differential according to some embodiments of the present disclosure;

[0108] Figure 30 is a structural diagram of the upper differential case in Figure 29;

[0109] Figure 31 is another structural diagram of the upper differential case in Figure 29;

[0110] Figure 32 is yet another structural diagram of the lower differential case in Figure 29;

[0111] Figure 33 is a structural diagram of the first gasket in Figure 29;

[0112] Figure 34 is a structural diagram of the first planetary shaft in Figure 29;

[0113] Figure 35 is a structural diagram of the retainer in Figure 29;

[0114] Figure 36 is a structural diagram of the second planetary shaft in Figure 29;

[0115] Figure 37 is a structural diagram of the oil extraction pipe arranged on the front case according to some embodiments of the present disclosure;

[0116] Figure 38 is a structural diagram of the oil extraction pipe in Figure 37;

[0117] Figure 39 is a partial structural diagram of the oil extraction pipe arranged in the reducer case according to some embodiments of the present disclosure;

[0118] Figure 40 is a diagram of the state of the oil in the reducer case when the vehicle is rapidly decelerating according to some embodiments of the present disclosure;

[0119] Figure 41 is a diagram of the state of oil in the reduction gearbox when the vehicle is accelerating rapidly, according to some embodiments of the present disclosure;

[0120] Figure 42 is a diagram of the structure of a fine filter, according to some embodiments of the present disclosure;

[0121] Figure 43 is a diagram of the structure of a fine filter mounted on a reduction gearbox, according to some embodiments of the present disclosure;

[0122] Figure 44 is a diagram of a cross-section along the radial direction of a fine filter, according to some embodiments of the present disclosure;

[0123] Figure 45 is a diagram of a cross-section of an oil pump integrated on a reduction gearbox, according to some embodiments of the present disclosure;

[0124] Figure 46 is a diagram of the structure of a reduction gearbox, according to some embodiments of the present disclosure;

[0125] Figure 47 is a cross-section of the reduction gearbox of Figure 46, according to some embodiments of the present disclosure;

[0126] Figure 48 is a diagram of a front view of a drive assembly housing, according to some embodiments of the present disclosure;

[0127] Figure 49 is a diagram of an integrated structure of a drive assembly housing with a passage, according to some embodiments of the present disclosure;

[0128] Figure 50 is a diagram of a cross-section of a suspension hole and an oil passage, according to some embodiments of the present disclosure.

[0129] Reference signs: 1000, vehicle 100, vehicle body; 200, wheel; 300, suspension system; 400, drive assembly; 1, reduction box; 1A, front box; 1B, rear box; 10, lightening groove; 11, main shaft mounting hole; 12, auxiliary shaft mounting hole; 13, differential shaft mounting hole; 14, concave oil storage groove; 141, first concave oil storage groove; 142, second concave oil storage groove; 15, fine filter accommodating cavity; 16, opening; 2, oil guiding structure; 21, oil guiding channel; 21A, oil inlet; 21B, first oil injection port; 21C, second oil injection port; 21D, oil outlet hole; 2101, main channel; 2102, branch channel; 211, first oil guiding channel section; 212, second oil guiding channel section; 213, third oil guiding channel section; 214, integrated oil pipe; 22, main shaft oil channel port; 23, auxiliary shaft oil channel port; 24, differential shaft oil channel port; 25, rotor heat exchange oil channel; 26, stator heat exchange oil channel; 261, first winding end heat exchange oil channel; 2611, third oil injection port; 2611A, first sub-oil injection port; 2611B, second sub-oil injection port; 262, second winding end heat exchange oil channel; 2621, fourth oil injection port; 2621A, third sub-oil injection port; 2621B, fourth sub-oil injection port; 3, structure to be lubricated; 31, main shaft bearing; 311, first outer ring; 312, first inner ring; 313, first rolling element; 32, auxiliary shaft bearing; 33, differential shaft bearing 4, reduction assembly; 41, main shaft; 411, first hollow oil channel; 42, auxiliary shaft; 43, differential shaft; 44, auxiliary shaft gear; 441, first auxiliary shaft driven gear; 442, second auxiliary shaft driven gear; 45, differential gear; 5, first valve; 50, oil guiding piece; 501, first oil guiding part; 502, second oil guiding part; 503, third oil guiding part; 51, main shaft bearing seat; 511, second avoiding port; 52, auxiliary shaft bearing seat; 53, differential shaft bearing seat; 54, motor; 541, stator; 5411, stator core; 5412, stator winding; 5412A, first winding end; 5412B, second winding end; 542, rotor; 55, motor box, 551, motor housing; 552, motor rear end cover; 56, motor bearing; 561, second inner ring; 562, second outer ring; 563, second rolling element; 57, motor bearing seat; 571, first avoiding port; 58, filling piece; 59, second valve; 6, oil pump; 6A, oil pump inlet; 60, oil cooler; 601, oil pipeline; 602, cooling medium outlet; 603, first flow channel; 604, second flow channel; 605, connecting flow channel; 6051, sub-flow channel section; 606, main oil inlet flow channel; 607, bypass flow channel; 61, communication flow channel; 62, multi-way valve; 63, temperature sensor; 64, third valve; 65, oil pan; 65A, front box oil pan; 65B, rear box oil pan; 650, oil storage space; 6501, first oil storage space;6502、 second oil storage space; 651, through hole; 6511, first through hole; 6512, second through hole; 652, first oil pan; 6521, first partition plate; 6522, second partition plate; 6523, first bottom plate; 653, second oil pan; 6531, third partition plate; 6532, fourth partition plate; 6533, second bottom plate; 6533A, oil guide port; 66, positioning pin; 67, connecting bolt; 68, differential housing; 68A, upper differential case; 68A1, threaded hole; 68A2, mating surface; 68A3, first elastic pin hole; 68B, lower differential case; 68B1, threaded via hole; 68B2, stop surface; 681, second inlet; 69, differential assembly; 691, first planetary shaft; 6911, first limiting portion; 6912, second elastic pin hole; 692, first planetary gear; 693, first gasket; 6931, first oil inlet hole; 6932, inner ring; 694, semi-axle gear; 695, bolt; 696, first elastic pin; 697, retainer; 6971, through hole; 6972, connecting hole; 6981, second planetary shaft; 6981A, second limiting portion; 6982, second planetary gear; 6983, second gasket; 70, oil extraction pipe; 701, oil extraction port; 7011, first oil extraction port; 7012, second oil extraction port; 71, suction filter; 72, fine filter; 721, fine filter element; 722, cover body; 7221, oil inlet port; 7222, oil outlet port; 723, sealing ring; 73, suspension hole; 731, first suspension hole; 732, second suspension hole; 733, third suspension hole; 734, fourth suspension hole; 735, fifth suspension hole; 736, sixth suspension hole; 737, seventh suspension hole; 74, reinforcing rib; 75, oil passage; 751, first oil passage; 752, second oil passage; 753, third oil passage. DETAILED DESCRIPTION

[0130] The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all the embodiments. Based on the embodiments in the present disclosure, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present disclosure.

[0131] It should be noted that all directionality indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present disclosure are only used to explain the relative positional relationship, movement condition, etc. between components in a certain specific posture (as shown in the drawings), and if the specific posture changes, the directionality indications will also change accordingly.

[0132] The terms "first", "second", "third", etc. are used to describe various embodiments and do not imply an order or a ranking of importance, unless otherwise specified. Thus, a feature described as "first", "second", etc. can include one or more of the features. In the description of the disclosure, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0133] In the description of the disclosure, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected", "connected" should be understood in a broad sense, for example, can be fixedly connected, can be detachably connected, or integrally connected. For those skilled in the art, the specific meaning of the above terms in the disclosure can be understood according to the specific circumstances. In addition, when describing the pipeline, "connected" and "connected" in the disclosure have the meaning of conducting. The specific meaning should be understood in combination with the context.

[0134] In the embodiments of the disclosure, the words such as "exemplary" or "for example" are used to mean serving as an example, instance, or illustration. Any embodiment or design presented as "exemplary" or "for example" in the embodiments of the disclosure should not be interpreted as being more preferred or advantageous than other embodiments or design solutions. Rather, the use of "exemplary" or "for example" is intended to present relevant concepts in a concrete manner.

[0135] In the description of the specification, specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

[0136] In the related art, in the reduction gearbox of the electric drive assembly, the gear rotation is mainly used to stir up the lubricating oil, so that the stirred lubricating oil lubricates the bearing. However, with the increasing requirement of current new energy vehicles on driving performance, the gear oil throwing structure in the related art cannot meet the oil amount requirement of each lubrication structure in the electric drive assembly when the motor rotates at high speed.

[0137] To solve the above problems, some embodiments of the disclosure provide a vehicle 1000. The vehicle 1000 can be a pure electric vehicle, a hybrid electric vehicle, a plug-in hybrid electric vehicle, a range-extended electric vehicle, a fuel vehicle, etc. The vehicle 1000 can also be a car, a truck, a bus, a truck, a trailer, etc.

[0138] Please refer to FIG. 1, which is a schematic diagram of a vehicle according to some embodiments of the disclosure. The vehicle 1000 includes a vehicle body 100 and a wheel 200. The vehicle body 100 is used for passengers to ride and carry articles, and the wheel 200 is installed below the vehicle body 100, used to carry the vehicle body 100, and can roll on the road surface to make the vehicle 1000 travel.

[0139] The vehicle 1000 further comprises a suspension system 300. The suspension system 300 is arranged between the vehicle body 100 and the wheels 200, and is configured to transmit force and torque between the vehicle body 100 and the wheels 200, and to absorb the impact force received by the vehicle body 100 during the driving of the vehicle 1000, so as to improve the riding or driving comfort. The suspension system 300 can be a non-independent suspension system, an independent suspension system, or an active suspension system.

[0140] The vehicle 1000 can further comprise a battery and a drive assembly 400 (as shown in FIG. 2), both of which are arranged in the vehicle body 100. The battery is electrically connected to the drive assembly 400, so as to provide power to the drive assembly 400. The drive assembly 400 is configured to convert electrical energy into mechanical energy, and to transmit the mechanical energy to the wheels 200, so as to drive the wheels 200 of the vehicle 1000 to rotate, thereby enabling the vehicle 1000 to drive. The drive assembly 400 can be arranged in the front compartment of the vehicle 1000, so as to drive the front wheels of the vehicle 1000 to rotate, or can be arranged in the rear compartment of the vehicle 1000, so as to drive the rear wheels of the vehicle 1000 to rotate, or can be arranged in both the front compartment and the rear compartment of the vehicle 1000, so as to simultaneously or selectively drive the front wheels and the rear wheels.

[0141] The vehicle 1000 can further comprise a vehicle control unit (VCU). The internal program of the VCU is the core of the vehicle control system, and is responsible for controlling and coordinating various subsystems of the vehicle system, such as the power system, the drive assembly 400, the vehicle charging system, and the like.

[0142] FIGS. 2 and 3 each show a structural diagram of a drive assembly according to some embodiments of the present disclosure. FIGS. 2 and 3 are perspective structural schematic diagrams of the drive assembly from different viewing angles.

[0143] In some embodiments, as shown in FIGS. 2 and 3, the drive assembly 400 can comprise a reduction gearbox 1, an oil guide structure 2, and a structure to be lubricated 3 (as shown in FIG. 4).

[0144] The reduction gearbox 1 can also be referred to as a reducer housing. The reduction gearbox 1 is a basic component for mounting various transmission shafts, and provides stable support and fixation for the transmission elements inside the reducer housing, so as to ensure that they can move according to the predetermined trajectory and speed. In addition, the reduction gearbox 1 is also configured to form a closed space, so as to prevent external dust, moisture, and other impurities from entering the inside of the reduction gearbox 1, and to protect the internal transmission elements from damage by the external environment.

[0145] It can be understood that, in order to improve the service life of the transmission elements in the reduction gearbox 1, the reduction gearbox 1 is provided with oil (which can also be referred to as lubricating oil). The transmission elements (such as gear and bearing components) in the reduction gearbox 1 will generate a large amount of friction when operating at high speed. The main function of the lubricating oil is to reduce the friction between the transmission elements and reduce wear and tear, thereby prolonging the service life of the transmission elements. In addition, the lubricating oil can also absorb and disperse the heat generated by the gears and other components during operation, thereby cooling and preventing the transmission elements from overheating and being damaged. In addition, the lubricating oil also has good cleaning and dispersing properties, which can effectively remove and disperse impurities and deposits in the oil, thereby keeping the inside of the reduction gearbox 1 clean.

[0146] In addition, the oil guide structure 2 is connected between the reduction gearbox 1 and the structure to be lubricated 3. The oil guide structure 2 is used to guide the oil in the reduction gearbox 1 to the structure to be lubricated 3, so as to lubricate the structure to be lubricated 3. For the convenience of description, the oil guide structure 2 and the structure to be lubricated 3 are not described here, and can be referred to in the subsequent description.

[0147] In this way, the oil in the reduction gearbox 1 can flow to the structure to be lubricated 3 through the oil guide structure 2, so as to lubricate the structure to be lubricated 3. Compared with the gear oil throwing structure in the related art, the oil guide structure 2 of some embodiments of the present disclosure can guide the oil in the reduction gearbox 1 to the plurality of structures to be lubricated 3 of the drive assembly 400, so as to meet the oil amount requirement of each structure to be lubricated 3 in the electric drive assembly 400 when the motor rotates at high speed, thereby improving the lubrication effect of each structure to be lubricated 3 of the drive assembly 400.

[0148] FIG. 4 shows an exploded view of part of the drive assembly in FIG. 2. In some embodiments, as shown in FIG. 4, the drive assembly 400 can further include a reduction assembly 4 and a main shaft bearing 31. The reduction assembly 4 is arranged in the reduction gearbox 1. The reduction assembly 4 can include a main shaft 41. The reduction gearbox 1 is provided with a main shaft mounting hole 11. Part of the main shaft 41 is accommodated in the main shaft mounting hole 11. The main shaft bearing 31 is arranged between the main shaft 41 and the inner wall surface of the main shaft mounting hole 11. The main shaft bearing 31 forms at least part of the structure to be lubricated 3.

[0149] The main shaft 41 in the reduction gearbox 1 is a key component of the reduction gearbox 1, which plays an important role in transmitting power and supporting the internal gear assembly. The main shaft 41 can also be referred to as an input shaft or a drive shaft, which is the shaft directly connected to the power source (such as a motor) in the reduction gearbox 1.

[0150] The main shaft 41 is usually made of high-strength and high-wear-resistant materials, for example, the material of the main shaft 41 can be carbon steel (such as 45 steel) or alloy steel (such as 40Cr). In this way, the main shaft 41 made of these materials can withstand both bending moment and torsion moment, ensuring the stability and durability of the main shaft 41 under high-speed operation.

[0151] The main shaft bearing 31 is installed on the main shaft 41 to support the main shaft 41 and reduce friction and wear during rotation. The main shaft bearing 31 can support the main shaft 41 to ensure that the main shaft 41 remains in a stable operating state during high-speed rotation. For example, the main shaft bearing 31 can be a rolling bearing, and for another example, the main shaft bearing 31 can also be a sliding bearing, which is not limited in the present disclosure. It can be understood that the type of bearing to be rotated can be comprehensively considered according to factors such as the working conditions, load characteristics, and speed requirements of the speed reducer 1. For example, for a high-speed heavy-load speed reducer 1, a rolling bearing can be selected because the rolling bearing has a high load capacity and a low friction coefficient.

[0152] Figures 5, 6, 7, and 8 each show a partial structure sectional view of the drive assembly in Figure 2. As shown in Figures 5, 6, 7, and 8, the oil guide structure 2 can include an oil guide channel 21 provided with an oil inlet 21A (as shown in Figure 14) and a first oil injection port 21B. The oil inlet 21A is in communication with the speed reducer 1, and the first oil injection port 21B is opposite the main shaft bearing 31. The first oil injection port 21B is used to inject oil to the main shaft bearing 31 to lubricate the main shaft bearing 31.

[0153] In this way, the oil in the speed reducer 1 can enter the oil guide channel 21 through the oil inlet 21A and then flow out from the first oil injection port 21B to the main shaft bearing 31 to achieve lubrication of the main shaft bearing 31. In addition, some embodiments of the present disclosure are suitable for high-speed operation of the main shaft 41 and can provide sufficient lubrication for the main shaft 41 with a rotational speed of more than 30,000 revolutions per minute.

[0154] In some embodiments, as shown in Figures 5, 7, and 8, the oil guide channel 21 includes a first oil guide channel segment 211, and the first oil guide channel segment 211 and the first oil injection port 21B are both provided on the speed reducer 1, and the first oil injection port 21B is provided on the first oil guide channel segment 211. That is, the first oil guide channel segment 211 and the first oil injection port 21B are both integrated on the speed reducer 1. In this way, some embodiments of the present disclosure reduce the arrangement space of the oil circuit outside the speed reducer 1 by providing the first oil injection port 21B and the first oil guide channel segment 211 on the speed reducer 1, thereby saving valuable space for the overall vehicle design.

[0155] In some embodiments, the main shaft bearing 31 and the first oil injection port 21B are both arranged along the axial direction of the main shaft bearing 31, and the axial direction of the first oil injection port 21B is consistent with the axial direction of the main shaft bearing 31.

[0156] The axial direction of the first oil injection port 21B is consistent with the axial direction of the main shaft bearing 31, which is not limited to absolute consistency, but also includes approximate consistency, i.e., the axial direction of the first oil injection port 21B is approximately consistent with the axial direction of the main shaft bearing 31, for example, the included angle between the axial direction of the first oil injection port 21B and the axial direction of the main shaft bearing 31 is less than 10°, which can be approximately consistent.

[0157] Since the axial direction of the first oil injection port 21B is consistent with the axial direction of the main shaft bearing 31, the oil flowing out of the first oil injection port 21B can flow towards the main shaft bearing 31, thereby improving the lubrication effect of the main shaft bearing 31.

[0158] In some embodiments, the first oil injection port 21B can form an included angle with the axial direction of the main shaft bearing 31 to change the direction or speed of oil injection. For example, the first oil injection port 21B forms an included angle of 30°, 45°, or 70° with the axial direction of the main shaft bearing 31.

[0159] In some embodiments, as shown in FIGS. 7 and 8, the inner wall of the reduction gearbox 1 is provided with a weight-reducing groove 10, which is located on the side of the reduction gearbox 1 in the axial direction of the main shaft bearing 31 to reduce the weight and material usage of the reduction gearbox 1. The first oil injection port 21B can be formed on the inner wall on the side of the weight-reducing groove 10 in the axial direction of the main shaft bearing 31. For example, in the axial direction of the main shaft bearing 31, the cross section of the first oil injection port 21B is smaller than the cross section of the weight-reducing groove 10, so that a negative pressure is formed in the weight-reducing groove 10 relative to the first oil injection port 21B, which facilitates the oil injection from the first oil injection port 21B and lubrication of the main shaft bearing 31.

[0160] In some embodiments, as shown in FIGS. 7 and 8, the first hollow oil channel 411 is arranged inside the main shaft 41, the inner wall of the reduction gearbox 1 is provided with an oil outlet hole 21D communicating with the first oil guide channel segment 211, the first hollow oil channel 411 communicates with the first oil guide channel segment 211 through the oil outlet hole 21D, and the rotor heat exchange oil channel 25 (as shown in FIG. 12) is arranged inside the motor shaft. The first hollow oil channel 411 and the rotor heat exchange oil channel 25 communicate. In this way, the oil is delivered to the rotor heat exchange oil channel 25 through the first oil guide channel segment 211, the oil outlet hole 21D, and the first hollow oil channel 411, and the motor shaft is cooled. Further, the oil outlet hole is arranged on the outer peripheral wall of the motor shaft and communicates with the rotor heat exchange oil channel 25, and the oil is thrown into the motor to cool the inside of the motor.

[0161] As shown in FIG. 7 and FIG. 8, the main shaft bearing 31 can include a first outer ring 311, a first inner ring 312, and at least one first rolling body 313. The first inner ring 312 is sleeved on the main shaft 41, the first outer ring 311 is located between the first inner ring 312 and the inner wall surface of the main shaft mounting hole 11, and the at least one first rolling body 313 is arranged between the first inner ring 312 and the first outer ring 311, that is, a rolling groove is formed between the first inner ring 312 and the first outer ring 311, and the at least one first rolling body 313 is arranged in the rolling groove. The first rolling body 313 transmits load by rolling between the first outer ring 311 and the first inner ring 312, so as to effectively reduce friction and wear, thereby improving the service life and efficiency of the main shaft bearing 31.

[0162] In some embodiments, as shown in FIG. 7 and FIG. 8, along the radial direction of the main shaft bearing 31, the central axis of the first oil injection port 21B (i.e., line O in FIG. 8) is located between the outer wall surface of the first inner ring 312 (i.e., line N in FIG. 8) and the inner wall surface of the first outer ring 311 (i.e., line M in FIG. 8). Since the central axis of the first oil injection port 21B (i.e., line O in FIG. 8) is located between the outer wall surface of the first inner ring 312 and the inner wall surface of the first outer ring 311, the oil injected from the first oil injection port 21B can fall between the first outer ring 311 and the first inner ring 312, thereby achieving lubrication of the first rolling body 313 and ensuring reliable and efficient lubrication of the main shaft bearing 31. Moreover, the oil injection position and angle can effectively break through the high-speed airflow around the main shaft bearing 31 during high-speed operation, so that the main shaft bearing 31 can be fully lubricated.

[0163] In some embodiments, when the rotation speed of the main shaft bearing 31 is low, in order to adapt to the structure of the gearbox (such as the reduction gearbox 1) and avoid other oil channel structures in the gearbox, the central axis of the first oil injection port 21B can be arranged at any position of the main shaft bearing 31, for example, towards the first outer ring 311 of the main shaft bearing 31 or towards the first inner ring 312 of the main shaft bearing 31, instead of being located between the outer wall surface of the first inner ring 312 (i.e., line N in FIG. 8) and the inner wall surface of the first outer ring 311 (i.e., line M in FIG. 8).

[0164] In order to control the lubrication of the main shaft bearing 31, in some embodiments, as shown in FIG. 5 and FIG. 6, the drive assembly 400 further includes a first valve 5 arranged in the first oil guide channel segment 211 and located between the first oil injection port 21B and the oil inlet port 21A. In this way, by controlling the opening and closing of the first valve 5, whether the first oil injection port 21B and the oil inlet port 21A are in communication can be controlled, thereby controlling whether the oil flows out of the first oil injection port 21B, and achieving controllable lubrication of the main shaft bearing 31.

[0165] In some embodiments, the first valve 5 can be a solenoid valve, which is an industrial device that uses electromagnetic control as an automation basic element, mainly used to control the direction, flow, speed and other parameters of fluid. The working principle of solenoid valve is based on electromagnetic induction phenomenon. When energized, the electromagnetic coil generates a magnetic field, attracting the iron core (or called armature) to move, thereby changing the opening and closing state of the valve. When de-energized, the magnetic field disappears, and the iron core is reset under the action of the spring force, and the valve is closed. According to different designs and structures, solenoid valves can realize two working modes of normally closed (de-energized) and normally open (de-energized). Solenoid valve has the advantages of simple structure, rapid action, high control precision, long service life, etc., so as to improve the control precision of the main shaft bearing 31 lubrication.

[0166] In some embodiments, the first valve 5 can also be an electric ball valve, an electric butterfly valve, a hydraulic valve or a pneumatic valve, etc., which is not limited in the present disclosure.

[0167] In some embodiments, as shown in FIG. 4, the speed reduction assembly 4 further comprises a secondary shaft 42 and a differential shaft 43, the speed reduction box 1 is provided with a secondary shaft mounting hole 12 and a differential shaft mounting hole 13, part of the secondary shaft 42 is accommodated in the secondary shaft mounting hole 12, and part of the differential shaft 43 is accommodated in the differential shaft mounting hole 13.

[0168] FIG. 9 shows a schematic diagram of splash lubrication of the rear box according to some embodiments of the present disclosure. As shown in FIG. 9, the driving assembly 400 can further comprise an oil guide 50.

[0169] The main shaft 41, the auxiliary shaft 42, the differential shaft 43 and the oil guide 50 are all arranged in the reduction gearbox 1. When the drive assembly 400 is arranged in the front compartment of the vehicle 1000, the differential shaft 43 can be arranged in a front position close to the front of the vehicle body 100, and the auxiliary shaft 42 can be arranged in a position between the differential shaft 43 and the main shaft 41 and close to the bottom, as shown in FIG. 9. At this time, the gears on the auxiliary shaft 42 can be immersed in the oil and stir the lubricating oil during operation. The auxiliary shaft 42 can also be arranged in a position between the differential shaft 43 and the main shaft 41 and close to the top. At this time, the gears on the auxiliary shaft 42 can not be immersed in the oil and will not stir the lubricating oil during operation. The main shaft 41 can be arranged in a rear position close to the rear of the vehicle body 100. When the drive assembly 400 is arranged in the rear compartment of the vehicle 1000, the differential shaft 43 can be arranged in a rear position close to the rear of the vehicle body 100, and the main shaft 41 can be arranged in a front position close to the front of the vehicle body 100. The auxiliary shaft 42 plays a role of intermediate transmission in the reduction gearbox 1, and it connects the main shaft 41 and the differential shaft 43 and is used to transmit the power of the main shaft 41 to the differential shaft 43. The differential shaft 43 distributes the power transmitted by the auxiliary shaft 42 to the differential, and then drives the two side wheels 200 to rotate, so as to realize the differential rotation of the two side wheels 200 of the vehicle 1000. The differential shaft 43 is a component in the reduction gearbox 1 that is specially used to connect the differential. The differential is a key component in the vehicle 1000 such as an automobile, which is used to realize the differential rotation of the two side wheels 200.

[0170] The main shaft 41 is in driving connection with the auxiliary shaft 42, and the auxiliary shaft 42 is arranged between the main shaft 41 and the differential shaft 43 and is in driving connection with the differential shaft 43.

[0171] As shown in FIG. 4, the reduction assembly 4 can further include a differential gear 45 and at least one auxiliary shaft gear 44. The auxiliary shaft 42 is provided with the auxiliary shaft gear 44, and the differential shaft 43 is provided with the differential gear 45.

[0172] In some embodiments, the auxiliary shaft gear 44 can be in meshing connection with the differential gear 45. In some embodiments, the auxiliary shaft gear 44 can also be in meshing connection with the gear on the main shaft 41, which is not limited in the present disclosure.

[0173] In some embodiments, the at least one auxiliary shaft gear 44 includes two auxiliary shaft gears 44, the two auxiliary shaft gears 44 have different numbers of teeth, and are arranged in sequence along the auxiliary shaft 42 in the axial direction. One auxiliary shaft gear 44 is in meshing connection with the gear on the main shaft 41, and the other auxiliary shaft gear 44 is in meshing connection with the differential gear 45.

[0174] In addition, the oil guide 50 can be connected to the inner wall of the reduction gearbox 1, and the oil guide 50 can be arranged between the differential shaft 43 and the main shaft 41. The oil guide 50 is used to guide the oil splashed by the rotation of the differential gear 45 or the pinion gear 44 to the oil guide 50, and then guide the oil to the main shaft 41, the pinion shaft 42 and the differential shaft 43 respectively.

[0175] For example, the oil guide 50 can be a plate structure connected to the inner wall of the reduction gearbox 1, and the oil guide 50 (i.e. the oil guide plate) is at least partially located at the position where the oil splashed by the rotation of the differential gear 45 or the pinion gear 44 is stirred, so as to ensure that the oil falling on the oil guide plate can flow to the main shaft 41, the pinion shaft 42 and the differential shaft 43 respectively.

[0176] In some embodiments, the oil guide 50 can include a first oil guide part 501 for guiding oil to the main shaft 41. The first oil guide part 501 can be a first oil guide plate arranged on the inner wall of the reduction gearbox 1. The first oil guide plate can be provided with a first oil guide groove for guiding the oil splashed on the first oil guide plate to flow along the first oil guide groove to the main shaft 41. The first oil guide part 501 is used to guide part of the oil splashed by the rotation of the differential gear 45 or the pinion gear 44 to the first oil guide part 501, and then guide the oil to the main shaft 41 by the first oil guide part 501.

[0177] That is, the first oil guide part 501 is used to guide part of the oil splashed by the rotation of the differential gear 45 or the pinion gear 44 to the first oil guide part 501, and then guide the oil to the main shaft 41 by the first oil guide part 501. In this way, the splashing lubrication of the main shaft 41 is realized, which is beneficial to improve the lubrication effect of the main shaft 41.

[0178] In some embodiments, the oil guide 50 can further include a second oil guide part 502 for guiding oil to the pinion shaft 42. The second oil guide part 502 can be a second oil guide plate arranged on the inner wall of the reduction gearbox 1. The second oil guide plate can be provided with a second oil guide groove for guiding the oil splashed on the second oil guide plate to flow along the second oil guide groove to the pinion shaft 42.

[0179] That is, the second oil guide part 502 is used to guide part of the oil splashed by the rotation of the differential gear 45 or the pinion gear 44 to the second oil guide part 502, and then guide the oil to the pinion shaft 42 by the second oil guide part 502. In this way, the splashing lubrication of the pinion shaft 42 is realized, which is beneficial to improve the lubrication effect of the pinion shaft 42.

[0180] In some embodiments, the oil guide 50 can further comprise a third oil guiding part 503 for guiding oil to the differential shaft 43. The third oil guiding part 503 can also be a third oil guiding plate, which can be arranged on the inner wall of the reduction box 1. The third oil guiding plate can be provided with a third oil guiding groove for guiding the oil splashed on the third oil guiding plate to flow along the third oil guiding groove to the differential shaft 43.

[0181] That is, the third oil guiding part 503 is used to splash part of the oil to the third oil guiding part 503 and transfer the oil to the differential shaft 43 through the third oil guiding part 503 when the differential gear 45 and the countershaft gear 44 operate to splash oil. In this way, splash lubrication of the differential shaft 43 is achieved, which is conducive to improving the lubrication effect of the differential shaft 43.

[0182] Further, in some embodiments, as shown in FIG. 4, the drive assembly 400 can further comprise a main shaft bearing 31 arranged on the main shaft 41, a countershaft bearing 32 arranged on the countershaft 42, and a differential shaft bearing 33 arranged on the differential shaft 43. The countershaft bearing 32 is arranged between the countershaft 42 and the inner wall surface of the countershaft mounting hole 12, and the differential shaft bearing 33 is arranged between the differential shaft 43 and the inner wall surface of the differential shaft mounting hole 13. The countershaft bearing 32 and the differential shaft bearing 33 form at least part of the lubrication structure 3.

[0183] The first oil guiding part 501 can be used to splash part of the oil to the first oil guiding part 501 and transfer the oil to the main shaft bearing 31 on the main shaft 41 through the first oil guiding part 501 when the differential gear 45 and the countershaft gear 44 operate to splash oil.

[0184] Similarly, the second oil guiding part 502 can be used to splash part of the oil to the second oil guiding part 502 and transfer the oil to the countershaft bearing 32 on the countershaft 42 through the second oil guiding part 502 when the differential gear 45 and the countershaft gear 44 operate to splash oil. The third oil guiding part 503 can be used to splash part of the oil to the third oil guiding part 503 and transfer the oil to the differential shaft bearing 33 on the differential shaft 43 through the third oil guiding part 503 when the differential gear 45 and the countershaft gear 44 operate to splash oil.

[0185] It should be noted that in some embodiments, the drive assembly 400 further comprises a main shaft bearing seat 51, a countershaft bearing seat 52, and a differential shaft bearing seat 53. The main shaft bearing seat 51, the countershaft bearing seat 52, and the differential shaft bearing seat 53 are used to support and smoothly work the bearings connected thereto. When the reduction assembly 4 is working, the main shaft bearing seat 51, the countershaft bearing seat 52, and the differential shaft bearing seat 53 can bear the heavy load and lateral force of the bearings connected thereto.

[0186] The main shaft bearing seat 51 is arranged between the main shaft bearing 31 and the inner wall surface of the main shaft mounting hole 11, and is connected with the main shaft bearing 31. The secondary shaft bearing seat 52 is arranged between the secondary shaft bearing 32 and the inner wall surface of the secondary shaft mounting hole 12, and is connected with the secondary shaft bearing 32. The differential bearing seat 53 is arranged between the differential bearing 33 and the inner wall surface of the differential shaft mounting hole 13, and is connected with the differential bearing 33.

[0187] In order to ensure that the oil flowing down the oil guide 50 can flow into the main shaft bearing 31, the secondary shaft bearing 32 and the differential bearing 33 respectively, the oil guide structure 2 can further include a main shaft oil channel port 22 arranged on the main shaft bearing seat 51 (as shown in FIG. 9). The main shaft oil channel port 22 is in communication with the main shaft bearing 31 arranged in the main shaft bearing seat 51, and the first oil guide part 501 is used to make part of the oil splash to the first oil guide part 501 and then transfer to the main shaft oil channel port 22 through the first oil guide part 501.

[0188] In some embodiments, the main shaft oil channel port 22 can be arranged towards the first rolling body 313 of the main shaft bearing seat 51, so as to improve the lubrication effect of the main shaft bearing 31.

[0189] Similarly, the oil guide structure 2 can further include a secondary shaft oil channel port 23 arranged on the secondary shaft bearing seat 52. The secondary shaft oil channel port 23 is in communication with the secondary shaft bearing 32 arranged in the secondary shaft bearing seat 52, and the second oil guide part 502 is used to make part of the oil splash to the second oil guide part 502 and then transfer to the secondary shaft oil channel port 23 through the second oil guide part 502. The oil guide structure 2 can further include a differential shaft oil channel port 24 arranged on the differential bearing seat 53. The differential shaft oil channel port 24 is in communication with the differential bearing 33 arranged in the differential bearing seat 53, and the third oil guide part 503 is used to make part of the oil splash to the third oil guide part 503 and then transfer to the differential shaft oil channel port 24 through the third oil guide part 503.

[0190] FIG. 10 shows a schematic diagram of splash lubrication of the front box. In order to ensure that the reduction box 1 can run smoothly and efficiently, in some embodiments, as shown in FIGS. 4, 9 and 10, the reduction box 1 can include a front box 1A and a rear box 1B, and the rear box 1B is located away from the motor on the side of the front box 1A. The front box 1A and the rear box 1B are both provided with the main shaft bearing 31, the secondary shaft bearing 32, the differential bearing 33, the main shaft bearing seat 51, the secondary shaft bearing seat 52, the differential bearing seat 53 and the oil guide 50. The main shaft bearing 31, the secondary shaft bearing 32, the differential bearing 33, the main shaft bearing seat 51, the secondary shaft bearing seat 52, the differential bearing seat 53 and the oil guide 50 in the front box 1A and the rear box 1B can be referred to the above description, and the present disclosure will not be repeated here.

[0191] Thus, when the rotation speed of the main shaft 41 is less than or equal to the first threshold value, the main shaft bearing 31 has a small lubrication requirement, the first valve 5 is closed, and the main shaft bearing 31 is lubricated by the oil splashing caused by the rotation of the differential gear 45 and the auxiliary shaft gear 44, so as to save energy. When the rotation speed of the main shaft 41 is greater than the first threshold value, the main shaft bearing 31 has a large lubrication requirement, the first valve 5 can be controlled to be opened, the oil sprayed by the first oil injection port 21B lubricates and cools the main shaft bearing 31, and the oil splashing caused by the rotation of the differential gear 45 and the auxiliary shaft gear 44 also lubricates and cools the main shaft bearing 31, so as to meet the lubrication requirement of the main shaft bearing 31.

[0192] For example, the first threshold value can be 25000r / min, and for another example, the first threshold value can also be 22000r / min, 23000r / min, 24000r / min, 26000r / min, 28000r / min, or 30000r / min, etc. The present disclosure does not make any limitation in this regard.

[0193] FIGS. 11, 12 and 13 each show a partial structure sectional view of the drive assembly in FIG. 2. As shown in FIGS. 11, 12 and 13, in some embodiments, the drive assembly 400 can further include a motor 54 (as shown in FIG. 24), a motor box 55 and a motor bearing 56. The motor box 55 can also be referred to as a motor box body, and the motor box 55 can prevent the motor 54 from being damaged due to changes in load or other reasons during operation. It plays a role of protection and insulation, and makes the motor 54 in a relatively safe working environment.

[0194] The motor 54, which can also be referred to as a motor, is arranged in the motor box 55. The motor can include a stator 541 and a rotor 542 (as shown in FIG. 24), the stator 541 and the rotor 542 are coaxially arranged, and the stator 541 is nested outside the rotor 542. The stator 541 includes a stator core 5411 and a stator winding 5412 arranged on the stator core 5411, and the rotor 542 includes a rotor core, a rotor winding arranged on the rotor core, and a rotating shaft. The working principle of the motor 54 is mainly based on the law of electromagnetic induction and the action of magnetic field on current force. For example, the stator winding 5412 generates a rotating magnetic field after being electrified, and the winding in the rotor 542 induces a current in the rotating magnetic field, and then generates an electromagnetic force. This electromagnetic force is the power source for the rotation of the rotor 542, which realizes the conversion of electric energy into mechanical energy.

[0195] The motor 54 can further include an output shaft, which can be connected with the rotating shaft of the rotor 542, for example, the output shaft can be integrated with the rotating shaft of the rotor 542. In this way, when the rotating shaft rotates, the output shaft rotates together. The motor box 55 is provided with an output shaft mounting hole, part of the output shaft is accommodated in the output shaft mounting hole, and the motor bearing 56 is arranged between the output shaft and the inner wall surface of the output shaft mounting hole, and the motor bearing 56 forms at least part of the lubrication structure 3 to be lubricated.

[0196] Figure 14 shows a schematic diagram of the flow of oil in the drive assembly according to some embodiments of the present disclosure. As shown in Figures 11, 12, 13 and 14, the oil guide structure 2 further includes an oil guide channel 21 provided with an oil inlet 21A and a second oil outlet 21C. The oil inlet 21A is in communication with the reduction box 1, and the second oil outlet 21C is arranged opposite the motor bearing 56, so that the oil sprayed from the second oil outlet 21C can flow to the motor bearing 56. In this way, the oil in the reduction box 1 can enter the oil guide channel 21 through the oil inlet 21A, and then flow out from the second oil outlet 21C to the motor bearing 56, so as to achieve lubrication of the motor bearing 56.

[0197] In some embodiments, the oil guide channel 21 includes a second oil guide channel segment 212, and the second oil guide channel segment 212 and the second oil outlet 21C are arranged on the motor box 55, and the second oil outlet 21C is arranged on the second oil guide channel segment 212. That is, the second oil guide channel segment 212 and the second oil outlet 21C are integrally arranged on the motor box 55. In this way, by arranging the second oil outlet 21C and the second oil guide channel segment 212 on the motor box 55, the arrangement space of the oil circuit is reduced, and the structure of the drive assembly 400 is more compact, saving space for vehicle design.

[0198] It should be noted that the oil guide channel 21 provided with the oil inlet 21A and the second oil outlet 21C, and the oil guide channel 21 provided with the oil inlet 21A and the first oil outlet 21B are different embodiments listed in the present disclosure. The oil guide structure 2 can include one of the oil guide channel 21 provided with the oil inlet 21A and the second oil outlet 21C, or the oil guide channel 21 provided with the oil inlet 21A and the first oil outlet 21B. The oil guide structure 2 can also include both the oil guide channel 21 provided with the oil inlet 21A and the second oil outlet 21C, and the oil guide channel 21 provided with the oil inlet 21A and the first oil outlet 21B.

[0199] For example, the oil guide structure 2 can include one oil guide channel 21, i.e. the oil guide channel 21 provided with the oil inlet 21A and the second oil outlet 21C, and the oil guide channel 21 provided with the oil inlet 21A and the first oil outlet 21B can be the same oil guide channel 21, i.e. the oil guide channel 21 is provided with the oil inlet 21A, the first oil outlet 21B and the second oil outlet 21C.

[0200] For example, the oil guide structure 2 can include two oil guide channels 21, i.e. the oil guide channel 21 provided with the oil inlet 21A and the second oil injection port 21C, and the oil guide channel 21 provided with the oil inlet 21A and the first oil injection port 21B can be two different oil guide channels 21, i.e. one of the oil guide channels 21 is provided with the oil inlet 21A and the second oil injection port 21C, and the other oil guide channel 21 is provided with the oil inlet 21A and the first oil injection port 21B.

[0201] In order to ensure that the motor bearing 56 can work stably during the operation of the motor 54, in some embodiments, as shown in FIGS. 12 and 13, the driving assembly 400 can further include a motor bearing seat 57. The motor bearing seat 57 is arranged in the motor box 55, the motor bearing seat 57 is arranged between the motor bearing 56 and the inner wall surface of the output shaft mounting hole, and is connected with the motor bearing 56. In this way, the motor bearing seat 57 can support the motor bearing 56, and when the motor 54 is normally operated, the motor bearing seat 57 can ensure the rotation accuracy and stability of the motor bearing 56, and ensure that the motor 54 can operate efficiently and reliably.

[0202] In addition, the motor bearing seat 57 is provided with a first avoiding port 571 facing the motor bearing 56, and the second oil injection port 21C is arranged towards the first avoiding port 571. Because the first avoiding port 571 is arranged on the motor bearing seat 57, and the second oil injection port 21C is arranged towards the first avoiding port 571.

[0203] It can be understood that the motor bearing 56 will generate a large amount of friction when rotating at high speed, and such friction will cause the surface of the motor bearing 56 to be abraded intensively, thereby shortening the service life of the motor 54. The oil ejected by the second oil injection port 21C of some embodiments of the present disclosure can be sprayed into the motor bearing 56 through the first avoiding port 571, and these oil can form a thin film on the outer surface of the motor bearing 56, thereby effectively reducing the friction and protecting the surface of the motor bearing 56 from being abraded.

[0204] In some embodiments, the reduction gearbox includes a front box and a rear box, the front box can be an integral structure with the motor box 55, i.e. the motor box 55 and the front box of the reduction gearbox 1 are integrally arranged, and the rear box is connected with the front box through bolts. At this time, the second oil injection port 21C and the second oil guide channel segment 212 are integrated in the integrally arranged motor box 55 and the front box of the reduction gearbox 1. In this way, it is beneficial to the miniaturization of the driving assembly 400, and saves space for the design of the whole vehicle.

[0205] In some embodiments, the motor housing 55 is integrally formed with the front housing, and the rear housing is bolted to the front housing. In other embodiments, the motor housing 55 is integrally formed with the rear housing, and the front housing is bolted to the rear housing. In yet other embodiments, the motor housing 55 is separately formed from the front housing and the rear housing, and the front housing and the rear housing are bolted to each other. In this case, the second oil injection port 21C and the second oil channel segment 212 can be integrated in the motor housing 55, and a corresponding communication hole can be formed in the front housing to allow the oil to be injected from the second oil injection port 21C and flow to the main shaft bearing 31. The second oil injection port 21C and the second oil channel segment 212 can also be integrated in the front housing, and a corresponding communication hole can be formed in the motor housing 55 to allow the oil to be injected from the second oil injection port 21C and flow to the motor bearing 56.

[0206] In some embodiments, the main shaft bearing seat 51 is provided with a second avoiding port 511 facing the main shaft bearing 31, and the first avoiding port 571 and the second avoiding port 511 can be oppositely arranged. The first avoiding port 571 and the second avoiding port 511 can be an integrated through structure to form an accommodation gap. The second oil injection port 21C is arranged between the first avoiding port 571 and the second avoiding port 511 to inject oil to both the motor bearing seat 57 and the main shaft bearing seat 51.

[0207] In this way, the oil injected from the second oil injection port 21C can flow into the first avoiding port 571 and the second avoiding port 511, respectively, and be sprayed to the motor bearing 56 and the main shaft bearing 31 through the first avoiding port 571 and the second avoiding port 511, respectively, so as to simultaneously lubricate the motor bearing 56 and the main shaft bearing 31.

[0208] It should be noted that the oil injected from the second oil injection port 21C to be sprayed to the motor bearing 56 and the main shaft bearing 31, and the oil injected from the first oil injection port 21B to be sprayed to the main shaft bearing 31 are different embodiments of the present disclosure. The oil guiding structure 2 can include one of the second oil injection port 21C and the first oil injection port 21B, or the oil guiding structure 2 can simultaneously include the second oil injection port 21C and the first oil injection port 21B, which is not limited by the present disclosure.

[0209] For example, when the oil guiding structure 2 simultaneously includes the second oil injection port 21C and the first oil injection port 21B, one end of the main shaft bearing 31 can be arranged in the front housing, the other end of the main shaft bearing 31 can be arranged in the rear housing, the second oil injection port 21C can be arranged close to or in the front housing, and the second oil injection port 21C can inject oil to the (part of) main shaft bearing 31 arranged in the front housing and the motor bearing 56. The first oil injection port can be arranged close to or in the rear housing to inject oil to the (part of) main shaft bearing 31 arranged in the rear housing.

[0210] In some embodiments, as shown in FIGS. 12 and 13, the motor bearing 56 can include a second inner ring 561, a second outer ring 562, and a plurality of second rolling elements 563. The second inner ring 561 is sleeved on the output shaft of the motor 54, and the second outer ring 562 is located between the second inner ring 561 and the inner wall surface of the output shaft mounting hole. The second rolling elements 563 are arranged between the second outer ring 562 and the second inner ring 561. The second rolling elements 563 can effectively reduce friction and wear by rolling between the second outer ring 562 and the second inner ring 561 to transmit load, thereby improving the service life and efficiency of the motor bearing 56.

[0211] As shown in FIG. 13, along the radial direction of the spindle bearing 31, the central axis (line R in FIG. 13) of the second oil injection port 21C is located between the outer wall surface (line Q in FIG. 13) of the first inner ring 312 and the inner wall surface (line P in FIG. 13) of the second outer ring 562.

[0212] In some embodiments, the spindle bearing 31 and the second oil injection port 21C are both arranged along the axial direction of the spindle bearing 31, and the axial direction of the second oil injection port 21C is consistent with the axial direction of the spindle bearing 31.

[0213] The axial direction of the second oil injection port 21C being consistent with the axial direction of the spindle bearing 31 is not limited to being absolutely consistent, but also includes being approximately consistent, that is, the axial direction of the second oil injection port 21C can be approximately consistent with the axial direction of the spindle bearing 31. For example, the included angle between the axial direction of the second oil injection port 21C and the axial direction of the spindle bearing 31 can be less than 10°, which can be approximately consistent. In this way, it can be ensured that the oil flowing out of the second oil injection port 21C flows towards the spindle bearing 31, thereby improving the lubrication effect of the spindle bearing 31.

[0214] In other embodiments, the second oil injection port 21C can form an included angle with the axial direction of the spindle bearing 31 to change the direction or speed of oil injection. For example, the second oil injection port 21C can form an included angle of 30°, 45°, or 70° with the axial direction of the spindle bearing 31.

[0215] In this way, it can be ensured that the oil injected from the second oil injection port 21C is located between the outer wall surface of the first inner ring 312 and the inner wall surface of the second outer ring 562, that is, the oil injected from the second oil injection port 21C can be injected onto the first rolling elements 313 and the second rolling elements 563 at the same time, thereby achieving effective lubrication of the spindle bearing 31 and the motor bearing 56 and improving the lubrication effect of the spindle bearing 31 and the motor bearing 56. In addition, the oil injection position and the oil injection angle can effectively break through the high-speed airflow generated around the spindle bearing 31 and the motor bearing 56 during high-speed operation, thereby enabling the spindle bearing 31 and the motor bearing 56 to be sufficiently lubricated.

[0216] In some embodiments, the first oil injection port 21B can be arranged at an angle with respect to the axial direction of the main shaft bearing 31, so as to change the direction of the injected oil or the speed of the injected oil. For example, the first oil injection port 21B can be arranged at an angle of 30°, 45° or 70° with respect to the axial direction of the main shaft bearing 31.

[0217] In some embodiments, as shown in FIG. 13, a filler 58, for example, a plastic filler ring, can be arranged between the main shaft bearing seat 51 and the motor bearing seat 57. The filler 58 gradually increases in height along a first direction from the motor bearing 56 to the reducer bearing. The side of the filler 58 close to the motor bearing 56 is flush with the second inner ring 562, and the side of the filler 58 close to the main shaft bearing 31 is flush with the first inner ring 312.

[0218] In this way, the injected oil can be prevented from flowing into the gap between the main shaft bearing seat 51 and the motor bearing seat 57, thereby preventing waste of lubricating oil and affecting the lubrication effect of the motor bearing 56 and the main shaft bearing 31.

[0219] In order to achieve controllable lubrication of the main shaft bearing 31 and the motor bearing 56, in some embodiments, as shown in FIG. 11, the drive assembly 400 can further include a second valve 59, which can be arranged in the second oil guide passage segment 212 and located between the second oil injection port 21C and the oil inlet 21A.

[0220] The second valve 59 can be an electromagnetic valve, an electric ball valve, an electric butterfly valve, a hydraulic valve or a pneumatic valve, and the present disclosure does not limit the valve type.

[0221] In this way, by controlling the opening and closing of the second valve 59, whether the second oil injection port 21C and the oil inlet 21A are in communication can be controlled, thereby controlling whether the second oil injection port 21C flows out oil, and achieving controllable lubrication of the main shaft bearing 31 and the motor bearing 56.

[0222] FIGS. 15 and 16 are cross-sectional views of the oil cooler communication flow channel according to some embodiments of the present disclosure. In some embodiments, as shown in FIGS. 14, 15 and 16, the oil guide structure 2 includes an oil guide passage 21, which is provided with an oil inlet 21A and an oil injection port. The oil inlet 21A is in communication with the speed reducer 1. The drive assembly 400 further includes an oil pump 6 and an oil cooler 60 arranged in the oil guide passage 21 in sequence.

[0223] The oil pump 6 is a device for delivering liquid (such as oil) from one location to another by mechanical or electrical means. For example, the oil pump 6 can be an electronic oil pump. The working principle of the electronic oil pump in some embodiments of the present disclosure is as follows: when the motor 54 is powered on, it drives the rotor 542 or the blade inside the oil pump 6 to rotate, thereby generating suction to suck oil from the reduction gearbox 1 into the pump. With the continuous rotation of the rotor 542, the oil is compressed and pressurized and then delivered to the oil cooler 60 through the oil outlet. For example, the oil pump 6 can also be a mechanical oil pump, a gear oil pump, a vane oil pump, an electric oil pump, etc., which are not limited in the present disclosure.

[0224] The oil cooler 60 is an oil cooling device commonly used in lubrication systems. It uses the principle of heat exchange to exchange heat between two fluid media (usually oil and cooling medium) with a certain temperature difference, thereby reducing the oil temperature.

[0225] For example, the oil cooler 60 provided by some embodiments of the present disclosure can be a water-cooled oil cooler that uses water as a cooling medium to remove heat from hot oil through the circulation of water. Since the water-cooled oil cooler has the advantages of good cooling effect and can meet the requirement of low oil temperature, etc., it can ensure that the oil temperature after cooling by the oil cooler is low, thereby improving the oil cooling effect.

[0226] For another example, the oil cooler 60 provided by some embodiments of the present disclosure can be an air-cooled oil cooler that uses air as a cooling medium to dissipate heat from hot oil into the air through a fan or natural convection.

[0227] In addition, the oil injection port is in communication with the oil outlet of the oil cooler 60, and the oil injection port is opposite to the lubricated structure 3. The oil injection port can be the first oil injection port 21B described above, and the oil injection port can also be the second oil injection port 21C described above, which are not limited in the present disclosure.

[0228] In this way, the oil in the reduction gearbox 1 can be pumped out from the oil inlet 21A under the action of the oil pump 6, and then flow into the oil cooler 60 through the oil guide channel 21 and the oil pump 6, and then flow into the lubricated structure 3 after being cooled by the oil cooler 60, thereby ensuring that the oil temperature is low and achieving cooling of some components.

[0229] In some embodiments, the oil guiding passage 21 can include a main passage and a plurality of branch passages, the main passage is provided with an oil inlet 21A, and the main passage sequentially connects the reduction gearbox 1, the oil pump 6 and the inlet of the oil cooler 60. The plurality of branch passages can include a first branch passage and a second branch passage, both of which are in communication with the oil outlet of the oil cooler, the first branch passage includes a first oil guiding passage segment 211, is provided with a first oil injection port 21B, and is used for lubricating the main shaft bearing 31. The second branch passage includes a second oil guiding passage segment 212, is provided with a second oil injection port 21C, and is used for lubricating the motor bearing 56.

[0230] FIG. 17 shows a structural diagram of the outer side of the front box of the reduction gearbox according to some embodiments of the present disclosure. As shown in FIGS. 16 and 17, the oil cooler 60 is provided with an oil flow channel 601 and a cooling medium flow channel, the oil flowing in the oil flow channel 601 can exchange heat with the cooling medium in the cooling medium flow channel, and the cooling medium flow channel exchanges heat with the outside through a cooling medium outlet 602 on the oil cooler, thereby reducing the temperature of the oil.

[0231] FIG. 18 shows a side view of the front box of the reduction gearbox in FIG. 17, FIG. 19 is a sectional view along the direction AA in FIG. 18, and FIG. 20 is a structural diagram of the inner side of the front box of the reduction gearbox according to some embodiments. As shown in FIGS. 18, 19 and 20, the oil cooler 60 further forms a first flow channel 603 and a second flow channel 604, and the oil flow channel 601 connects the first flow channel 603 and the second flow channel 604. The oil cooler 60 can further form a connecting flow channel 605 and a main oil inlet flow channel 606, the connecting flow channel 605 includes a plurality of sub-flow channel segments 6051 connected in sequence, any two adjacent sub-flow channel segments 6051 are connected by bending, the first flow channel 603 is in communication with one of the sub-flow channel segments 6051, and the main oil inlet flow channel 606 is selectively in communication with the second flow channel 604 and another one of the sub-flow channel segments 6051.

[0232] The oil cooler 60 is formed with a cooling medium flow channel and an oil flow channel 601, which can be arranged adjacently. The oil cooler 60 can be formed with a cooling medium inlet and a cooling medium outlet 602, the cooling medium flow channel is communicated with the cooling medium inlet and the cooling medium outlet 602, the heat exchange medium (for example, water, gas or other medium) flows into the cooling medium flow channel from the cooling medium inlet, the heat exchange medium flowing into the cooling medium flow channel flows along the cooling medium flow channel to the cooling medium outlet 602, and the heat exchange medium flows out of the oil cooler 60 through the cooling medium outlet 602. The oil cooler 60 has a first flow channel 603 and a second flow channel 604, the oil flow channel 601 is communicated with the first flow channel 603 and the second flow channel 604, one of the first flow channel 603 and the second flow channel 604 is an oil outlet flow channel of the oil cooler 60, and the other of the first flow channel 603 and the second flow channel 604 is an oil inlet flow channel of the oil cooler 60. It can also be understood that when the first flow channel 603 is the oil inlet flow channel of the oil cooler 60, the second flow channel 604 is the oil outlet flow channel of the oil cooler 60, and when the first flow channel 603 is the oil outlet flow channel of the oil cooler 60, the second flow channel 604 is the oil inlet flow channel of the oil cooler 60. Some embodiments of the present disclosure mainly take the first flow channel 603 as the oil inlet flow channel of the oil cooler 60 and the second flow channel 604 as the oil outlet flow channel of the oil cooler 60 as an example for description.

[0233] The lubricating oil in the reduction gearbox 1 can flow into the oil flow channel 601 through the first flow channel 603, the lubricating oil flowing into the oil flow channel 601 flows along the oil flow channel 601 to the second flow channel 604, and the lubricating oil flows out of the oil cooler 60 from the second flow channel 604. When the heat exchange medium flows in the cooling medium flow channel and the lubricating oil flows in the oil flow channel 601, heat exchange between the lubricating oil and the heat exchange medium can be achieved.

[0234] As shown in FIG. 19, the oil cooler 60 is further formed with a connecting flow channel 605 and a main oil inlet flow channel 606. The connecting flow channel 605 includes a plurality of sub-flow channel segments 6051, which can include two, three, or four sub-flow channel segments 6051, and the number of the sub-flow channel segments 6051 can be reasonably set according to actual conditions. The plurality of sub-flow channel segments 6051 are connected in sequence, and any two adjacent sub-flow channel segments 6051 are connected in communication, connected in bending, or form an included angle therebetween, and the included angle therebetween can be reasonably set according to actual requirements. The first flow channel 603 is in communication with one of the plurality of sub-flow channel segments 6051, and the main oil inlet flow channel 606 is selectively in communication with the second flow channel 604 or another of the plurality of sub-flow channel segments 6051. The sub-flow channel segment 6051 in communication with the first flow channel 603 and the sub-flow channel segment 6051 in communication with the main oil inlet flow channel 606 are two different sub-flow channel segments 6051, or it can be understood that one of the two different sub-flow channel segments 6051 in the plurality of sub-flow channel segments 6051 is in communication with the first flow channel 603, and the other of the two different sub-flow channel segments 6051 in the plurality of sub-flow channel segments 6051 is adapted to be in communication with the main oil inlet flow channel 606. The main oil inlet flow channel 606 can be in communication with the inside of the reduction gearbox 1, and the lubricating oil in the reduction gearbox 1 can flow into the main oil inlet flow channel 606.

[0235] In some embodiments, the oil cooler is formed with a communication flow channel 61, which includes three interfaces in communication with the main oil inlet flow channel 606, the second flow channel 604, and the corresponding sub-flow channel segment 6051, respectively. The drive assembly 400 can further include a multi-way valve 62, at least part of which is arranged in the communication flow channel 61, and the main oil inlet flow channel 606 can be selectively in communication with one of the second flow channel 604 and the corresponding sub-flow channel segment 6051 by the multi-way valve 62.

[0236] For example, the multi-way valve 62 can be a three-way valve, which mainly includes a valve body, a valve core (or a valve plate), a sealing element, and the like. The position change of the valve core determines the flow direction and flow rate of the fluid. The working principle of the three-way valve is based on the position change of the valve core. When the valve core is in different positions, the flow direction and flow rate of the fluid will change.

[0237] For example, the three-way valve can be a two-position three-way solenoid valve, which generally includes an electromagnet, a valve core and the like. When the electromagnet (or other control element) is energized, the valve core is attracted or moved, so that the main oil inlet flow channel 606 is in communication with the second flow channel 604, and the main oil inlet flow channel 606 is disconnected from one of the corresponding sub-flow channel segments 6051. In this way, the fluid can flow along the predetermined path. When the electromagnet is de-energized, the valve core is reset under the action of a spring or other reset mechanism, so that the main oil inlet flow channel 606 is in communication with one of the corresponding sub-flow channel segments 6051, and the main oil inlet flow channel 606 is disconnected from the second flow channel 604, thereby changing the flow direction of the oil.

[0238] For example, the multi-way valve can also be a four-way valve or a five-way valve, which is not limited in the present disclosure.

[0239] In other embodiments, the main oil inlet flow channel 606 can also be selectively communicated with the second flow channel 604 and one of the corresponding sub-flow channel segments 6051 by an opening and closing door. For example, the outlet of the main oil inlet flow channel 606 is in communication with the inlet of the second flow channel 604 and the inlet of the corresponding sub-flow channel segment 6051. By closing one of the inlet of the second flow channel 604 and the inlet of the corresponding sub-flow channel segment 6051 by the opening and closing door, the main oil inlet flow channel 606 is in communication with the other one of the inlet of the second flow channel 604 and the inlet of the corresponding sub-flow channel segment 6051. In addition, the present disclosure is not limited thereto, and other schemes can also be used to control the main oil inlet flow channel 606 to be selectively communicated with the second flow channel 604 and one of the corresponding sub-flow channel segments 6051, as long as the main oil inlet flow channel 606 can be selectively communicated with the second flow channel 604 and one of the corresponding sub-flow channel segments 6051.

[0240] When the main oil inlet flow channel 606 is in communication with the corresponding sub-flow channel segment 6051, the oil flowing into the main oil inlet flow channel 606 can flow into the first flow channel 603 along the connecting flow channel 605. When the first flow channel 603 is the oil inlet flow channel of the oil cooler 60 and the second flow channel 604 is the oil outlet flow channel of the oil cooler 60, the oil flows into the oil flow channel 601 through the first flow channel 603, and the oil flows out along the oil flow channel 601 through the second flow channel 604. The heat exchange medium in the heat exchange medium flow channel can exchange heat with the oil in the oil flow channel 601 during the flow process, thereby reducing the temperature of the oil.

[0241] When the main oil inlet flow channel 606 is in communication with the second flow channel 604, the oil flowing into the main oil inlet flow channel 606 flows into the second flow channel 604. Compared with the case where the main oil inlet flow channel 606 is in communication with the corresponding sub-flow channel segment 6051, the oil does not flow through the oil flow channel 601 and does not exchange heat with the heat exchange medium in the heat exchange medium flow channel, but flows into the structure to be lubricated 3 along the second flow channel 604.

[0242] For example, when the oil temperature is low, for example, when the oil temperature is less than or equal to 30°, the main oil inlet flow channel 606 is in communication with the second flow channel 604, which is conducive to rapid increase of the oil temperature, so as to achieve the purpose of active temperature control. When the oil temperature is high and needs to be cooled, the main oil inlet flow channel 606 is in communication with the corresponding sub-flow channel section 6051, and the oil enters the oil cooler and is cooled by the heat exchange medium, so as to reduce the oil temperature. Therefore, by selectively communicating the main oil inlet flow channel 606 with one of the second flow channel 604 and another sub-flow channel section 6051, the effects of regulating the oil temperature increase and decrease can be achieved, so as to achieve the regulation of the oil temperature. In addition, the oil cooler 60 has simple structure and low manufacturing cost, and is convenient for production and manufacturing.

[0243] In addition, when the main oil inlet flow channel 606 is in communication with the second flow channel 604, the inlet of the corresponding sub-flow channel section 6051 in communication with the main oil inlet flow channel 606 is closed by the opening and closing door, the multi-way valve 62 or the like. There is a gap between the opening and closing door, the multi-way valve 62 and the inlet of the corresponding sub-flow channel section 6051, and a small amount of oil will flow into the oil flow channel 601 under the action of oil pressure, thereby affecting the oil temperature increase speed. Therefore, by bending and connecting the adjacent two sub-flow channel sections 6051, the oil flows into the connecting flow channel 605, and the oil flowing into the connecting flow channel 605 needs to change the flow direction to flow into the first flow channel 603. When the oil flows through the connecting flow channel 605, the flow resistance increases, the oil pressure decreases, which is conducive to reducing the amount of oil entering the oil flow channel 601, reducing the amount of cooled oil, and facilitating the oil temperature increase.

[0244] In some embodiments of the present disclosure, as shown in FIG. 19, the oil cooler 60 can further form a bypass flow channel 607, the bypass flow channel 607 is in communication with the second flow channel 604, and the main oil inlet flow channel 606 is selectively in communication with the bypass flow channel 607, so that the bypass flow channel 607 is in communication with the second flow channel 604 and the main oil inlet flow channel 606. That is, when the main oil inlet flow channel 606 is selectively in communication with the second flow channel 604, the main oil inlet flow channel 606 is in communication with the second flow channel 604 through the bypass flow channel 607; when the main oil inlet flow channel 606 is selectively in communication with another sub-flow channel section 6051, the bypass flow channel 607 is closed.

[0245] The oil cooler 60 defines the bypass flow channel 607, the outlet of the bypass flow channel 607 is in communication with the second flow channel 604, and the main oil inlet flow channel 606 is selectively in communication with the inlet of the bypass flow channel 607. When the main oil inlet flow channel 606 is in communication with the inlet of the bypass flow channel 607, the bypass flow channel 607 is in communication with the second flow channel 604 and the main oil inlet flow channel 606. By providing the bypass flow channel 607, the effect of indirect communication between the second flow channel 604 and the main oil inlet flow channel 606 can be achieved. When the bypass flow channel 607 and the main oil inlet flow channel 606 are in communication, the bypass flow channel 607 plays a guiding role for the oil, which can make the oil flow to the second flow channel 604, and is conducive to rapid flow of the oil out of the second flow channel 604.

[0246] FIG. 21 shows a structural diagram of the reducer rear case arrangement temperature sensor according to some embodiments of the present disclosure. In some embodiments, the drive assembly 400 can further include a temperature sensor 63, which can be arranged in the reduction gearbox 1, as shown in FIG. 21. For example, the temperature sensor 63 can be arranged on the rear case IB, and the temperature sensor 63 is configured to detect the oil temperature in the reduction gearbox 1.

[0247] The temperature sensor 63 is electrically connected to the multi-way valve 62, and the temperature sensor 63 can also be electrically connected to the vehicle controller VCU.

[0248] As shown in FIG. 22, when the temperature sensor 63 detects that the oil temperature is greater than or equal to a preset temperature value, the vehicle controller VCU identifies that the oil needs to be cooled, and the vehicle controller VCU sends a closing instruction to the multi-way valve 62. After receiving the closing instruction, the multi-way valve 62 connects the first inlet 621 and the first outlet 622 (as shown in FIG. 15), and at this time, the oil path is: inside the reduction gearbox 1 - the oil inlet 21A - the oil pump 6 - the first inlet 621 - the first outlet 622 - the heat exchange pipeline 601 - the oil cooler 60 oil outlet - the lubrication structure 3.

[0249] As shown in FIG. 23, when the temperature sensor 63 detects that the oil temperature is lower than the preset temperature value, the vehicle controller VCU identifies that the oil does not need to be cooled, and the vehicle controller VCU sends an opening instruction to the multi-way valve 62. After receiving the opening instruction, the multi-way valve 62 connects the first inlet 621 and the second outlet 623 (as shown in FIG. 15), and at this time, the oil path is: inside the reduction gearbox 1 - the oil inlet 21A - the oil pump 6 - the first inlet 621 - the second outlet 623 - the communication flow passage 61 - the oil cooler 60 oil outlet - the lubrication structure 3.

[0250] The preset temperature value can be 30°C, and the preset temperature value can also be 35°C, 40°C, or 50°C, which is not limited in the present disclosure, and the preset temperature value can be set according to the actual situation.

[0251] In this way, when the oil temperature in the reduction gearbox 1 does not reach the preset temperature value, the first inlet 621 is connected to the second outlet 623, the oil enters through the first inlet 621, and directly flows into the oil outlet of the oil cooler 60 through the second outlet 623 and the communication flow passage 61, thereby reducing the flow resistance of the oil path and reducing the power of the oil pump 6. When the oil temperature of the drive assembly 400 reaches the preset temperature value, the first inlet 621 is connected to the first outlet 622, the oil enters through the first inlet 621, and flows into the heat exchange oil path of the oil cooler 60 through the first outlet 622, thereby achieving heat exchange and cooling of the oil.

[0252] It can be understood that the rotor 542 of the motor 54 generates a large amount of heat during high-speed rotation due to friction with the stator 541, bearing and other components, and resistance heat generated by current passing through; or a large amount of heat is generated during gear transmission in the reduction box 1. If the heat is not dissipated in time, the temperature of the drive assembly 400 will rise, thereby affecting the performance and service life of the entire drive assembly 400.

[0253] Therefore, in some embodiments of the present disclosure, as shown in FIGS. 14 and 24, the oil guide channel 21 can include a main channel 2101 and a branch channel 2102, the main channel 2101 is provided with an oil inlet 21A, and the main channel 2101 sequentially communicates the reduction box 1, the oil pump 6 and the inlet of the oil cooler 60. The oil guide channel 21 is provided with the oil inlet 21A and the oil outlet hole 21D, and the oil inlet 21A communicates with the reduction box 1. The branch channel 2102 can further include a third branch channel, one end of the third branch channel communicates with the oil outlet of the oil cooler 60, and the other end of the third branch channel forms the oil outlet hole 21D.

[0254] The oil guide structure 2 further includes a rotor heat exchange oil channel 25, which communicates with the oil outlet hole 21D. The rotor heat exchange oil channel 25 is used for heat exchange with the rotor 542 to carry away the heat of the rotor 542. In this way, the oil in the reduction box 1 can flow into the oil guide channel 21 through the oil inlet 21A, and flow into the rotor heat exchange oil channel 25 through the oil outlet hole 21D to exchange heat with the rotor 542 to carry away the heat of the rotor 542, thereby achieving cooling of the rotor 542.

[0255] In some embodiments, the oil guide channel 21 further includes a third oil guide channel segment 213, and the third oil guide channel segment 213 and the oil outlet hole 21D can be arranged on the rear box 1B of the reduction box 1, and the oil outlet hole 21D is arranged on the third oil guide channel segment 213. The third branch channel includes the third oil guide channel segment 213.

[0256] In this way, some embodiments of the present disclosure arrange the oil outlet hole 21D and the third oil guide channel segment 213 on the rear box 1B, thereby reducing the arrangement space of the oil circuit, making the structure of the drive assembly 400 more compact, and saving space for the design of the whole vehicle.

[0257] In order to achieve controllable cooling of the rotor 542 of the motor 54, in some embodiments, the drive assembly 400 can further include a third valve 64, which is arranged on the third oil guide channel segment 213, and the third valve 64 is located between the oil outlet hole 21D and the oil inlet 21A.

[0258] The third valve 64 can also be an electromagnetic valve, an electric ball valve, an electric butterfly valve, a hydraulic valve or a pneumatic valve, etc., which is not limited in the present disclosure.

[0259] In this way, by controlling the opening and closing of the third valve 64, whether the oil outlet hole 21D is in communication with the oil inlet hole 21A can be controlled, thereby controlling whether the oil outlet hole 21D flows out oil, so as to achieve controllable cooling of the rotor 542 of the motor 54.

[0260] In order to achieve cooling of the stator 541, in some embodiments of the present disclosure, the oil guiding structure 2 can further comprise a stator heat exchange oil channel 26.

[0261] In some embodiments, the stator heat exchange oil channel 26 can be in communication with the oil outlet of the oil cooler 60. The stator heat exchange oil channel 26 is used to exchange heat with the stator 541 to take away the heat of the stator 541. In this way, the oil in the reduction gearbox 1 can flow into the oil guiding channel 21 through the oil inlet hole 21A, and flow into the stator heat exchange oil channel 26 through the oil outlet of the oil cooler 60, exchange heat with the stator 541 to take away the heat of the stator 541, so as to achieve cooling of the stator 541.

[0262] In other embodiments, the stator heat exchange oil channel 26 can also be in communication with the oil outlet hole 21D, so that by controlling the opening and closing of the third valve 64, whether the oil outlet hole 21D flows out oil into the stator heat exchange oil channel 26 can be controlled, and the third valve 64 can achieve controllable cooling of the stator 541 of the motor 54.

[0263] In some embodiments of the present disclosure, the stator 541 comprises a stator core 5411 and a stator winding 5412. The stator core 5411 is an important component of the stator 541, which can be made of high-permeability silicon steel sheets laminated together to reduce eddy current loss. The main function of the stator core 5411 is to form the main magnetic circuit of the motor 54 and serve as a support structure for the stator winding 5412. The stator winding 5412 is wound by insulated wires and embedded in the slots of the stator core 5411. The main function of the stator winding 5412 is to generate a rotating magnetic field that interacts with the rotor 542 to achieve rotation of the motor 54. The stator core 5411 is arranged in the motor box 55, and the stator core 5411 can be in interference fit with the motor box 55, so as to avoid the stator core 5411 from being detached from the motor box 55.

[0264] The stator winding 5412 of some embodiments of the present disclosure can comprise a first winding end 5412A and a second winding end 5412B arranged axially along the stator core 5411, and the first winding end 5412A and the second winding end 5412B are arranged at both ends of the stator core 5411. The first winding end 5412A can be the end of the stator winding 5412 close to the crown end of the stator winding. The second winding end 5412B can be the end of the stator winding 5412 close to the welding end of the stator winding.

[0265] It can be understood that the stator winding 5412 can adopt a Hair-pin or I-pin structure. The Hair-pin winding is first formed into a U-shaped structure by splitting, stamping or bending when forming, and this formed end is called the stator winding crown end. When the stator winding 5412 is formed, the other end is processed by a specific process to become a welding end, which is used for welding with the stator core 5411.

[0266] As shown in FIGS. 24, 25 and 26, the stator heat exchange oil channel 26 can include a first winding end heat exchange oil channel 261 and a second winding end heat exchange oil channel 262. One end of the first winding end heat exchange oil channel 261 is in communication with the oil outlet hole 21D, and the first winding end heat exchange oil channel 261 is provided with a third oil injection port 2611, which is arranged towards the first winding end 5412A. The second winding end heat exchange oil channel 262 is provided with a fourth oil injection port 2621, and one end of the second winding end heat exchange oil channel 262 is also in communication with the oil outlet hole 21D. The second winding end heat exchange oil channel 262 is provided with a fourth oil injection port 2621, which is arranged towards the second winding end 5412B.

[0267] In this way, it can be ensured that the oil sprayed from the third oil injection port 2611 can be sprayed on the first winding end 5412A, and the oil sprayed from the fourth oil injection port 2621 can be sprayed on the second winding end 5412B, so as to ensure that the stator winding 5412 can be sufficiently cooled.

[0268] In some embodiments, as shown in FIGS. 24 and 25, the first winding end heat exchange oil channel 261 and the second winding end heat exchange oil channel 262 are annular and coaxially arranged with the stator core 5411. The first winding end heat exchange oil channel 261 can be located on the end face of the first winding end 5412A, and the first winding end heat exchange oil channel 261 is provided with a plurality of third oil injection ports 2611 around the central axis thereof. The second winding end heat exchange oil channel 262 can be located on the end face of the second winding end 5412B, and the second winding end heat exchange oil channel 262 is provided with a plurality of fourth oil injection ports 2621 around the central axis thereof.

[0269] Since the heat generation of the stator winding welding end is higher than that of the stator winding crown end, in some embodiments, the number of fourth oil injection ports 2621 can be greater than the number of third oil injection ports 2611. In this way, some embodiments of the present disclosure can accurately cool different positions of the stator winding 5412 by distributing the number of oil injection ports according to the heat generation of different positions of the stator winding 5412.

[0270] In order to improve the uniform cooling of the stator winding 5412, in some embodiments of the present disclosure, a plurality of third oil injection ports 2611 are uniformly arranged around the central axis of the first winding end heat exchange oil channel 261. A plurality of fourth oil injection ports 2621 are uniformly arranged around the central axis of the first winding end heat exchange oil channel 261.

[0271] For example, the plurality of third oil injection ports 2611 includes 12 third oil injection ports 2611, and the first winding end heat exchange oil channel 261 can be provided with one third oil injection port 2611 every 30° around the central axis thereof. For another example, the plurality of third oil injection ports 2611 includes 30 third oil injection ports 2611, and the first winding end heat exchange oil channel 261 can be provided with one third oil injection port 2611 every 12° around the central axis thereof. In this way, the oil sprayed from the plurality of third oil injection ports 2611 can uniformly spray the first winding end 5412A, so as to achieve precise and uniform cooling of the end portion of the stator winding 5412.

[0272] In order to improve the heat exchange effect on the first winding end 5412A, in some embodiments, the third oil injection port 2611 includes a plurality of first sub-oil injection ports 2611A and a plurality of second sub-oil injection ports 2611B. The plurality of first sub-oil injection ports 2611A are uniformly arranged around the central axis of the first winding end heat exchange oil channel 261. The plurality of second sub-oil injection ports 2611B are also uniformly arranged around the central axis of the first winding end heat exchange oil channel 261, and the plurality of second sub-oil injection ports 2611B are arranged in the outer circle of the plurality of first sub-oil injection ports 2611A.

[0273] That is, the first winding end heat exchange oil channel 261 is provided with two circles of third oil injection ports 2611 around the central axis thereof, and the two circles of oil injection ports include: inner circle oil injection ports and outer circle oil injection ports, the inner circle oil injection ports are formed by the plurality of first sub-oil injection ports 2611A, and the outer circle oil injection ports are formed by the plurality of second sub-oil injection ports 2611B. The first sub-oil injection port 2611A and the second sub-oil injection port 2611B are both arranged towards the first winding end 5412A.

[0274] For example, the plurality of first sub-oil injection ports 2611A includes 12 first sub-oil injection ports 2611A, i.e., the first winding end heat exchange oil channel 261 can be provided with one first sub-oil injection port 2611A every 30° around the central axis thereof, and the 12 first sub-oil injection ports 2611A are concentric. The plurality of second sub-oil injection ports 2611B includes 12 second sub-oil injection ports 2611B, i.e., the second winding end heat exchange oil channel 262 can be provided with one second sub-oil injection port 2611B every 30° around the central axis thereof, and the 12 second sub-oil injection ports 2611B are concentric. In this way, the cooling oil is more uniformly directly sprayed on the first winding end 5412A, so as to achieve precise cooling of the first winding end 5412A.

[0275] In some embodiments, the extension line of the first sub-injection port 2611A intersects with the extension line of the second sub-injection port 2611B. The first sub-injection port 2611A and the second sub-injection port 2611B are both arranged towards the first winding end 5412A, so that when one sub-injection port is blocked, the other sub-injection port can still inject oil to cool down, avoiding the temperature rise of a certain position of the first winding end 5412A.

[0276] In other embodiments, the fourth injection port 2621 also includes a plurality of third sub-injection ports 2621A and a plurality of fourth sub-injection ports 2621B. The plurality of third sub-injection ports 2621A are uniformly arranged around the central axis of the second winding end heat exchange oil channel 262. The plurality of fourth sub-injection ports 2621B are also uniformly arranged around the central axis of the second winding end heat exchange oil channel 262, and the plurality of fourth sub-injection ports 2621B surround the outer circle of the plurality of third sub-injection ports 2621A.

[0277] For example, when the number of third injection ports 2611 is 24, one third injection port 2611 can be arranged every 15° around the central axis of the first winding end heat exchange oil channel 261. When the number of third injection ports 2611 is 30, one third injection port 2611 can be arranged every 12° around the central axis of the first winding end heat exchange oil channel 261. In this way, some embodiments of the present disclosure re-distribute the number and position of cooling injection ports according to the difference in heat generation between the crown end of the stator winding of the motor 54 and the soldered end of the stator winding of the motor 54, so that the cooling oil is more evenly sprayed directly onto the end of the stator winding 5412 to achieve precise cooling of the end of the stator winding 5412.

[0278] The extension line of the third sub-injection port 2621A can also intersect with the extension line of the fourth sub-injection port 2621B, and the specific beneficial effects can be referred to the description of the first sub-injection port 2611A and the second sub-injection port 2611B above, which will not be repeated here.

[0279] In some embodiments of the present disclosure, the stator heat exchange oil channel 26 further includes at least one stator core heat exchange oil channel, one end of the stator core heat exchange oil channel being in communication with the oil outlet hole 21D, at least part of the stator core heat exchange oil channel being arranged in the stator core 5411 and being arranged along the radial direction of the stator core 5411. In this way, the cooling oil flowing out of the oil outlet hole 21D can exchange heat with the stator core 5411 through the stator core heat exchange oil channel, thereby reducing the temperature of the stator core 5411.

[0280] In some embodiments, in the case that the at least one stator core heat exchange oil channel comprises a plurality of stator core heat exchange oil channels, the plurality of stator core heat exchange oil channels are uniformly arranged around the circumference of the stator core 5411. For example, if there are 9 stator core heat exchange oil channels, then 1 stator core heat exchange oil channel is arranged every 40° around the axial direction of the stator core 5411. In this way, uniform cooling of the stator core 5411 of the motor 54 can be achieved.

[0281] In other embodiments, the stator core heat exchange oil channels are arranged in multiple groups, and the multiple groups of stator core heat exchange oil channels are uniformly arranged along the axial direction of the stator core 5411. Any one of the multiple groups of stator core heat exchange oil channels comprises a plurality of stator core heat exchange oil channels uniformly arranged along the radial direction of the stator core 5411.

[0282] For example, if there are 20 groups of stator core heat exchange oil channels, then the 20 groups of stator core heat exchange oil channels are uniformly arranged along the central axis direction of the stator core 5411, and each group of stator core heat exchange oil channels comprises 9 stator core heat exchange oil channels arranged every 40° around the central axis direction of the stator core 5411. In this way, uniform cooling of the stator core 5411 of the motor 54 can be achieved, and local overheating of the stator 541 can be avoided.

[0283] FIG. 27 shows a structural diagram of the oil sump in FIG. 4. In some embodiments of the present disclosure, as shown in FIG. 27, the drive assembly 400 can further comprise an oil sump 65 arranged in the reduction box 1. The oil sump 65 forms an oil storage space 650 therein, at least part of the reduction assembly 4 is located in the oil storage space 650, and at least one through hole 651 is arranged on the bottom wall of the oil sump 65, which communicates with the oil storage space 650, so that the oil at the bottom of the reduction box 1 can flow into the oil storage space 650 through the through hole 651. At least part of the reduction assembly 4 forms at least part of the structure to be lubricated 3; and the at least one through hole 651 forms at least part of the oil guide structure 2. In this way, the oil at the bottom of the reduction box 1 can flow into the oil storage space 650 through the through hole 651 to lubricate the reduction assembly 4 in the oil storage space 650.

[0284] In some embodiments, as shown in FIG. 4, the reduction assembly 4 can include a differential gear 45 and a countershaft gear 44, the countershaft gear 44 can include a first countershaft driven gear 441 and a second countershaft driven gear 442, the differential gear 45 is engaged with the first countershaft driven gear 441, the first countershaft driven gear 441 is coaxially connected with the second countershaft driven gear 442, and the second countershaft driven gear 442 is configured to be engaged with a gear on the main shaft 41. In this way, when the main shaft 41 rotates, the second countershaft driven gear 442 is driven to rotate, and since the first countershaft driven gear 441 is coaxially connected with the second countershaft driven gear 442, the first countershaft driven gear 441 is also driven to rotate, thereby driving the differential gear 45 to rotate.

[0285] The oil sump 65 includes a first oil sump 652 and a second oil sump 653, both of which are arranged in the reduction box 1. The bottom of the first oil sump 652 is formed with a first oil storage space 6501, and the bottom of the first oil sump 652 is provided with a first through hole 6511. The differential gear 45 is arranged in the reduction box 1 and located in the first oil storage space 6501. The bottom of the second oil sump 653 is formed with a second oil storage space 6502, and the bottom of the second oil sump 653 is provided with a second through hole 6512. The second countershaft driven gear 442 is arranged in the reduction box 1 and located in the second oil storage space 6502.

[0286] In this way, the oil at the bottom of the reduction box 1 can enter the first oil storage space 6501 and the second oil storage space 6502 through the first through hole 6511 and the second through hole 6512, respectively, so that the differential gear 45 in the first oil storage space 6501 and the second countershaft driven gear 442 in the second oil storage space 6502 can be lubricated, respectively.

[0287] In some embodiments, the first oil sump 652 includes a first partition plate 6521, a second partition plate 6522, and a first bottom plate 6523. The first partition plate 6521 and the second partition plate 6522 are arranged at intervals, and the first bottom plate 6523 is connected to both the first partition plate 6521 and the second partition plate 6522. The first bottom plate 6523 is arranged around the circumference of the differential gear 45, i.e., the first bottom plate 6523 is bent and arranged around the circumference of the differential gear 45. The first oil storage space 6501 is arranged between the first partition plate 6521, the second partition plate 6522, and the first bottom plate 6523. The first through hole 6511 is arranged on the first bottom plate 6523.

[0288] In this way, the first oil sump 652 wraps the differential gear 45. Compared with the oil sump in the related art in which at least one side of the gear (differential gear) is not wrapped, the first oil sump 652 in some embodiments of the present disclosure can reduce the oil stirring loss of the differential gear 45.

[0289] In some embodiments, the second oil sump 653 comprises a third partition plate 6531, a fourth partition plate 6532, and a second bottom plate 6533, the third partition plate 6531 and the fourth partition plate 6532 are spaced apart, the second bottom plate 6533 is connected with the third partition plate 6531 and the fourth partition plate 6532, and the second bottom plate 6533 is disposed around the circumference of the second countershaft driven gear 442. That is, the first bottom plate 6523 is bent and disposed along the circumference of the second countershaft driven gear 442. The second oil storage space 6502 is arranged between the third partition plate 6531, the fourth partition plate 6532, and the second bottom plate 6533; and the second through hole 6512 is arranged on the second bottom plate 6533.

[0290] In this way, the second oil sump 653 wraps the second countershaft driven gear 442, and compared with the oil sump in the prior art in which at least one side (the second countershaft driven gear) of the gear is not wrapped, the second oil sump 653 in some embodiments of the present disclosure can reduce the oil stirring loss of the second countershaft driven gear 442.

[0291] In some embodiments, the first partition plate 6521, the first bottom plate 6523, and the fourth partition plate 6532 are an integral structure, and the second partition plate 6522, the second bottom plate 6533, and the third partition plate 6531 are an integral structure.

[0292] The first partition plate 6521, the first bottom plate 6523, and the fourth partition plate 6532 constitute the rear oil sump 65B, and the second partition plate 6522, the second bottom plate 6533, and the third partition plate 6531 constitute the front oil sump 65A. The front oil sump 65A is connected with the front case, the rear oil sump 65B is connected with the rear case, and the front oil sump 65A is further connected with the rear oil sump 65B.

[0293] The connection between the front oil sump 65A and the rear oil sump 65B can be positioned by the positioning pin 66 and the pin hole, and connected by the connecting bolt 67, which is not limited in the present disclosure.

[0294] In this way, the step of assembling the oil sump to the case can comprise:

[0295] 1. The positions of the front oil sump 65A and the front case are determined by the positioning pin and the pin hole arranged on the front oil sump 65A and the front case respectively, and the front oil sump 65A is fixed on the front case by the connecting bolt 67.

[0296] 2. The differential shaft 43, the differential gear 45, the countershaft 42, and the countershaft gear 44 are assembled to the front oil sump 65A and the front case.

[0297] 3. The rear oil sump 65B is fixed to the front oil sump 65A by the connecting bolt 67.

[0298] 4. The rear box is combined with the front box, and the rear box oil sump 65B is provided with a positioning pin 66 and a pin hole, which are used for positioning during combination.

[0299] In this way, the split oil sump 65 is simple to assemble, and can effectively avoid the problem that the full-coverage oil sump 65 must be installed together with the pinion shaft, and one side is blind, which leads to the problem that the installation of the oil sump 65 is too difficult.

[0300] In addition, the split oil sump 65 is positioned by the positioning pin 66 and the pin hole, and is connected by the connecting bolt 67, so that the pinion shaft (i.e., the differential shaft 43, the differential gear 45, the countershaft 42, and the countershaft gear 44) and the oil sump 65 are assembled separately. Compared with the clamping structure, the complexity of the structure and the manufacturing and assembly process are reduced. Moreover, the oil sumps 65 are connected by bolts, which can avoid quality problems such as stability compared with the clamping connection method.

[0301] In some embodiments, the second partition plate 6522 and the fourth partition plate 6532 are located in the same plane, and the first partition plate 6521 is located on the side of the second partition plate 6522 away from the third partition plate 6531 along the differential gear 45. That is, the first partition plate 6521 is arranged close to the front box, the third partition plate 6531 is arranged close to the rear box, and the second partition plate 6522 and the fourth partition plate 6532 are arranged between the first partition plate 6521 and the third partition plate 6531. In this way, the first oil sump 652 and the second oil sump 653 are arranged in a staggered manner.

[0302] As shown in FIGS. 4 and 27, since the differential gear 45 is engaged with the first countershaft driven gear 441, and the first countershaft driven gear 441 is coaxially arranged with the second countershaft driven gear 442, the differential gear 45 and the second countershaft driven gear 442 are arranged in a staggered manner. Some embodiments of the present disclosure arrange the first oil sump 652 and the second oil sump 653 in a staggered manner, so that the oil sump 65 avoids the first countershaft driven gear 441 arranged opposite to the differential gear 45 and engaged with the differential gear 45.

[0303] In addition, the first oil sump 652 can reduce the oil stirring loss of the differential gear 45, improve the lubrication effect of the differential gear 45, and further reduce the transmission wear between the differential gear 45 and the first countershaft driven gear 441. The second oil sump 653 can reduce the oil stirring loss of the second countershaft driven gear 442, improve the lubrication effect of the second countershaft driven gear 442, and further reduce the wear between the second countershaft driven gear 442 and the gear on the main shaft 41. In this way, by arranging the first oil sump 652 and the second oil sump 653, the transmission process from the differential gear 45 to the main shaft 41 can be effectively lubricated, and the service life of the drive assembly 400 can be improved.

[0304] Figure 28 shows a structural diagram of an oil sump and gear matching structure according to some embodiments of the present disclosure. In some embodiments, as shown in Figure 28, the drive assembly 400 further comprises a differential housing 68 and a differential assembly 69 (as shown in Figure 29) arranged in the differential housing 68. The differential housing 68 is coaxially connected with the differential gear 45, and the differential housing 68 is located on the side of the differential gear 45 away from the rear housing.

[0305] In addition, at least one second inlet 681 is formed in the circumferential wall of the differential housing 68 and communicates with the differential assembly 69. The second bottom plate 6533 is provided with an oil guide hole 6533A located between the second oil storage space 6502 and the second inlet 681 and communicating with the second oil storage space 6502, so that the oil agitated by the second pinion gear 442 flows into the second inlet 681 through the oil guide hole 6533A.

[0306] In this way, when the second pinion gear 442 rotates, the oil agitated by the second pinion gear 442 can flow into the second inlet 681 through the oil guide hole 6533A to lubricate the differential assembly 69 in the differential housing 68. In this way, the lubrication effect of the differential assembly 69 can be improved, and the problem of large oil demand in splash lubrication can be solved.

[0307] The oil guide hole 6533A can be arranged towards a first rotation center point, which is the rotation center point of the second inlet 681 on the differential housing 68. In this way, the oil can smoothly enter the inside of the differential housing 68.

[0308] Figure 29 shows an exploded view of a differential according to some embodiments of the present disclosure. In some embodiments of the present disclosure, the differential housing 68 defines an accommodation space, and the differential assembly 69 is arranged in the accommodation space. As shown in Figure 29, the differential assembly 69 can include a first planetary shaft 691, a first planetary gear 692, a first gasket 693, and a half shaft gear 694.

[0309] The first planetary shaft 691 is fixed on the differential housing 68 to rotate synchronously with the differential housing 68, and the first planetary gear 692 is arranged on the first planetary shaft 691 and is rotatable relative to the first planetary shaft 691. The first planetary shaft 691 is fixed on the differential housing 68 and rotates synchronously with the differential housing 68. That is, when the differential assembly 69 works, the first planetary gear 692 can rotate synchronously (i.e., revolution) with the differential housing 68 and the first planetary shaft 691, and at the same time, the first planetary gear 692 can also rotate relative to the first planetary shaft 691 (i.e., rotation).

[0310] It should be noted that the differential housing 68 can be open, and FIGS. 30 and 31 show structural diagrams of different perspectives of the upper differential housing in FIG. 29, and FIG. 32 shows a structural diagram of the lower differential housing in FIG. 29. As shown in FIGS. 30, 31 and 32, the differential housing 68 includes an upper differential housing 68A and a lower differential housing 68B. The upper differential housing 68A is provided with a plurality of threaded holes 68A1, and the lower differential housing 68B is provided opposite with a plurality of bolt through holes 68B1. The differential assembly 69 can further include a plurality of bolts 695. The plurality of bolts 695 pass through the plurality of bolt through holes 68B1 and are matched with the plurality of threaded holes 68A1 on the upper differential housing 68A, so as to connect the upper differential housing 68A and the lower differential housing 68B. In addition, the stop face 68B2 of the lower differential housing 68B is matched with the matching face 68A2 of the upper differential housing 68A.

[0311] The first gasket 693 is sleeved on the first planetary shaft 691 and located between the first planetary gear 692 and the differential housing 68. In this way, the arrangement of the first gasket 693 can effectively avoid the direct contact between the first planetary gear 692 and the differential housing 68, so as to avoid the wear of the first planetary gear 692 and the differential housing 68 caused by the contact friction therebetween when the first planetary gear 692 rotates relative to the first planetary shaft 691, thereby improving the reliability of the structure of the differential assembly 69 and prolonging the service life of the differential.

[0312] In addition, FIG. 33 shows a structural diagram of the first gasket in FIG. 29. As shown in FIG. 33, the first gasket 693 is provided with a first oil inlet hole 6931 on the surface facing the first planetary gear 692, and the half shaft gear 694 is arranged in the accommodation space and engaged with the first planetary gear 692. The half shaft gear 694 is arranged in the accommodation space and engaged with the first planetary gear 692. In this way, the reliable operation of the differential can be ensured.

[0313] When the differential is used in the vehicle 1000, the first planetary shaft 691 rotates synchronously with the rotation of the differential housing 68, thereby driving the first planetary gear 692 to revolve. Since the first planetary gear 692 is engaged with the half shaft gears 694, the half shaft gears 694 on both sides are driven to rotate, thereby driving the drive wheels on both sides of the vehicle 1000 to rotate.

[0314] When the vehicle 1000 runs on a flat road, the resistance received by the wheels 200 on both sides of the vehicle 1000 is equivalent, the engagement points of the first planetary gear 692 and the half shaft gears 694 on both sides receive the same force, so that the first planetary gear 692 only revolves.

[0315] When the vehicle 1000 is running on uneven road or turning, due to the different resistance received by the wheels 200 on both sides of the vehicle 1000, the feedback of the resistance makes the engagement points of the first planetary gear 692 and the half shaft gears 694 on both sides receive different forces, and further makes the first planetary gear 692 not only revolve but also rotate under the action of the force difference, and further makes the rotation speeds of the half shaft gears 694 on both sides of the first planetary gear 692 different, so that the rotation speeds of the wheels 200 on both sides of the vehicle 1000 are different, thereby making the vehicle 1000 reliably run on uneven road or smoothly turn, and improving the reliability of the vehicle 1000.

[0316] In addition, by providing the first oil inlet hole 6931 on the surface of the first gasket 693 facing the planetary gear, the oil entering from the second inlet 681 can enter through the first oil inlet hole 6931 to lubricate the first gasket 693 and the planetary gear, and reduce the dry grinding phenomenon between the first gasket 693 and the first planetary gear 692. At the same time, it can also lubricate the first planetary gear 692 and the first planetary shaft 691 to a certain extent, and reduce the wear between the first planetary gear 692 and the first planetary shaft 691. Further improve the reliability of the differential assembly 69, which is beneficial to prolong the service life of the differential.

[0317] In some embodiments, as shown in FIG. 34, the circumferential wall of the first planetary shaft 691 is provided with a first limiting portion 6911, and the inner ring 6932 of the first gasket 693 cooperates with the first limiting portion 6911 to limit the circumferential rotation of the first gasket 693 around the first planetary shaft 691.

[0318] The cross section of the first limiting portion 6911 can be a polygon, or a shape formed by connecting curves and straight lines, and the inner ring 6932 of the first gasket 693 can be a polygon hole matched with the polygon. The first limiting portion 6911 can be a milled plane.

[0319] In this way, the rotation of the first gasket 693 relative to the first planetary shaft 691 can be prevented, and the relative stillness of the first gasket 693 and the first planetary shaft 691 can be ensured, avoiding the friction and wear problems caused by the relative rotation of the first gasket 693 and the differential housing 68, ensuring the quietness and stability of the differential, and improving the service life of the differential. In addition, when the first gasket 693 and the differential housing 68 are relatively still, the lubricating oil of the second inlet 681 can pass through the first oil inlet hole 6931 to lubricate the first gasket 693 and the first planetary gear 692, and reduce the dry grinding phenomenon between the first gasket 693 and the first planetary gear 692. At the same time, it can also lubricate the first planetary gear 692 and the first planetary shaft 691 to a certain extent, and reduce the wear between the first planetary gear 692 and the first planetary shaft 691.

[0320] In some embodiments, the first planet shaft 691 can be provided with a protrusion, and the inner ring 6932 of the first washer 693 is provided with a groove matched with the protrusion, and the protrusion and the groove are matched to limit the circumferential rotation of the first washer 693 around the first planet shaft 691. Thus, the friction and wear problems caused by the relative rotation of the first washer 693 and the differential housing 68 are avoided.

[0321] In order to fix the first planet shaft 691, in some embodiments, as shown in FIGS. 29, 31 and 34, the differential housing 68 is provided with a first elastic pin hole 68A3, and the first planet shaft 691 is provided with a second elastic pin hole 6912. The differential assembly 69 further comprises a first elastic pin 696 matched with the second elastic pin hole 6912 and the first elastic pin hole 68A3 to fix the first planet shaft 691.

[0322] In this way, the first planet shaft 691 is fixed on the differential housing 68 by matching the first elastic pin 696, the second elastic pin hole 6912 and the first elastic pin hole 68A3.

[0323] FIG. 35 shows a schematic view of the retainer in FIG. 29. In some embodiments, as shown in FIGS. 29 and 35, the differential assembly 69 further comprises a retainer 697 provided on the side of the first washer 693 away from the first planet gear 692, and the retainer 697 is provided with a through hole 6971, and the first limiting portion 6911 of the first planet shaft 691 is at least partially located in the through hole 6971. The first limiting portion 6911 and the through hole 6971 are matched to limit the rotation of the first planet shaft 691 around the axis direction thereof.

[0324] The cross section of the first limiting portion 6911 can be a polygon, or a shape formed by connecting a curve and a straight line, and the through hole 6971 can be a polygon hole matched with the polygon.

[0325] In this way, the retainer 697 can prevent the rotation of the first planet shaft 691, thereby reducing the tendency of the first elastic pin 696 to be sheared and broken.

[0326] To improve the stability of the differential operation, as shown in FIG. 29 and FIG. 36, in some embodiments, the differential assembly 69 can further include a second planetary shaft 6981, a second planetary gear 6982 and a second gasket 6983. The second planetary shaft 6981 is arranged perpendicularly to the first planetary shaft 691, and the second planetary shaft 6981 is also fixed on the differential housing 68 to rotate synchronously with the differential housing 68. The second gasket 6983 is sleeved on the second planetary shaft 6981, and is located between the second planetary gear 6982 and the differential housing 68, and the surface of the second gasket 6983 facing the second planetary gear 6982 is provided with a second oil inlet hole. The second planetary gear 6982 is also engaged with the half shaft gear 694. The second gasket 6983 is located on the side of the second planetary gear 6982 away from the retainer 697.

[0327] In this way, when the vehicle 1000 is driving on uneven road or turning, due to the different resistance received by the wheels 200 on both sides of the vehicle 1000, the engagement points of the first planetary gear 692 and the second planetary gear 6982 with the half shaft gears 694 on both sides are subjected to different forces through the feedback of the resistance, so that the first planetary gear 692 and the second planetary gear 6982 not only revolve, but also rotate under the action of the force difference. The cooperation of the first planetary gear 692 and the second planetary gear 6982 makes the rotation speeds of the half shaft gears 694 on both sides of the first planetary gear 692 different, thereby improving the stability of the differential operation.

[0328] In some embodiments, the circumferential wall surface of the second planetary shaft 6981 is provided with a second limiting portion 6981A, and the inner ring of the second gasket 6983 cooperates with the second limiting portion 6981A to limit the circumferential rotation of the second gasket 6983 around the second planetary shaft 6981.

[0329] Similarly, the cooperation of the second limiting portion 6981A and the second gasket 6983 can refer to the cooperation of the first limiting portion 6911 and the first gasket 693 described above, and the present disclosure will not repeat it here.

[0330] In this way, the second gasket 6983 can be prevented from rotating relative to the second planetary shaft 6981, ensuring that the second gasket 6983 and the second planetary shaft 6981 are relatively stationary, avoiding friction and wear caused by relative rotation of the second gasket 6983 and the differential housing 68, ensuring the quietness and stability of the differential, and improving the service life of the differential. In addition, when the second gasket 6983 is relatively stationary with the differential housing 68, the lubricating oil of the second inlet 681 can pass through the second oil inlet hole to lubricate the second gasket 6983 and the second planetary gear 6982, thereby reducing dry grinding between the second gasket 6983 and the second planetary gear 6982. At the same time, it can also lubricate the second planetary gear 6982 and the second planetary shaft 6981 to some extent, reducing wear between the second planetary gear 6982 and the second planetary shaft 6981.

[0331] In other embodiments, as shown in FIG. 35, the cage 697 is provided with a connecting hole 6972, which can be arranged vertically with the through hole 6971, and the second limiting portion 6981A of the second planetary shaft 6981 is at least partially located in the connecting hole 6972. The second limiting portion 6981A cooperates with the connecting hole 6972 to limit the rotation of the second planetary shaft 6981 about its axis.

[0332] The cooperation between the connecting hole 6972 and the second limiting portion 6981A can refer to the cooperation between the through hole 6971 and the first limiting portion 6911 described above, and the present disclosure does not limit it.

[0333] In some embodiments, the surfaces of the first planetary shaft, the second planetary shaft 6981, the first gasket 693, and the second gasket 6983 can be provided with a coating, which can be a high-hardness material. For example, the coating material can be a hard alloy coating, such as a tungsten-cobalt or titanium-cobalt coating formed by mixing metal powder and a certain binder. The coating material can also be a diamond coating, and the present disclosure does not limit it.

[0334] In this way, the surface hardness and wear resistance of the first planetary shaft 691, the second planetary shaft 6981, the first gasket 693, and the second gasket 6983 can be improved.

[0335] FIG. 37 shows a structure diagram of an oil pump arranged on the front tank according to some embodiments of the present disclosure, and FIG. 38 is a structure diagram of the oil pump in FIG. 37. In some embodiments of the present disclosure, as shown in FIGS. 37 and 38, the drive assembly 400 further includes an oil pump 70, which can be arranged on the oil pan 65. For example, the oil pump 70 can be arranged on the front tank oil pan 65A. For another example, the oil pump 70 can also be arranged on the rear tank oil pan 65B.

[0336] In addition, the oil suction pipe 70 is provided with a plurality of oil suction ports 701, which are used to suck the oil in the reduction gearbox 1 into the oil suction pipe 70 and then into the oil guide structure 2.

[0337] That is, the plurality of oil suction pipes 70 can be in communication with the oil pump 6 through the main channel 2101, so that the oil can flow through the oil suction ports 701, the plurality of oil suction pipes 70, the main channel 2101, and the oil pump 6 in sequence, and be pumped out by the oil pump 6 to the oil cooler 60, flow into the branch channel 2102 from the oil outlet of the oil cooler 60, and finally flow to the lubricated structure 3.

[0338] In some embodiments, the plurality of oil suction pipes 70 can be integrally arranged on the oil pan 65. In this way, the oil suction pipe 70 does not need to be additionally arranged and installed, which can improve the space utilization of the drive assembly 400, reduce the installation process of the drive assembly 400, and improve the assembly efficiency.

[0339] In some embodiments, the opening area of the oil suction port 701 is greater than or equal to 320 square millimeters, so that the oil suction amount of the oil pump 6 can be sufficient for lubricating the lubricated components.

[0340] In some embodiments, the drive assembly 400 can further include a suction filter 71, which is mainly used to remove impurities in the oil to maintain the cleanliness of the oil and prolong the service life of the reduction gearbox 1. The suction filter 71 effectively removes solid particles, sludge, iron filings and other impurities in the oil through internal filter paper or filter screen and other filter media, so that the oil remains clean. In this way, clean oil can reduce the wear of the friction surface of the lubricated structure 3, improve the transmission efficiency, and reduce noise and vibration.

[0341] As shown in FIG. 38, the suction filter 71 can be integrally arranged in the plurality of oil suction pipes 70, so that the oil can flow through the oil suction ports 701, the plurality of oil suction pipes 70, pass through the suction filter 71, and then flow into the oil pump 6 through the main channel 2101, and be pumped out by the oil pump 6 to the oil cooler 60, flow into the branch channel 2102 from the oil outlet of the oil cooler 60, and finally flow to the lubricated structure 3.

[0342] In addition, by integrally arranging the oil pipe in the plurality of oil suction pipes 70, the problems of misloading and assembly difficulty can be effectively avoided, and the production efficiency of the drive assembly 400 is improved.

[0343] In some embodiments, the plurality of oil suction ports 701 can include a first oil suction port 7011 and a second oil suction port 7012, and the first oil suction port 7011 is arranged perpendicular to the bottom wall in the reduction gearbox 1. The included angle between the first oil suction port 7011 and the second oil suction port 7012 is greater than or equal to 73.5° and less than or equal to 147°. In this way, it can be ensured that the oil pump 6 can normally suck oil under uphill and downhill working conditions through the oil suction port 701.

[0344] Figure 39 shows a cross-sectional view of an oil suction tube of some embodiments of the present disclosure arranged in a reduction box, in order to further ensure that the oil pump 6 can normally suck oil through the oil suction port 701 in uphill and downhill working conditions, in some embodiments, as shown in Figure 39, the first oil suction port 7011 and the second oil suction port 7012 are arranged close to the bottom wall in the reduction box 1, so that the first oil suction port 7011 and the second oil suction port 7012 are close to the bottom wall of the reduction box 1, which can ensure that the oil pump 6 can normally suck oil through the oil suction port 701.

[0345] In some embodiments, as shown in Figure 39, a concave oil storage groove 14 is arranged on the bottom wall of the reduction box 1, and the concave oil storage groove 14 is arranged directly below the oil suction port 701.

[0346] In this way, when the vehicle 1000 is rapidly decelerated, as shown in Figure 40, the oil at the bottom of the reduction box 1 is shaken violently, and when the oil is tilted forward to the A area in Figure 40, the concave oil storage groove 14 can still store part of the oil, thereby effectively preventing the oil suction port 701 from being temporarily sucked by the vehicle 1000 during rapid deceleration.

[0347] When the vehicle is rapidly accelerated, as shown in Figure 41, the oil at the bottom of the reduction box 1 is shaken violently, and when the oil is tilted backward to the B area in Figure 41, the concave oil storage groove 14 can still store part of the oil, thereby effectively preventing the oil suction port 701 from being temporarily sucked by the vehicle 1000 during rapid acceleration.

[0348] In some embodiments, as shown in Figure 39, the concave oil storage groove 14 can include a first concave oil storage groove 141 and a second concave oil storage groove 142, the first concave oil storage groove 141 is arranged directly below the first oil suction port 7011, and the second concave oil storage groove 142 is arranged directly below the second oil suction port 7012. In this way, the concave oil storage groove 14 is arranged directly below the first oil suction port 7011 and the second oil suction port 7012, which can effectively prevent the first oil suction port 7011 and the second oil suction port 7012 from being temporarily sucked by the vehicle 1000 during rapid acceleration or rapid deceleration.

[0349] In other embodiments, the oil suction port 701 can also include a first oil suction port 7011, a second oil suction port 7012, and a third oil suction port, the installation angle of the first oil suction port 7011, the second oil suction port 7012, and the third oil suction port can be adjusted according to the installation angle of the reduction box 1, which is not limited by the present disclosure. In this way, by arranging three oil suction ports 701, the stability of the oil pump 6 can be ensured for larger reduction boxes 1. In addition, in some embodiments, the oil suction port 701 can also be provided with four, five or six oil suction ports, which are not limited by the present disclosure.

[0350] It can be understood that the oil circulating in the reduction gearbox 1 usually contains impurities, metal debris, tiny particles and other contaminants. If these impurities remain in the oil, they can cause wear and tear to the gears, bearings and other precision components in the reduction gearbox 1, and even cause failure. Therefore, in order to improve the cleanliness of the oil, in some embodiments of the present disclosure, as shown in FIG. 14, the drive assembly 400 can further include a fine filter 72, which is arranged on the oil guide channel 21 and between the oil pump 6 and the oil cooler 60. That is, the fine filter 72 is arranged on the main channel 2101 and communicates with the oil pump 6 and the oil cooler 60 at both ends.

[0351] The fine filter 72 is used to filter out impurities, metal debris, tiny particles and other contaminants in the oil, improve the cleanliness of the oil, and protect the precision components inside the drive assembly 400, such as gears, bearings, etc., thereby prolonging the service life of the drive assembly 400. The fine filter 72 can be made of high-quality filter material, such as stainless steel fiber mesh, glass fiber or synthetic fiber, etc. In this way, the fine filter 72 can filter out tiny particles and impurities in the oil, ensuring the purity of the oil.

[0352] In this way, the oil pumped out by the oil pump 6 can be filtered by the fine filter 72 before flowing into the oil cooler 60, and finally flowing out from the outlet of the oil cooler 60 to the lubricated structure 3, which can reduce the wear of the lubricated structure 3 and improve the service life of the lubricated structure 3.

[0353] FIG. 42 shows a structural diagram of a fine filter according to some embodiments of the present disclosure, FIG. 43 shows a structural diagram of a fine filter mounted on a reduction gearbox according to some embodiments of the present disclosure, and FIG. 44 shows a radial cross-sectional view of a fine filter according to some embodiments of the present disclosure. In some embodiments of the present disclosure, as shown in FIGS. 42, 43 and 44, the reduction gearbox 1 is provided with a fine filter accommodating cavity 15 in the body, and the body of the reduction gearbox 1 is further provided with an opening 16, which communicates with the fine filter accommodating cavity 15.

[0354] The fine filter 72 can include a fine filter element 721 and a cover 722, the fine filter element 721 is connected with the cover 722, the fine filter element 721 is arranged in the fine filter accommodating cavity 15, and the cover 722 is used to block the opening 16. The fine filter element 721 is responsible for filtering impurities, metal debris, tiny particles and contaminants in the oil, ensuring the cleanliness of the oil, and the material of the fine filter element 721 can be stainless steel fiber mesh, glass fiber, synthetic fiber, etc. In this way, the fine filter element 721 has good filtering performance and wear resistance, and can effectively remove tiny particles and impurities in the oil.

[0355] In addition, the cover 722 is provided with an oil inlet 7221 and an oil outlet 7222. The oil inlet 7221 is communicated with the oil pump 6, and the oil outlet 7222 is communicated with the oil cooler 60. In this way, by providing the fine filter containing cavity 15 on the reduction gearbox 1, the fine filter is integrated in the reduction gearbox 1, which can effectively avoid the problem of oil leakage, and the structure is a maintenance-free design, which can save replacement costs, and compared with the related art, the design demand of low cost and easy assembly is better met. The fine filter containing cavity 15 is integrated with the reduction gearbox 1, which can improve the structural rigidity and noise, vibration and harshness (NVH) performance of the drive assembly 400.

[0356] In some embodiments, the fine filter 72 can further include a sealing ring 723 arranged between the cover 722 and the wall surface surrounding the opening 16. The sealing ring 723 can be composed of an elastic material, which can be a rubber sealing ring, a metal sealing ring, a plastic sealing ring, a hydraulic sealing ring, etc., which is not limited in the present disclosure. In this way, by arranging the sealing ring 723 between the opening 16 and the cover 722, the sealing effect of the fine filter containing cavity 15 can be improved, and the oil in the fine filter containing cavity 15 can be prevented from leaking between the cover 722 and the wall surface surrounding the opening 16.

[0357] FIG. 45 shows a cross-sectional view of an oil pump integrated on a reduction gearbox according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 45, the oil pump 6 can be arranged on the front case 1A, and the oil pump inlet 6A can be communicated with the oil outlet of the fine filter 72.

[0358] In addition, FIG. 46 shows a structural view of a reduction gearbox according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 46, the oil cooler 60, the oil pump 6 and the fine filter containing cavity 15 can all be arranged on the front case 1A.

[0359] The oil cooler 60 is fixedly arranged on the front case 1A and can be fixedly connected with the front case 1A by clamping, bolt connection or the like. The oil cooler 60 is located outside the front case 1A. The oil cooler 60 can exchange heat with the oil flowing therethrough. The oil pump 6 is fixedly arranged on the front case 1A and can be fixedly connected with the front case 1A by clamping, bolt connection or the like. The front case 1A is provided with the fine filter containing cavity 15, which can also be located outside the front case 1A. The fine filter element 721 and the cover 722 can be fixedly connected with the front case 1A at the fine filter containing cavity 15 by clamping, bolt connection or the like.

[0360] The oil pump 6 and the fine filter 72 are both located outside the front case 1A. The oil cooler 60, the oil pump 6 and the fine filter 72 are all located on the oil flow path, and the oil can flow through the oil cooler 60, the oil pump 6 and the fine filter 72.

[0361] As an embodiment, the oil flow path can be configured such that the oil is driven by the oil pump 6 and sequentially flows to the fine filter 72 and the oil cooler 60. The oil pump 6 can drive the oil in the front tank 1A to flow along the oil flow path, the oil can flow along the oil flow path to the oil cooler 60, the oil pump 6 and the fine filter 72, the oil can be driven by the oil pump 6 to flow through the oil pump 6, the oil can flow to the fine filter 72 and be filtered in the fine filter 72, and the oil can flow to the oil cooler 60 and be cooled by heat exchange in the oil cooler 60.

[0362] Since the oil cooler 60, the oil pump 6 and the fine filter 72 are all located on the front tank 1A, the overall structure of the oil cooler 60, the oil pump 6 and the fine filter 72 is compact, which is conducive to improving the structural compactness of the drive assembly 400, reducing the space occupation of the drive assembly 400, and improving the space utilization of the vehicle.

[0363] FIG. 47 shows a sectional view of the reduction gearbox in FIG. 46. In some embodiments, as shown in FIG. 47, the oil guide channel 21 includes an integrated oil pipe 214 that sequentially connects the oil pump 6, the fine filter 72 and the oil cooler 60, i.e., at least part of the main channel 2101 is formed in the integrated oil pipe 214.

[0364] The material of the integrated oil pipe 214 can be rubber, metal, composite material, etc., which is not limited in the present disclosure.

[0365] In this way, the layout of the oil passage in the reduction gearbox 1 can be reduced, the manufacturing cost of the gearbox can be reduced, and the structural rigidity of the reduction gearbox 1 can be further improved.

[0366] In other embodiments, as shown in FIG. 46, the multi-way valve 62 is arranged on the front tank 1A. The multi-way valve 62 can be integrally arranged on the front tank 1A, i.e., the first inlet 621, the first outlet 622 and the second outlet 623 are connected and arranged on the front tank 1A, and the valve core of the multi-way valve is arranged at the first inlet 621, the first outlet 622 and the second outlet 623 to realize the connection between the first inlet 621 and the first outlet 622 or the connection between the first inlet 621 and the second outlet 623. In this way, the overall structural arrangement of the drive assembly 400 is compact, and the space utilization is improved.

[0367] FIG. 48 shows a front view of a drive assembly gearbox according to an embodiment of the present disclosure. In some embodiments of the present disclosure, the drive assembly gearbox can include an integrated motor gearbox 55 and a reduction gearbox 1. The motor gearbox 55 can include a motor housing 551 and a motor rear end cover 552, the motor rear end cover 552 is connected with the motor housing 551 and located on the side of the motor housing 551 away from the reduction gearbox 1.

[0368] The front case 1A and the rear case 1B are both provided with suspension holes 73. As shown in FIG. 48, the front case 1A is provided with a first suspension hole 731 and a second suspension hole 732, and the rear case 1B is provided with a third suspension hole 733. In addition, the motor rear end cover 552 is provided with a fourth suspension hole 734, a fifth suspension hole 735, a sixth suspension hole 736, and a seventh suspension hole 737.

[0369] The plurality of suspension holes 73 are used to connect with different types of suspensions, improve the compatibility of the drive assembly case, and the arrangement of the suspension structure is more flexible.

[0370] In order to improve the strength of the suspension hole 73, in some embodiments, as shown in FIG. 48, a plurality of reinforcing ribs 74 are arranged beside the suspension hole 73, so that the strength of the suspension hole can be improved by arranging the reinforcing ribs 74.

[0371] FIG. 49 shows a schematic diagram of a drive assembly case with a channel according to some embodiments of the present disclosure, and FIG. 50 shows a cross-sectional view of a suspension hole and an oil channel according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 49 and FIG. 50, the front case 1A is provided with an oil channel 75, which can include a first oil channel 751, a second oil channel 752, and a third oil channel 753.

[0372] The first oil channel 751, the second oil channel 752, and the third oil channel 753 are arranged perpendicularly to the reinforcing ribs 74 at the oil channel 75 on the reduction case 1. The oil channel 75 can be the first oil guide channel segment 211, the second oil guide channel segment 212, and the third oil guide channel segment 213 described above, and the oil channel can also be other oil guide channels 21, which are not limited by the present disclosure. In this way, by arranging the reinforcing ribs 74 and the oil channel 75 crossly, the strength of the periphery of the suspension hole 73 is increased, while the use of the reinforcing ribs 74 is reduced, and the reliability and durability of the entire drive assembly 400 are increased.

[0373] In understanding the scope of the present disclosure, the term "comprising" and its derivatives, as used herein, are intended to be open-ended terms that specify the presence of the stated features, elements, components, groups, integers, and / or steps, but do not exclude the presence of other unstated features, elements, components, groups, integers and / or steps. The foregoing also applies to like-terms, such as "comprise," "have," "include," and "contain," among others.

[0374] The term "attached" or "attaching" as used herein includes configurations in which an element is directly secured to another element by affixing the element directly to the other element; configurations in which the element is indirectly secured to the other element by affixing the element to intermediate member(s) which in turn are affixed to the other element; and configurations in which one element is integral with the other element, i.e., one element is essentially a part of the other element. The definition also applies to words of similar meaning, for example, "connected", "coupled", "coupling", "mounting", "bonding", "fixing", and their derivatives. Finally, degree terms such as "substantially" "about" and "approximately" as used herein mean an acceptable quantity of deviation from the stated condition so that the end result is not significantly changed.

[0375] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of this disclosure. The features described herein in one embodiment can be applied to another embodiment, either singly or in combination, unless the features are not applicable or are otherwise stated.

[0376] The present disclosure has been described above by way of the embodiments, but it should be understood that the embodiments described above are merely by way of illustration and example and are not intended to limit the present disclosure to the precise details thereof. Moreover, it is to be understood that the present disclosure is not limited to the embodiments described above, but many variations and modifications of the embodiments described above can be made in accordance with the teachings of the present disclosure, which fall within the scope of the present disclosure.

Claims

1. A drive assembly (400) comprising a reduction box (1), an oil guiding structure (2) and a structure to be lubricated (3); the oil guiding structure (2) is connected between the reduction box (1) and the structure to be lubricated (3).

2. The drive assembly (400) according to claim 1, further comprising a reduction assembly (4) and a main shaft bearing (31), the reduction assembly (4) is arranged in the reduction box (1); the reduction assembly (4) comprises a main shaft (41), the reduction box (1) is provided with a main shaft mounting hole (11), part of the main shaft (41) is accommodated in the main shaft mounting hole (11), and the main shaft bearing (31) is arranged between the main shaft (41) and the inner wall surface of the main shaft mounting hole (11), the main shaft bearing (31) forms at least part of the structure to be lubricated (3); the oil guiding structure (2) comprises an oil guiding channel (21), the oil guiding channel (21) is provided with an oil inlet (21A) and a first oil outlet (21B), the oil inlet (21A) is communicated with the reduction box (1), and the first oil outlet (21B) is opposite to the main shaft bearing (31). The oil guiding channel (21) comprises a first oil guiding channel section (211), the first oil guiding channel section (211) and the first oil outlet (21B) are arranged in the reduction box (1), and the first oil outlet (21B) is arranged in the first oil guiding channel section (211).

3. The drive assembly (400) of claim 2, wherein, 4. The drive assembly (400) according to any one of claims 1 to 3, further comprising a motor (54), a motor box (55) and a motor bearing (56), the motor (54) comprises an output shaft, the motor box (55) is provided with an output shaft mounting hole, part of the output shaft is accommodated in the output shaft mounting hole, and the motor bearing (56) is arranged between the output shaft and the inner wall surface of the output shaft mounting hole, the motor bearing (56) forms at least part of the structure to be lubricated (3); the oil guiding structure (2) comprises an oil guiding channel (21), the oil guiding channel (21) is provided with an oil inlet (21A) and a second oil outlet (21C), the oil inlet (21A) is communicated with the reduction box (1), and the second oil outlet (21C) is opposite to the motor bearing (56). The oil guiding channel (21) comprises a second oil guiding channel section (212), the second oil guiding channel section (212) and the second oil outlet (21C) are arranged in the motor box (55), and the second oil outlet (21C) is arranged in the second oil guiding channel section (212).

6. The drive assembly (400) according to claim 5, further comprising a motor bearing seat (57), the motor bearing seat (57) is arranged in the motor box (55), the motor bearing seat (57) is arranged between the motor bearing (56) and the inner wall surface of the output shaft mounting hole, and is connected with the motor bearing (56).

5. The drive assembly (400) of claim 4, wherein, ​ ​ The motor bearing seat (57) is provided with a first avoiding opening (571) facing the motor bearing (56), and the second oil injection opening (21C) is arranged towards the first avoiding opening (571).

7. The drive assembly (400) according to any one of claims 1-6, further comprising a main shaft (41), a secondary shaft (42), a differential shaft (43) and an oil guide (50) arranged in the reduction box (1), the main shaft (41) being in driving connection with the secondary shaft (42), the secondary shaft (42) being arranged between the main shaft (41) and the differential shaft (43) and in driving connection with the differential shaft (43); the secondary shaft (42) being provided with a secondary shaft gear (44), and the differential shaft (43) being provided with a differential gear (45); The oil guide (50) is arranged between the differential shaft (43) and the main shaft (41), and the oil guide (50) comprises a first oil guiding portion (501) configured to, when the differential gear (45) and the secondary shaft gear (44) operate to splash oil, splash part of the oil onto the first oil guiding portion (501) and transfer the oil to the main shaft (41) through the first oil guiding portion (501).

8. The drive assembly (400) according to any one of claims 1 to 7, further comprising: A motor (54) and a motor box (55), the motor (54) being arranged in the motor box (55); The motor (54) comprises a stator (541) and a rotor (542), the stator (541) and the rotor (542) are coaxially arranged, and the stator (541) is nested outside the rotor (542); The oil guide structure (2) comprises an oil guide channel (21), the oil guide channel (21) is provided with an oil inlet (21A) and an oil outlet (21D), and the oil inlet (21A) is in communication with the reduction box (1); The oil guide structure (2) further comprises a rotor heat exchange oil channel (25), the rotor heat exchange oil channel (25) is in communication with the oil outlet (21D); the rotor heat exchange oil channel (25) is configured to exchange heat with the rotor (542) to carry away heat of the rotor (542).

9. The drive assembly (400) according to any one of claims 1 to 8, wherein, The drive assembly further comprises an oil sump (65) and a reduction assembly (4); The oil sump (65) is arranged in the reduction box (1), and an oil storage space (650) is formed in the oil sump (65); the reduction assembly (4) is arranged in the reduction box (1), and at least part of the reduction assembly (4) is located in the oil storage space (650); a bottom wall of the oil sump (65) is provided with at least one through hole (651); The at least part of the reduction assembly (4) forms at least part of the structure (3) to be lubricated; and the at least one through hole (651) forms at least part of the oil guide structure (2).

10. A vehicle (1000) comprising the drive assembly (400) according to any one of claims 1-9.

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