Power assembly and vehicle

Abstract

The invention provides a power assembly and a vehicle, relates to the technical field of power assemblies, and aims to improve the lubricating effect of some bearings and / or gear teeth in the power assembly. A bearing chamber is arranged in a shell of the power assembly, a motor shaft of a motor in the power assembly penetrates through the bearing chamber and extends into a planet carrier of a planetary reducer in the power assembly, the part, facing one side of the motor, of the planet carrier extends into the bearing chamber, one bearing in the bearing chamber is used for being connected with the part, extending into the bearing chamber, of the planet carrier, and the other bearing is used for being connected with the motor shaft. Wherein the motor shaft comprises a plurality of first holes, the plurality of first holes are used for outputting oil in a shaft cavity of the motor shaft, a gap is formed between the motor shaft and the part, extending into the bearing chamber, of the planet carrier, and the gap is used for communicating the plurality of first holes with the bearing chamber. By means of the gap, oil output by the multiple first holes of the motor shaft can flow to the bearing chamber, two bearings in the bearing chamber are lubricated, and the lubricating effect of the two bearings is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of powertrains, in particular to a powertrain and a vehicle. BACKGROUND

[0002] In the new energy vehicle industry, the powertrain is the main power source of the vehicle. Among them, the motor is an important part of the powertrain, which is used to provide high-speed kinetic energy; the planetary reducer is another important part of the powertrain, which is used to convert high-speed kinetic energy into greater torque output. However, in the current powertrain, some bearings and / or gear teeth have the problem of insufficient lubrication, which may cause the planetary reducer to wear seriously, reduce the service life of the planetary reducer, and negatively affect the normal operation of the powertrain. SUMMARY

[0003] The purpose of the present application is to provide a powertrain and a vehicle for improving the lubrication effect of some bearings and / or gear teeth in the powertrain.

[0004] To achieve the above-mentioned purpose, the present application adopts the following technical scheme:

[0005] In a first aspect, the embodiments of the present application provide a powertrain, the housing of the powertrain includes a bearing chamber, the motor shaft of the motor in the powertrain passes through the bearing chamber and extends into the planet carrier of the planetary reducer in the powertrain, the part of the planet carrier towards the motor side extends into the bearing chamber, one bearing in the bearing chamber is used to connect the part of the planet carrier extending into the bearing chamber, and another bearing is used to connect the motor shaft. Wherein: the motor shaft includes a plurality of first holes, the plurality of first holes are used to output the oil in the shaft cavity of the motor shaft, and one gap is included between the motor shaft and the part of the planet carrier extending into the bearing chamber, the one gap is used to communicate the plurality of first holes and the bearing chamber.

[0006] In the powertrain provided by the embodiments of the present application, the housing includes a bearing chamber accommodating two bearings, one of which connects the part of the planet carrier extending into the bearing chamber, and the other of which connects the part of the motor shaft extending into the bearing chamber, and one gap is included between the part of the planet carrier extending into the bearing chamber and the motor shaft. The oil output by the plurality of first holes of the motor shaft can flow to the bearing chamber through the one gap, so as to lubricate the two bearings in the bearing chamber and improve the lubrication effect of the two bearings.

[0007] In order to meet the needs of the vehicle in the driving process, the motor outputs high-speed kinetic energy, and the planetary reducer converts the high-speed kinetic energy into greater torque output, which makes the one bearing connected by the planet carrier and the other bearing connected by the motor shaft very easy to wear out.

[0008] Since the torque of the output shaft of the planet carrier in the planetary reducer is usually large, the bearing connected to the planet carrier is heavily loaded, in particular, the high torque directly increases the radial and axial load of the bearing, which easily causes raceway deformation, roller edge stress concentration, and accelerates fatigue wear. In the embodiments of the present application, the gap enables the oil output from the plurality of first holes of the motor shaft to flow to the bearing chamber, thereby achieving sufficient lubrication of the bearing connected to the planet carrier, so as to reduce the heavy load friction of the bearing, improve the problem of accelerated wear of the bearing caused by high torque, and prolong the service life of the bearing.

[0009] Since the rotating speed of the motor shaft in the motor is usually high, the motor shaft drives another bearing to rotate at high speed, which causes the bearing to generate more heat by friction, the lubrication to fail easily, and the bearing to wear out quickly. In the embodiments of the present application, the gap enables the oil output from the plurality of first holes of the motor shaft to flow to the bearing chamber, thereby achieving sufficient lubrication of the other bearing connected to the motor shaft, so as to reduce the friction and enhance the heat dissipation of the other bearing, improve the problem of easy lubrication failure and accelerated wear of the other bearing caused by high speed, and prolong the service life of the other bearing.

[0010] Through the lubrication of the above two bearings, the running stability of the motor shaft and the planet carrier is better, which is conducive to improving the service life of the motor and the planetary reducer and ensuring the long-term stable operation of the power assembly.

[0011] In the embodiments of the present application, the bearing chamber is constructed in the housing by using a part of the housing, and the gap between the part of the planet carrier extending into the bearing chamber and the part of the motor shaft extending into the bearing chamber is used to transmit oil to the bearing chamber, without the need to increase other additional components to lubricate the two bearings in the bearing chamber. Therefore, while improving the service life of the two bearings and the motor and the planetary reducer, the structure of the power assembly is also more compact, which is conducive to the miniaturization design of the power assembly.

[0012] In one embodiment, the inner circumferential surface of the part of the planet carrier extending into the bearing chamber has a trumpet mouth at the end close to the motor.

[0013] In the embodiments of the present application, the trumpet mouth refers to a hollow structure with a small opening at one end (referred to as a small mouth end) and a large opening at the other end (referred to as a large mouth end). Since the large mouth end of the trumpet mouth faces the other bearing, the oil in the above gap can flow to the other bearing through the trumpet mouth. Specifically, under the action of the rotating centrifugal force, the oil in the above gap will flow to the other bearing through the trumpet mouth along the part of the planet carrier extending into the bearing chamber.

[0014] In the embodiments of the present application, the planet carrier portion extending into the bearing chamber does not need to be provided with a radial hole for allowing oil in the gap to flow into the bearing chamber, and if the oil is allowed to flow into the bearing chamber through the radial hole, it is likely to result in insufficient lubrication of the other bearing with high rotation speed. Compared with the scheme of providing the radial hole, the embodiments of the present application include the trumpet mouth, so that the oil can be thrown to the other bearing with high rotation speed first, the other bearing is sufficiently lubricated and cooled, the problem of poor heat dissipation and easy wear of the other bearing is improved, the service life of the other bearing is prolonged, and the stability and reliability of the motor shaft during high-speed rotation are ensured.

[0015] In an embodiment, the trumpet mouth includes two sections of trumpet mouth, the large end of the first section of trumpet mouth is connected to the small end of the second section of trumpet mouth, and the large end of the second section of trumpet mouth faces the other bearing; the length of the second section of trumpet mouth is greater than the length of the first section of trumpet mouth along the axial direction of the motor, and the inclination of the second section of trumpet mouth is greater than the inclination of the first section of trumpet mouth.

[0016] In the embodiments of the present application, the trumpet mouth is divided into two sections of trumpet mouth with different inclinations, which is easier to be realized by a numerical control machine tool or a mold, and the risk of stress concentration or deformation caused by a single steep slope is avoided.

[0017] In the embodiments of the present application, the length of the first section of trumpet mouth is short and the inclination is small, which helps to maintain the laminar flow state of the fluid in the gap, slow down the flow rate of the fluid, avoid vortex or splashing caused by sudden change of flow rate, and ensure smooth transition of the oil to the second section of trumpet mouth. The inclination of the second section of trumpet mouth is large and the length is long, which is used to quickly guide the fluid to flow away from the edge of the trumpet mouth to the other bearing, avoid residual caused by surface tension, reduce the risk of droplet accumulation on the edge, and thus realize more sufficient lubrication of the other bearing.

[0018] In an embodiment, the inner circumferential surface of the planet carrier portion extending into the bearing chamber includes a ring of protrusions, the ring of protrusions protrudes toward the motor shaft along the radial direction of the motor, and the ring of protrusions surrounds the motor shaft. The outlets of a part of the first holes in the plurality of first holes along the axial direction of the motor are located on the side of the ring of protrusions facing the motor.

[0019] In the embodiments of the present application, the inner circumferential surface of the part of the planet carrier extending into the bearing chamber comprises a ring of protrusions, and since the ring of protrusions protrudes towards the motor shaft and surrounds the motor shaft, the ring of protrusions can divide a gap into two regions along the axial direction of the motor. Meanwhile, since the outlets of a part of the first holes are located on the side of the ring of protrusions facing the motor, the oil output by the outlets of the part of the first holes can enter the region closer to the motor of the two regions, and the oil in this region is less likely to flow towards the side of the ring of protrusions away from the motor and into the planet carrier, so that more or even all of the oil in this region can flow into the bearing chamber and lubricate the other bearing.

[0020] In an embodiment, the outlets of another part of the first holes are located on the side of the ring of protrusions away from the motor. In the embodiments of the present application, the first holes further comprise another part of the first holes, and since the outlets of the another part of the first holes are located on the side of the ring of protrusions away from the motor, the oil output by the outlets of the another part of the first holes can enter the region farther away from the motor of the two regions, and the oil in the other region is less likely to flow towards the side of the ring of protrusions facing the motor. The part of the planet carrier extending into the bearing chamber extends towards the side away from the motor along the axial direction of the motor to the inner cavity of the planet carrier, so that more of the oil in the other region can flow into the inner cavity of the planet carrier and lubricate the teeth of the sun gear, the teeth of the planet gears, the planet gear bearings and other components in the planet carrier.

[0021] In an embodiment, the distance from the ring of protrusions to the end of the part of the planet carrier extending into the bearing chamber closer to the motor along the axial direction of the motor is less than the distance from the ring of protrusions to the inner side wall of the inner cavity of the planet carrier closer to the motor.

[0022] In the embodiments of the present application, since the distance from the ring of protrusions to the end of the part of the planet carrier extending into the bearing chamber closer to the motor along the axial direction of the motor is small, the oil flowing into the region on the side of the ring of protrusions facing the motor can quickly accumulate and flow into the bearing chamber due to the blockage of the ring of protrusions.

[0023] In a combination example, the oil flowing into the bearing chamber due to the blockage of the ring of protrusions can quickly flow into the other bearing and sufficiently lubricate the other bearing in cooperation with the design of a bell mouth included in the inner circumferential surface of the part of the planet carrier extending into the bearing chamber closer to the motor.

[0024] In the embodiments of this application, since the distance from the circumference of the motor to the inner wall of the planetary carrier near the motor is relatively large, the amount of oil flowing into the area away from the motor side of the circumference of the circumference will accumulate more. This larger amount of oil provides sufficient and stable lubrication for the sun gear teeth, planet gear teeth, planet gear bearings and other components in the planetary carrier, making the planetary reducer less prone to wear and ensuring the normal and stable operation of the planetary reducer.

[0025] In one embodiment, the radial thickness of the portion of the planetary carrier extending into the bearing housing is less than the axial thickness of the portion of the planetary carrier on the side facing the motor that is opposite the planetary gears of the planetary reducer.

[0026] In the embodiments of this application, the thickness of the planetary gears relative to each other along the axial direction of the motor is relatively large, which makes the structure of the planetary carrier stronger, provides better support and positioning for the planetary gears, and makes the meshing of the planetary gears with the sun gear and the ring gear more stable, and less prone to generating unstable local stress.

[0027] In the embodiments of this application, the thickness of the portion of the planetary carrier extending into the bearing chamber along the radial direction of the motor is relatively small. This results in a larger gap between the portion of the planetary carrier extending into the bearing chamber and the motor shaft along the radial direction of the motor, i.e., a larger oil passage space, facilitating oil flow and preventing oil blockage and stagnation. Furthermore, in conjunction with some of the preceding embodiments, sufficient space is provided for the previously described ring of protrusions, facilitating their configuration.

[0028] In one embodiment, one bearing (a bearing connected to the planetary carrier in a bearing housing) and another bearing (a bearing connected to the motor shaft in a bearing housing) are spaced apart along the axial direction of the motor. The outer diameter of one bearing is larger than that of the other bearing, the inner diameter of one bearing is smaller than that of the other bearing, and the inner diameter of one bearing is larger than that of the other bearing.

[0029] In the embodiments of this application, since one bearing is spaced apart from another along the axial direction of the motor, a space for oil flow is included between the two bearings along the axial direction of the motor. Because the outer diameter of one bearing is larger than that of the other, and the inner diameter of one bearing is smaller than that of the other, and the inner diameter of one bearing is larger than that of the other, one bearing is further away from the motor shaft than the other along the radial direction of the motor. This allows the oil to be thrown, under the action of centrifugal force, from the bearing closer to the motor shaft (the bearing connected to the motor shaft in the bearing housing) through the space between the two bearings to the bearing farther from the motor shaft (the bearing connected to the planetary carrier in the bearing housing), thus enabling sufficient lubrication of both bearings sequentially.

[0030] In an embodiment, one bearing (the bearing connecting the planet carrier in the bearing chamber) is a tapered roller bearing, and the tapered roller bearing has its tapered bottom facing away from the other bearing (the bearing connecting the motor shaft in the bearing chamber).

[0031] In an embodiment of the application, one bearing (the bearing connecting the planet carrier in the bearing chamber) is a tapered roller bearing, and the tapered roller bearing has its tapered bottom facing away from the other bearing (the bearing connecting the motor shaft in the bearing chamber), i.e. facing away from the motor. The tapered roller bearing can bear both radial and axial forces, making the planetary reducer operate more stably. At the same time, because the tapered bottom of the tapered roller bearing faces away from the other bearing (the bearing connecting the motor shaft in the bearing chamber), the oil in the space between the two bearings can flow along the inclined direction of the roller to the side of the tapered roller bearing facing away from the motor under the action of the rotating centrifugal force, i.e. from the tapered top to the tapered bottom of the tapered roller bearing, thus achieving sufficient lubrication of the tapered roller.

[0032] In an embodiment, the other gap between the planet carrier side facing the motor and the housing along the axial direction of the motor is used to communicate the side of one bearing facing away from the motor and the gap between the planet carrier and the ring gear of the planetary reducer.

[0033] In an embodiment of the application, the oil flows from the side of one bearing (the bearing connecting the planet carrier in the bearing chamber) facing the motor to the side of the bearing facing away from the motor, and after sufficient lubrication of the bearing, the oil continues to flow to the other gap between the planet carrier side facing the motor and the housing along the axial direction of the motor. Due to the centrifugal force of the planet carrier in rotation, the oil can flow along the other gap to the gap between the planet carrier and the ring gear, also achieving lubrication of the teeth of the ring gear. Then, due to the meshing of the planet gears with the ring gear and the sun gear, the oil can also lubricate the teeth of the planet gears and the teeth of the sun gear. In addition, the oil can also flow into the planetary shaft and the planetary shaft bearing through the gap between the planet carrier and the planet carrier along the axial direction of the motor, achieving lubrication of the planetary shaft and the planetary shaft bearing.

[0034] In an embodiment, the side of the planet carrier facing the motor includes a plurality of recessed holes, and the openings of the plurality of recessed holes along the axial direction of the motor face the other gap. The side wall of each recessed hole away from the motor shaft along the radial direction of the motor includes one or more through holes, and the one or more through holes are used to deliver oil to the inner tooth surface of the ring gear of the planetary reducer.

[0035] In the embodiments of the present application, since the side of the planet carrier facing the motor includes a plurality of recessed holes, the openings of the plurality of recessed holes face the other gap, so that the oil in the other gap can also enter the plurality of recessed holes. Since the side wall of each recessed hole away from the motor shaft along the radial direction of the motor includes one or more through holes, the oil in each recessed hole is thrown to the inner tooth surface of the ring gear through the one or more through holes under the centrifugal force of the rotation of the planet carrier, so as to realize the lubrication of the inner tooth surface of the ring gear. Moreover, since the planet gears are engaged with the ring gear and the sun gear, the oil can also lubricate the teeth of the planet gears and the teeth of the sun gear.

[0036] In an embodiment, along the circumferential direction of the motor, the plurality of recessed holes are distributed between the plurality of planet gears, so that the volume of the recessed holes can be enlarged to accommodate more oil, the axial space of the planet carrier occupied by the recessed holes can be reduced, the weight of the planet carrier is also reduced, and the lightweight design of the planet carrier is realized.

[0037] In an embodiment, the outer circumferential surface of the motor shaft includes a recess, the recess is recessed inward along the radial direction of the motor, and the inner wall of the recess and the part of the planet carrier extending into the bearing chamber form the gap described above.

[0038] In the embodiments of the present application, since the outer circumferential surface of the motor shaft includes a recess, the recess is recessed inward along the radial direction of the motor, so that the radial dimension of the gap between the part of the planet carrier extending into the bearing chamber and the motor shaft (i.e. the inner wall of the recess) is larger, that is, the oil flow space is larger, the oil flow is more convenient, and the oil is prevented from being blocked and retained. When combined with some of the above embodiments, sufficient space is also left for the above-described ring of protrusions, facilitating the configuration of the above-described ring of protrusions.

[0039] In an embodiment, along the axial direction of the motor, the recess near the side wall of the motor does not exceed the end of the part of the planet carrier near the motor extending into the bearing chamber.

[0040] In the embodiments of the present application, since along the axial direction of the motor, the recess near the side wall of the motor does not exceed the end of the part of the planet carrier near the motor extending into the bearing chamber, the oil under the centrifugal force of the rotation of the motor shaft does not directly fall into the bearing chamber, but first falls on the inner circumferential surface of the part of the planet carrier extending into the bearing chamber. In this way, under the centrifugal force of the rotation of the planet carrier, the oil can flow to the other bearing connected to the motor shaft in the bearing chamber through the inner circumferential surface of the part of the planet carrier extending into the bearing chamber, so that the other bearing can be better lubricated, and the problem of insufficient lubrication of the other bearing and easy wear is avoided.

[0041] In an embodiment, the sun gear of the planetary reducer is integrated with the motor shaft as a unitary shaft; wherein: along the axial direction of the motor, the recess away from the side wall of the motor is the end surface of the sun gear facing the motor.

[0042] In the embodiment of the present application, the motor shaft and the sun gear are integrated into a one-piece shaft, which is more convenient to install. The motor shaft is directly inserted into the planet carrier, so that the teeth on the motor shaft (i.e. the teeth of the sun gear) are engaged with the teeth of the planet gears to complete the installation. Compared with the scheme in which the motor shaft is connected to the sun gear through splines and the shaft shoulder is used to position the sun gear, the structure is simpler and the axial size is smaller, which is more conducive to the miniaturization design of the power assembly.

[0043] In the embodiment of the present application, the side wall of the one groove away from the motor is extended into the inner cavity of the planet carrier, so that when the oil is located in the area of the one groove away from the motor, the oil is thrown into the inner cavity of the planet carrier under the action of the rotational centrifugal force of the motor shaft, for example, into the gap between the planet gears and the planet carrier along the axial direction of the motor, thereby fully lubricating the planet shaft and the planet gear bearing and ensuring the stable and reliable operation of the planet gears.

[0044] In one embodiment, the motor shaft includes a plurality of second holes, one end of the plurality of second holes being used to communicate the shaft cavity of the motor shaft, and the other end being used to deliver oil to the rotor of the motor. The plurality of first holes are used to communicate the shaft cavity of the part of the motor shaft extending into the planet carrier, and the plurality of second holes are used to communicate the shaft cavity of the part of the motor shaft not extending into the planet carrier. The radial size of the shaft cavity of the part of the motor shaft extending into the planet carrier is smaller than the radial size of the shaft cavity of the part of the motor shaft not extending into the planet carrier, and the diameter of each first hole is smaller than the diameter of each second hole.

[0045] The rotor generates a large mechanical loss due to high-speed rotation, and insufficient lubrication of the rotor will have a serious impact on the performance, reliability and service life of the motor. In addition, the rotor generates a large amount of heat due to electromagnetic loss, mechanical loss, etc., and insufficient heat dissipation of the motor rotor will also have a serious impact on the performance, reliability and service life of the motor. In the embodiment of the present application, the motor shaft includes a plurality of second holes, so that the oil in the shaft cavity of the motor shaft is thrown to the rotor of the motor under the action of the rotational centrifugal force of the motor shaft, thereby achieving sufficient lubrication and heat dissipation of the rotor.

[0046] In the embodiment of the present application, the radial size of the shaft cavity of the part of the motor shaft extending into the planet carrier is small, and the diameter of the plurality of first holes communicating the shaft cavity of the part of the motor shaft extending into the planet carrier is small, so that the jet velocity of the oil is high but the flow is small at this position, the oil can interfere with the main flow weakly while lubricating the two bearings and the planetary reducer, and the oil can also flow well to the shaft cavity of the part of the motor shaft not extending into the planet carrier. In the embodiment of the present application, the radial size of the shaft cavity of the part of the motor shaft extending into the planet carrier is small, and the strength of the part of the motor shaft extending into the planet carrier is also taken into account, so that the motor shaft is not easy to break.

[0047] In the embodiments of the present application, the radial dimension of the shaft cavity of the portion of the motor shaft not extending into the planet carrier is large, and the hole diameter of the plurality of second holes communicating with the shaft cavity of the portion of the motor shaft not extending into the planet carrier is large, so that the flow rate of the oil liquid at this position is low but the flow volume is large, and the rotor can be well lubricated and cooled.

[0048] In a second aspect, a vehicle is provided, comprising: a wheel and the power assembly described in any one of the embodiments of the first aspect, the power assembly being configured to drive the wheel to rotate.

[0049] In the embodiments of the present application, the power assembly described in any one of the embodiments of the first aspect is applied to a vehicle, and the service life of the motor and the planetary reducer is prolonged, the long-term stable operation of the power assembly is ensured, and the long-term smooth and safe driving of the vehicle is ensured. BRIEF DESCRIPTION OF DRAWINGS

[0050] Figure 1 A structural diagram of a vehicle provided in the embodiments of the present application is shown in FIG. 1.

[0051] Figure 2 An installation schematic diagram of a power assembly and a wheel cooperating with each other provided in the embodiments of the present application is shown in FIG. 2.

[0052] Figure 3 A partial structural sectional view of a power assembly provided in the embodiments of the present application is shown in FIG. 3.

[0053] Figure 4 A partial structural sectional view of a power assembly provided in the embodiments of the present application is shown in FIG. 3. Figure 3 An enlarged view of a partial structure of the M portion of the power assembly shown in FIG. 3 is shown in FIG. 4.

[0054] Figure 5 A structural diagram of a planet carrier provided in the embodiments of the present application is shown in FIG. 5.

[0055] Figure 6 A sectional structural diagram of the planet carrier shown in FIG. 5 is shown in FIG. 6. Figure 5

[0056] A structural diagram of a motor shaft provided in the embodiments of the present application is shown in FIG. 7. Figure 7

[0057] A partial structural sectional view of another power assembly provided in the embodiments of the present application is shown in FIG. 8. Figure 8

[0058] A partial structural sectional view of another power assembly provided in the embodiments of the present application is shown in FIG. 8. Figure 9 Figure 8 A partial structural sectional view of another power assembly provided in the embodiments of the present application is shown in FIG. 8.

[0059] Figure 10 A structural diagram of a planet carrier in the embodiments of the present application is shown in FIG. 5. Figure 8 A structural diagram of a planet carrier in the embodiments of the present application is shown in FIG. 5.​

[0060] Figure 11 For Figure 8 Structure diagram of the planetary carrier in the embodiment from another perspective;

[0061] Figure 12 For Figure 8 Assembly structure diagram of part of the structure in the embodiment;

[0062] Figure 13 Structure diagram of an oil baffle provided in the embodiment of the application;

[0063] Figure 14 Partial structure sectional view of another power assembly provided in the embodiment of the application;

[0064] Figure 15 Exploded view of an oil baffle provided in the embodiment of the application from the perspective of the side away from the motor;

[0065] Figure 16 Exploded view of an oil baffle provided in the embodiment of the application from the perspective of the side toward the motor;

[0066] Figure 17 Structure diagram of an outer layer of an oil baffle provided in the embodiment of the application;

[0067] Figure 18 Structure diagram of another outer layer of an oil baffle provided in the embodiment of the application;

[0068] Figure 19 Structure diagram of an intermediate layer of an oil baffle provided in the embodiment of the application. DETAILED DESCRIPTION

[0069] The technical solutions in the embodiments of the application will be described below with reference to the drawings in the embodiments of the application. Obviously, the described embodiments are only some of the embodiments of the application.

[0070] In the drawings of the embodiments of the application, the structures of components, assemblies, etc. are represented by guide lines; the hollow structures such as gaps, openings, holes, grooves, cavities, spaces, etc. and the surfaces such as outer circumferential surfaces, inner circumferential surfaces, side walls, bottom surfaces, end surfaces, etc. are represented by guide lines with arrows.

[0071] In current power assemblies, some bearings and / or gear teeth have the problem of insufficient lubrication. Based on this, the application provides a power assembly and a vehicle, aiming to improve the lubrication effect of some bearings and / or gear teeth.

[0072] To make the objectives, technical solutions, and advantages of the application clearer, the application will be described in further detail below with reference to the drawings.

[0073] Please refer to Figure 1 , Figure 1 A structural diagram of a vehicle 1000 is provided in an embodiment of the present application. In the embodiment of the present application, the vehicle 1000 refers to a wheeled device driven or pulled by a power device. The vehicle 1000 includes a battery electric vehicle (BEV), a hybrid electric vehicle (HEV), a range-extended electric vehicle (REEV), or a plug-in hybrid electric vehicle (PHEV), etc.

[0074] In the embodiment of the present application, the vehicle 1000 includes a power assembly 100, a frame 200, a battery pack 300, and wheels 400. The frame 200 is a structural framework of the vehicle 1000, and is used to mount the power assembly 100, the battery pack 300, and the wheels 400. The frame 200 can bear environmental loads. The battery pack 300 is used to supply power to the power assembly 100, and can also be referred to as a power battery. The power assembly 100 is a power source of the vehicle 1000, and is used to convert electrical energy provided by the battery pack 300 into mechanical energy, thereby driving the wheels 400 of the vehicle 1000 to rotate, and further driving the vehicle 1000 to travel.

[0075] In the embodiment of the present application, the power assembly 100 is used to drive the rear wheels of the vehicle 1000 to rotate, and the front wheels of the vehicle 1000 are used to realize steering. The vehicle 1000 is more sensitive in steering and more stable in cornering. Figure 1 The rear wheels of the vehicle 1000 are the wheels 400 on the right side close to the tail side. Figure 1 The rear wheels of the vehicle 1000 are the wheels 400 on the right side close to the tail side.

[0076] In other embodiments of the present application, the power assembly 100 is used to drive the front wheels of the vehicle 1000 to rotate, and the front wheels are used to realize driving and steering. The front-wheel drive mode has a simple structure, fewer parts, lighter weight, reduced power loss, higher transmission efficiency, lower fuel consumption, and lower cost. Figure 1 The front wheels of the vehicle 1000 are the wheels 400 on the left side close to the head side.

[0077] Please refer to Figure 2 , Figure 2 An installation schematic diagram of the power assembly 100 and the wheels is provided in an embodiment of the present application. Figure 2Some internal components of the power assembly 100 are only schematically shown, and the specific shape, size and positional relationship of the components are not represented, and the connection between some components is hidden for the purpose of simplicity. In the embodiments of the present application, the power assembly 100 can include a single electric drive power assembly, a dual electric drive power assembly or a hybrid electric drive power assembly.

[0078] In the embodiments of the present application, the power assembly 100 includes the motor 1 and the planetary reducer 2. The motor shaft 11 of the motor 10 outputs high-speed kinetic energy, and the planetary reducer 2 converts the high-speed kinetic energy into greater torque output. The output shaft 212 of the planetary reducer 2 outputs low-speed and high-torque kinetic energy. In an embodiment of the present application, the output shaft 212 is a gear shaft, which is engaged with the second parallel gear 401 for transmission, and the kinetic energy is output to the wheels 400 through two half shafts 402. Those skilled in the art can select the transmission structure between the output shaft 212 and the wheels according to actual needs.

[0079] Please refer to Figure 3 , Figure 3 A partial structure sectional view of a power assembly 100 is provided in the embodiments of the present application. Specifically, Figure 3 is a sectional view along the axial direction of the motor along the central axis of the motor shaft, Figure 3 The oil flow direction is indicated by the dashed arrows. In the embodiments of the present application, the power assembly 100 includes a housing 00, a motor 1 and a planetary reducer 2.

[0080] The housing 00 in some embodiments of the present application is described below.

[0081] In an embodiment of the present application, the housing 00 includes two-part housing (01, 02), wherein the housing 01 and the housing 02 are fixedly connected by bolts to form a closed chamber for accommodating the motor 1, the planetary reducer 2 and other components.

[0082] In the embodiments of the present application, the housing 01 includes a partition plate (01a, 01b) that separates the motor slot and the reducer slot in the housing 01 along the axial direction of the motor 1. The motor 1 is installed in the motor slot from the opening on the side away from the partition plate, and the planetary reducer 2 is installed in the reducer slot from the opening on the side away from the partition plate. In the present embodiment, the partition plate of the housing 01 is integrally cast with other parts of the housing, and does not need to be added separately, which does not increase the assembly difficulty.

[0083] In the embodiments of the present application, a part 01b of the partition plate extends along the radial direction of the motor 1, and another part 01a of the partition plate extends along the axial direction of the motor. The inner circumferential side of the other part 01a of the partition plate includes a bearing chamber 90.

[0084] In the embodiment of the application, the bearing chamber 90 comprises two bearing mounting positions arranged in the axial direction. One of the bearing mounting positions is arranged to mount a bearing from the motor slot side and limit the bearing from moving away from the reducer slot side by a shaft shoulder; the other bearing mounting position is arranged to mount a bearing from the reducer slot side and limit the bearing from moving away from the motor slot side by another shaft shoulder.

[0085] The motor 1 in some embodiments of the application is described below.

[0086] In the embodiment of the application, the motor 1 comprises a stator 13, a rotor 12 and a motor shaft 11, wherein the rotor 12 surrounds the motor shaft 11, the stator 13 surrounds the rotor 12, and the stator 13 is fixed in the housing 01. Figure 1 The direct current provided by the battery pack 300 is converted into alternating current by the motor controller and then delivered to the winding of the rotor 12. The rotating magnetic field generated by the winding of the rotor 12 after receiving the alternating current interacts with the permanent magnet on the rotor. The electromagnetic field causes the rotor 12 to rotate relative to the stator 13, thereby driving the motor shaft 11 to rotate. The motor shaft 11 is used to output kinetic energy with high rotational speed. The motor shaft 11 extends into the reducer slot through the bearing chamber 90. The inner ring of the bearing 92 near the motor in the bearing chamber 90 is connected to the motor shaft 11 and is used to support and position the motor shaft 11.

[0087] In the embodiment of the application, the motor shaft 11 comprises a shaft cavity 110. Referring to Figure 3 , the shaft cavity 110 of the motor shaft 11 extends in the axial direction of the motor. The shaft cavity 110 of the motor shaft 11 is used to introduce oil.

[0088] During the operation of the motor 1, the rotor 12 generates a large amount of heat and wear due to electromagnetic loss, mechanical loss, etc. If the heat dissipation and lubrication of the rotor 12 are insufficient, it will have a serious impact on the performance, reliability and service life of the motor. Therefore, in order to ensure the normal operation of the motor 1, the rotor 12 needs to be designed for heat dissipation and lubrication.

[0089] In one embodiment of the application, the motor shaft comprises a plurality of second holes 112, which are used to: under the action of the rotational centrifugal force of the motor shaft 11, the oil in the shaft cavity 110 is thrown out to the rotor 12 of the motor. In the embodiment of the application, the side of the end plate 121 of the rotor 12 facing the rotor core comprises an oil groove 121a. The oil thrown out from the plurality of second holes 112 will first enter a part of the oil groove 121a, then pass through a part of the oil groove 121a to enter the internal flow channel of the rotor core for lubrication and heat dissipation, and finally be discharged from another part of the oil groove of the end plate 121. In this way, sufficient lubrication and heat dissipation of the motor rotor are achieved, which is conducive to improving the performance, reliability and service life of the motor.

[0090] In an embodiment of the present application, the plurality of second holes 112 are parallel to the radial direction of the motor 1, and the plurality of second holes 112 are arranged at intervals along the circumferential direction of the motor, so that the oil can be thrown out more quickly and more through the plurality of second holes 112, and the motor rotor can be better lubricated and cooled.

[0091] The planetary reducer 2 in some embodiments of the present application is described below.

[0092] In an embodiment of the present application, the planetary reducer 2 includes a planet carrier 21, a plurality of planet gears 22, a sun gear 23, and a ring gear 24. The ring gear 24 is fixed in the housing 01, the plurality of planet gears 22 are rotatably mounted on the planet carrier 21 along the circumferential direction of the motor 1, and the plurality of planet gears 22 are simultaneously engaged with the sun gear 23 and the ring gear 24. The planetary reducer 2 converts the kinetic energy of high rotational speed into greater torque output, and outputs low rotational speed and large torque through the output shaft 212 of the planet carrier 21. In an embodiment of the present application, as shown in Figure 3 , the planet carrier 21 and the output shaft 212 of the planet carrier are designed in a split type, the part of the output shaft 212 of the planet carrier towards the end of the planet carrier 21 extends into the central hole of the planet carrier 21, and the outer circumferential surface of the part of the output shaft 212 of the planet carrier extending into the central hole of the planet carrier 21 and the shaft end surface of the output shaft 212 of the planet carrier towards the end of the planet carrier 21 are welded with the planet carrier 21 (i.e. the weld joint in Figure 3 ), so that the connection reliability is high. In another embodiment of the present application, the planet carrier 21 and the output shaft 212 of the planet carrier are designed in an integrated type, such as integrally cast (not shown), so that the subsequent assembly of the planet carrier 21 and the output shaft 212 is not needed, and the assembly process can be simplified.

[0093] In an embodiment of the present application, the motor shaft 11 extends into the central hole of the sun gear 23 at the end of the reducer slot, and is connected through spline fitting to realize high-speed rotation of the sun gear 23. In another embodiment of the present application, as shown in Figure 3 , the sun gear 23 and the motor shaft are a one-piece shaft, i.e. an integrated structure, without the need for subsequent assembly and connection process. The end of the motor shaft 11 extending into the reducer slot is directly configured as the sun gear 23, and the teeth on the outer circumferential surface of the sun gear 23 are engaged with the teeth of the plurality of planet gears.

[0094] In an embodiment of the present application, the part 211 of the planet carrier 21 towards the side of the motor 1 extends into the bearing chamber 90, and the inner ring of the bearing 91 in the bearing chamber 90 away from the motor is connected with the part 211 of the planet carrier 21 towards the side of the motor 1, for supporting and positioning the planet carrier 21.

[0095] At present, in the working process of the power assembly 100, since the bearing 92 of the power assembly 100 has high rotating speed and the bearing 91 has large load, one of the key factors to improve the reliability of the bearing 92 and the bearing 91 is the lubrication effect on the bearing 92 and the bearing 91. If the lubrication is insufficient to cause the bearing 92 and the bearing 91 to lack lubricating oil to form an oil film, the bearing 92 and the bearing 91 will be quickly worn, and in severe cases, a safety risk can be caused.

[0096] Some embodiments of the present application can improve the lubrication efficiency of the bearing 92 and the bearing 91 of the power assembly 100 by improving the lubrication mode of the bearing 92 and the bearing 91 of the power assembly 100, and ensure the normal operation of the power assembly 100.

[0097] Please refer to Figure 4 , Figure 4 for Figure 3 the partial structure enlarged view of the M part of the power assembly 100 shown in the figure, Figure 4 the oil flow direction is indicated by a dashed arrow.

[0098] In the embodiments of the present application, the motor shaft 11 comprises a plurality of first holes 111, and the plurality of first holes 111 are used to: under the action of the rotating centrifugal force of the motor shaft 11, the oil in the shaft cavity 110 is thrown out from the plurality of first holes 111.

[0099] In the embodiments of the present application, since the housing 01 comprises a bearing chamber accommodating the bearing 92 and the bearing 91, and the part 211 of the carrier 21 extending into the bearing chamber 90 has a gap g1 with the motor shaft 11. The oil output by the plurality of first holes 111 of the motor shaft 11 can flow to the bearing chamber 90 through the gap g1, so as to lubricate the two bearings (91, 92) in the bearing chamber 90 and improve the lubrication effect of the two bearings (91, 92).

[0100] Through the lubrication of the above two bearings (91, 92), the running stability of the motor shaft 11 and the carrier 21 is better, which is conducive to improving the service life of the motor 1 and the planetary reducer 2, and ensuring the long-term stable operation of the power assembly 100.

[0101] In the embodiments of the present application, the bearing chamber 90 is constructed in the housing by using a part 01a of the housing 01, and the oil is transmitted to the bearing chamber 90 through a gap g1 between the part 211 of the carrier 21 extending into the bearing chamber 90 and the part of the motor shaft 11 extending into the bearing chamber 90. Without adding other additional components, the lubrication of the two bearings (91, 92) in the bearing chamber 90 can be realized, so as to improve the service life of the two bearings (91, 92), the motor 1 and the planetary reducer 2, and make the structure of the power assembly 100 more compact, which is also conducive to the miniaturization design of the power assembly 100.

[0102] The following will be described in combination with Figures 4-6 The relevant features of the part 211 of the planet carrier 21 extending into the bearing chamber 90 will be described.

[0103] Continuing to refer to Figure 4 In an embodiment, the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90 near the end of the motor 1 is a bell mouth E1, and the large end of the bell mouth E1 faces the other bearing 92.

[0104] In the embodiment of the present application, the bell mouth E1 refers to a hollow structure with a small opening at one end (referred to as the small end) and a large opening at the other end (referred to as the large end). Since the large end of the bell mouth E1 faces the other bearing 92, the oil in the above-mentioned one gap g1 can flow to the other bearing 92 through the bell mouth E2. Specifically, under the action of the rotating centrifugal force, the oil in the above-mentioned one gap g1 will flow to the other bearing 92 through the bell mouth E1 along the part 211 of the planet carrier 21 extending into the bearing chamber 90.

[0105] In the embodiment of the present application, it is not necessary to punch a radial hole in the part of the planet carrier 21 extending into the bearing chamber 90 to make the oil in the one gap g1 flow into the bearing chamber 90, and if the radial hole is used to make the oil flow into the bearing chamber 90, it is likely to cause insufficient lubrication of the oil to the high-speed other bearing 92. Compared with the scheme of punching a radial hole, the embodiment of the present application includes the bell mouth E1, so that the oil can be thrown to the high-speed other bearing 92 first, fully lubricate and cool the other bearing 92, improve the problem of poor heat dissipation and easy wear of the other bearing 92, prolong the service life of the other bearing 92, and ensure the stability and reliability of the high-speed operation of the motor shaft 11.

[0106] Figure 5 The structural diagram of the planet carrier provided in the embodiment of the present application is shown in Figure 6 The structural diagram of the planet carrier provided in the embodiment of the present application is shown in Figure 5 The cross-sectional structural diagram of the planet carrier is shown in

[0107] In combination with Figure 5 And Figure 6 In an embodiment of the present application, the bell mouth E1 includes two bell mouths (E11, E12), the large end of the first bell mouth E11 is connected to the small end of the second bell mouth E12, and the large end of the second bell mouth E12 faces the other bearing 92; the length k12 of the second bell mouth E12 in the axial direction of the motor is greater than the length k11 of the first bell mouth E11, and the inclination α12 of the second bell mouth E12 is greater than the inclination α11 of the first bell mouth E11.

[0108] In the embodiments of the present application, the horn mouth E1 is divided into two sections of different inclinations (E11, E12), which is easier to be realized by a numerical control machine tool or a mold, and avoids the risk of stress concentration or deformation caused by a single steep slope.

[0109] In the embodiments of the present application, the length k11 of the first section of the horn mouth E11 is short and the inclination a11 is small, which helps to maintain the laminar flow state of the fluid in a gap, slows down the flow rate of the fluid, avoids the generation of vortex or splashing due to sudden change of flow rate, and ensures smooth transition of the oil to the second section of the horn mouth E12. The inclination a12 of the second section of the horn mouth E12 is large and the length k12 is long, which is used to quickly guide the fluid to flow away from the edge of the horn mouth E1 to another bearing 92, avoids residual caused by surface tension, reduces the risk of droplets accumulating at the edge, and thus realizes more sufficient lubrication of another bearing 92.

[0110] In an embodiment of the present application, in combination with Figures 3-6 As shown in the figure, the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90 includes a ring of protrusions 213, the ring of protrusions 213 protrudes towards the motor shaft 11 along the radial direction of the motor 1, and the ring of protrusions 213 surrounds the motor shaft 11. The outlets of a part of the plurality of first holes 111 (refer to Figure 4 the first hole 111 located on the right side of the ring of protrusions 213 in the figure) in the axial direction of the motor 1 are located on the side of the ring of protrusions 213 facing the motor 1.

[0111] In an embodiment, the ring of protrusions 213 is fixed by welding process on the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90. In another embodiment, the ring of protrusions 213 is an integral structure with the part 211 of the planet carrier 21 extending into the bearing chamber 90, and is formed by integral casting process.

[0112] In the embodiments of the present application, by including the ring of protrusions 213 on the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90, since the ring of protrusions 213 protrudes towards the motor shaft 11 and surrounds the motor shaft 11, the ring of protrusions 213 can divide a gap g1 into two regions along the axial direction of the motor 1. At the same time, since the outlets of a part of the plurality of first holes 111 are located on the side of the ring of protrusions 213 facing the motor 1, the oil output by the outlets of this part of the first holes 111 can enter a region close to the motor 1 of the two regions. The oil in this region is not easy to flow into the planet carrier 21 towards the side of the ring of protrusions 213 away from the motor 1 due to the blockage of the ring of protrusions 213, so more or even all of the oil in this region can flow into the bearing chamber 90 and flow to another bearing 92, thereby fully lubricating another bearing 92.

[0113] In one embodiment of the present application, the outlets of the other portion of the first holes 111 are located on the side of the ring-shaped protrusion 213 away from the motor 1. In the embodiment of the present application, the plurality of first holes 111 further include the other portion of the first holes 111 (refer to Figure 4 the first holes 111 located on the left side of the ring-shaped protrusion 213), and since the outlets of the other portion of the first holes 111 are located on the side of the ring-shaped protrusion 213 away from the motor 1, the oil outputted from the outlets of the other portion of the first holes 111 can enter the other region away from the motor 1 of the two regions, and the oil in the other region is not easy to flow toward the side of the ring-shaped protrusion 213 toward the motor 1 due to the blockage of the ring-shaped protrusion 213. The portion 211 of the carrier 21 extending into the bearing chamber 90 extends to the inner cavity of the carrier along the axial direction of the motor 1 toward the side away from the motor 1, and thus the oil in the other region can flow more into the inner cavity of the carrier 21 through the gap between the carrier 21 and the motor shaft, and flow to the gear teeth of the sun gear 23, the gear teeth of the planetary gear 22, the planetary gear bearing and other components in the carrier 21, thereby sufficiently lubricating the gear teeth of the sun gear 23, the gear teeth of the planetary gear 22, the planetary gear bearing and other components in the carrier.

[0114] In one embodiment of the present application, the distance k21 from the ring-shaped protrusion 213 to the end of the portion 211 of the carrier 21 extending into the bearing chamber 90 close to the motor 1 along the axial direction of the motor 1 is smaller than the distance k22 from the ring-shaped protrusion 213 to the inner side wall of the inner cavity of the carrier 21 close to the side of the motor 1.

[0115] In the embodiment of the present application, since the distance from the ring-shaped protrusion 213 to the end of the portion 211 of the carrier 21 extending into the bearing chamber 90 close to the motor 1 along the axial direction of the motor 1 is small, the oil flowing into the region on the side of the ring-shaped protrusion 213 toward the motor 1 can quickly accumulate and flow to the bearing chamber 90 due to the blockage of the ring-shaped protrusion 213.

[0116] In one combination example, the oil flowing to the bearing chamber 90 due to the blockage of the ring-shaped protrusion 213 can quickly flow to the other bearing 92 to quickly and sufficiently lubricate the other bearing 92 in cooperation with the design of the horn E1 included in the inner circumferential surface m1 of the portion 211 of the carrier 21 extending into the bearing chamber 90 close to the motor 1.

[0117] In the embodiments of the present application, because the distance k22 of the inner side wall close to the side of the motor 1 of the inner cavity of the planet carrier 21 to the one circle of protrusions 213 along the axial direction of the motor 1 is large, the amount of oil flowing into the area away from the side of the motor 1 of the one circle of protrusions 213 can be accumulated more, and the more amount of oil can provide sufficient and stable lubrication for the gear teeth of the sun gear 23, the gear teeth of the planet gear 22, the planet gear bearing and other components in the planet carrier 21, so that the planetary reducer 2 is not easy to wear and tear, and the normal and stable operation of the planetary reducer 2 is ensured.

[0118] In an embodiment of the present application, referring to Figure 6 , the thickness k31 of the part 211 of the planet carrier 21 extending into the bearing chamber 90 along the radial direction of the motor 1 is less than the thickness k32 of the part 214 of the planet carrier 21 opposite to the planet gear 22 of the planetary reducer 2 along the axial direction of the motor 1.

[0119] In the embodiments of the present application, the thickness k32 of the part 214 of the planet carrier 21 opposite to the planet gear 22 of the planetary reducer 2 along the axial direction of the motor 1 is large, so that the structural strength of the planet carrier 21 is higher, the planet gear 22 is well supported and positioned, the engagement of the planet gear 22 with the sun gear 23 and the ring gear 24 is more stable, and the unstable local pitting stress is not easy to occur.

[0120] In the embodiments of the present application, the thickness k31 of the part 211 of the planet carrier 21 extending into the bearing chamber 90 along the radial direction of the motor 1 is small, so that the size of the gap g1 between the part 211 of the planet carrier 21 extending into the bearing chamber 90 and the motor shaft 11 along the radial direction of the motor 1 is larger, that is, the oil space is larger, the oil flow is facilitated, and the oil blockage and retention are avoided. In combination with some of the foregoing embodiments, sufficient space is left for the one circle of protrusions 213 described above, and the one circle of protrusions 213 described above is facilitated to be configured.

[0121] The arrangement of the two bearings in the bearing chamber and other features of the planet carrier toward the side of the motor will be introduced below. Figures 3-6

[0122] In an embodiment of the present application, as shown in Figure 3 and Figure 4 , one bearing 91 and another bearing 92 are arranged at intervals along the axial direction of the motor 1, the outer diameter size of the one bearing 91 is larger than that of the another bearing 92, the inner diameter size of the one bearing 91 is smaller than that of the another bearing 92, and the inner diameter size of the one bearing 91 is larger than that of the another bearing 92.

[0123] ​In the embodiment of the application, since one bearing 91 is spaced apart from the other bearing 92 along the axial direction of the motor 1, a space for circulating oil is included between the two bearings along the axial direction of the motor 1. Since the outer diameter of one bearing 91 is larger than the outer diameter of the other bearing 92, the inner diameter of one bearing 91 is smaller than the outer diameter of the other bearing 92, and the inner diameter of one bearing 91 is larger than the inner diameter of the other bearing 92, one bearing 91 is farther away from the motor shaft 11 than the other bearing 92 along the radial direction of the motor 1, so that the oil can be thrown from the other bearing 92 closer to the motor shaft 11 to one bearing 91 farther away from the motor shaft 11 under the action of centrifugal force through the space between the two bearings, and thus the two bearings can be fully lubricated in turn.

[0124] In one embodiment, one bearing 91 is a tapered roller bearing, and the tapered bottom of the tapered roller bearing faces away from the other bearing 92.

[0125] In the embodiment of the application, one bearing 91 connected to the planet carrier 21 in the bearing chamber 90 is a tapered roller bearing, and the tapered bottom of the tapered roller bearing faces away from the other bearing 92 connected to the motor shaft 11 in the bearing chamber 90, i.e., away from the motor 1. The tapered roller bearing can simultaneously withstand radial and axial forces, making the planetary reducer 2 operate more stably. At the same time, since the tapered bottom of the tapered roller bearing faces away from the other bearing 92 connected to the motor shaft 11 in the bearing chamber 90, the oil in the space between the two bearings can flow along the inclined direction of the rollers of the tapered roller bearing to the side of the tapered roller bearing away from the motor 1 under the action of rotational centrifugal force, i.e., from the tapered top to the tapered bottom of the tapered roller bearing, so that the tapered roller bearing is fully lubricated.

[0126] In one embodiment of the application, referring to Figure 4 , the planet carrier 21 includes another gap g2 between the side facing the motor 1 and the housing 01 along the axial direction of the motor 1, one end of the other gap g2 is used to communicate with the side of one bearing 91 away from the motor 1, and the other end is used to communicate with the gap between the planet carrier 21 and the ring gear 24.

[0127] In the embodiments of the present application, the oil liquid from the bearing 91 of the planet carrier 21 on the side of the bearing chamber 90 facing the motor 1 flows through the bearing 91 to the side of the bearing 91 away from the motor 1, and after the bearing 91 is sufficiently lubricated, the oil liquid continues to flow to another gap g2 between the planet carrier 21 on the side facing the motor 1 and the housing 01 (i.e. a part 01b of the partition plate) along the axial direction of the motor 1, and due to the centrifugal force of the rotation of the planet carrier 21, the oil liquid can flow along the other gap g2 to the gap between the planet carrier 21 and the ring gear 24, and also achieve lubrication of the teeth of the ring gear 24, and then due to the meshing of the planet wheel 22 with the ring gear 24 and the sun gear 23, the oil liquid can also lubricate the teeth of the planet wheel 22 and the teeth of the sun gear 23, and the oil liquid can also flow into the planet shaft and the planet shaft bearing (not shown, see the following description) through the gap between the planet wheel 22 and the planet carrier 21 along the axial direction of the motor 1, and achieve lubrication of the planet shaft and the planet shaft bearing. Figures 3-6 The planet shaft and the planet shaft bearing are not shown, and can be referred to in the following Figure 8 , which will be introduced below), to achieve lubrication of the planet shaft and the planet shaft bearing.

[0128] In an embodiment, referring to Figure 5 and Figure 6 , the side of the planet carrier 21 facing the motor 1 includes a plurality of recess holes 202, and the openings of the plurality of recess holes 202 along the axial direction of the motor 1 face the other gap g2 (shown in combination with Figure 4 ), and the side wall of each recess hole 202 away from the motor shaft 11 along the radial direction of the motor 1 includes one or more through holes 202a, and the one or more through holes are used to deliver oil liquid to the inner tooth surface of the ring gear 24 of the planetary reducer 2.

[0129] In the embodiments of the present application, since the side of the planet carrier 21 facing the motor 1 includes a plurality of recess holes 202, and the openings of the plurality of recess holes 202 face the other gap g2, the oil liquid in the other gap g2 can also enter the plurality of recess holes 202. Since the side wall of each recess hole 202 away from the motor shaft 11 along the radial direction of the motor 1 includes one or more through holes 202a, the oil liquid in each recess hole 202 is thrown to the inner tooth surface of the ring gear 24 through the one or more through holes 202a under the centrifugal force of the rotation of the planet carrier 21, and lubrication of the inner tooth surface of the ring gear 24 is achieved. And due to the meshing of the planet wheel 22 with the ring gear 24 and the sun gear 23, the oil liquid can also lubricate the teeth of the planet wheel 22 and the teeth of the sun gear 23.

[0130] In an embodiment, along the circumferential direction of the motor 1, the plurality of recess holes 202 are distributed between the plurality of planet wheels 22, so that the volume of the recess hole 202 can be enlarged to accommodate more oil liquid, the axial space of the planet carrier 21 occupied by the recess hole 202 can be reduced, the weight of the planet carrier 21 can be reduced, and the lightweight design of the planet carrier can be achieved. Figure 5In the example shown in FIG. 1, the plurality of recessed holes 202 and the plurality of planetary gears 22 are arranged alternately along the circumferential direction of the motor 1. Figure 5 The mounting position between the two recessed holes 202 is used to mount the planetary gear 22. Specifically, the planetary shaft is fixed in the shaft hole 201, and the planetary gear 22 is mounted on the planetary shaft through the planetary gear bearing.

[0131] In an embodiment of the present application, each recessed hole 202 on the side of the motor 1 towards the planetary carrier 21 is in the shape of a fan ring. Specifically, the fan ring is the shape of the remaining part after a small fan-shaped side of the sharp corner of a sector is removed. Along the radial direction of the motor, the fan ring includes two parallel arc surfaces. In an embodiment of the present application, each recessed hole 202 corresponds to at least two through holes 202a distributed in the side wall of the recessed hole 202 away from the motor shaft 11 in the two end regions along the axial direction of the motor 1. In this way, under the action of the rotational centrifugal force of the planetary carrier 21, the oil flows along the two sides of the recessed hole 202 along the circumferential direction of the motor 1 to the side wall of the recessed hole 202 away from the motor shaft 11, and then is thrown out to the ring gear 24 through the through holes 202a distributed in the side wall of the recessed hole 202 away from the motor shaft 11 in the two end regions along the axial direction of the motor 1, respectively.

[0132] In an embodiment of the present application, the through holes 202a are parallel to the radial direction of the motor, so that the oil in the recessed hole 202 can be quickly thrown out to the ring gear 24 through the through holes 202a under the action of the rotational centrifugal force of the planetary carrier 21.

[0133] The following will be described in combination with Figure 3 , Figure 4 , Figure 7 The related features of the motor shaft 11 will be introduced. Figure 7 The structural diagram of the motor shaft 11 provided in an embodiment of the present application.

[0134] In an embodiment of the present application, the outer circumferential surface of the motor shaft 11 includes a groove C1, and the groove C1 is recessed inwardly along the radial direction of the motor 1. The inner wall of the groove C1 and the part 211 of the planetary carrier 21 extending into the bearing chamber 90 form a gap g1 described above.

[0135] In an embodiment of the present application, since the outer circumferential surface of the motor shaft 11 includes a groove C1, and the groove C1 is recessed inwardly along the radial direction of the motor 1, the radial dimension of the gap g1 between the part 211 of the planetary carrier 21 extending into the bearing chamber 90 and the motor shaft 11 (i.e. the inner wall of the groove C1) is larger, i.e. the oil flow space is larger, which is more convenient for the oil to flow through and avoids the oil from being blocked and retained. When combined with some of the above embodiments, sufficient space is also left for the above-described ring of protrusions 213, which is convenient for the configuration of the above-described ring of protrusions 213.

[0136] In an embodiment of the present application, a groove C1 along the axial direction of the motor 1 is close to the side wall a1 of the motor 1, and does not exceed the part 211 of the planet carrier 21 extending into the bearing chamber 90 close to one end of the motor 1.

[0137] In an embodiment of the present application, since the groove C1 along the axial direction of the motor 1 is close to the side wall a1 of the motor 1, and does not exceed the part 211 of the planet carrier 21 extending into the bearing chamber 90 close to one end of the motor 1, the oil liquid under the centrifugal force of the rotation of the motor shaft 11 will not directly fall into the bearing chamber 90, but first fall on the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90. In this way, through the centrifugal force of the rotation of the planet carrier 21, the oil liquid can first flow to the other bearing 92 connected to the motor shaft 11 in the bearing chamber 90 through the inner circumferential surface m1 of the part 211 of the planet carrier 21 extending into the bearing chamber 90, so that the other bearing 92 can be better lubricated, and the problem of insufficient lubrication of the other bearing 92 and easy wear can be avoided.

[0138] In an embodiment of the present application, the sun gear 23 of the planetary reducer 2 is integrated with the motor shaft 11 as a unitary shaft. Among them: a groove C1 along the axial direction of the motor 1 is away from the side wall a2 of the motor 1, which is the end surface of the sun gear 23 facing the motor 1.

[0139] In an embodiment of the present application, the motor shaft 11 and the sun gear 23 are integrated as a unitary shaft, which is more stable in structure and more convenient to install. The motor shaft 11 is directly inserted into the planet carrier 21, so that the gear teeth on the motor shaft 11 (i.e. the gear teeth of the sun gear 23) are engaged with the gear teeth of the planet wheel 22 to complete the installation. Compared with the scheme that the motor shaft 11 is connected to the sun gear 23 through splines and the shaft shoulder positions the sun gear, the structure is simpler, the axial size is smaller, and it is more conducive to the miniaturization design of the power assembly.

[0140] In an embodiment of the present application, since the groove C1 along the axial direction of the motor 1 is away from the side wall a2 of the motor 1, which is the end surface of the sun gear 23 facing the motor 1, the groove C1 away from the side wall a2 of the motor 1 extends into the inner cavity of the planet carrier 21. When the oil liquid is in the area away from the motor 1 of the groove C1, under the centrifugal force of the rotation of the motor shaft 11, the oil liquid will be thrown into the inner cavity of the planet carrier 21, such as the gap between the planet wheel 22 and the planet carrier 21 along the axial direction of the motor 1, which can fully lubricate the planet shaft and the planet wheel bearing, and ensure the stable and reliable operation of the planet wheel 22.

[0141] In an embodiment of the present application, referring to Figure 7 and combining Figure 3 It is shown that the shaft shoulder 113 of the motor shaft 11 is used to limit the bearing 92 from moving away from the bearing chamber 90 along the axial direction of the motor 1.

[0142] In an embodiment of the present application, the plurality of first holes 111 are used to communicate the shaft cavity 110a of the portion of the motor shaft 11 extending into the planet carrier 21, and the plurality of second holes 112 are used to communicate the shaft cavity 110b of the portion of the motor shaft 11 not extending into the planet carrier 21. The radial dimension of the shaft cavity 110a of the portion of the motor shaft 11 extending into the planet carrier 21 is smaller than the radial dimension of the shaft cavity 110b of the portion of the motor shaft 11 not extending into the planet carrier 21, and the hole diameter of each first hole 111 is smaller than the hole diameter of each second hole 112.

[0143] In an embodiment of the present application, because the radial dimension of the shaft cavity 110a of the portion of the motor shaft 11 extending into the planet carrier 21 is small, and the hole diameter of the plurality of first holes 111 communicating the shaft cavity 110a of the portion of the motor shaft 11 extending into the planet carrier 21 is small, the jet velocity of the oil at this location is high, but the flow is small, and the main flow is weakly interfered, and the oil can also flow well to the shaft cavity 110b of the portion of the motor shaft 11 not extending into the planet carrier 21, while lubricating the two bearings (91, 92) and the planetary reducer 2. In an embodiment of the present application, because the radial dimension of the shaft cavity 110a of the portion of the motor shaft 11 extending into the planet carrier 21 is small, the strength of the portion of the motor shaft 11 extending into the planet carrier 21 is also taken into account, so that the motor shaft 11 is not easily broken.

[0144] In an embodiment of the present application, because the radial dimension of the shaft cavity 110b of the portion of the motor shaft 11 not extending into the planet carrier 21 is large, and the hole diameter of the plurality of second holes 112 communicating the shaft cavity 110b of the portion of the motor shaft 11 not extending into the planet carrier 21 is large, the flow velocity of the oil at this location is low, but the flow is large, and the rotor 12 of the motor 1 can also be well lubricated and cooled.

[0145] The lubricating oil path of the planetary reducer toward the motor side in the power assembly is introduced above, and the lubricating oil path of the planetary reducer away from the motor side will be introduced below. Figures 8-19 The lubricating oil path of the planetary reducer away from the motor side will be introduced below. The lubricating oil paths of the two sides in the present application can exist separately or simultaneously.

[0146] At present, in the working process of the power assembly 100, the planetary reducer converts high-speed kinetic energy into greater torque output, which makes the gear teeth of the sun gear, the gear teeth of the planet gears, the planet gear bearings and other components in the planet carrier very easy to wear out.

[0147] Please refer to Figure 8 and Figure 9 , Figure 8 Another partial structure sectional view of the power assembly 100 provided by an embodiment of the present application is shown in detail, Figure 8 is a sectional view along the axial direction of the motor along the central axis of the motor shaft, Figure 9 is Figure 8Another partial structural sectional view of the power assembly 100 is shown after the power assembly 100 rotates an angle along the circumference of the motor 1, Figure 8 and Figure 9 The oil flow direction is indicated by the dashed arrow in the figure.

[0148] In an embodiment of the present application, an oil baffle 3 is arranged on the side of the planet carrier 21 away from the motor 1. A gap g3 is formed between the oil baffle 3 and the planet carrier 21. Part of the oil in the housing 00 of the power assembly 100 can be collected in the gap g3. For example, when other rotating components in the housing 00 rotate, part of the oil can be thrown into the gap g3 between the oil baffle 3 and the planet carrier 21. The oil can enter the planet carrier 21 through the gap g3 to lubricate the teeth and / or bearings in the planet carrier 21. Specifically, the oil is delivered to the planet carrier 21 through the gap g3 between the oil baffle 3 and the planet carrier 21. The oil is delivered to the teeth of the sun gear 23, the teeth of the planet gears 22, the planet gear bearings 222, etc. through the planet carrier 21. The teeth of the sun gear 23, the teeth of the planet gears 22, the planet gear bearings 222, etc. in the planet carrier 21 are fully lubricated. The planetary reducer 2 can operate stably for a long time. The service life of the planetary reducer 2 is prolonged. The power assembly 100 can operate stably for a long time.

[0149] In an embodiment of the present application, the oil is collected and delivered to the planet carrier 21 through the gap g3 between the oil baffle 3 and the planet carrier 21. The oil baffle 3 does not need to have a hollow channel inside for transmitting oil. The oil baffle 3 can be designed to be lighter and thinner. The structure is simple. The processing difficulty is low. The cost is low. The practicality is higher.

[0150] Some embodiments of the present application will be described below. Figure 6 , Figure 8 and Figure 10 The oil inlet design of some embodiments of the present application will be described below.

[0151] Please refer to Figure 8 In an embodiment of the present application, the oil pipe 4 of the power assembly 100 extends into the shaft cavity 2120 of the output shaft 212. In an embodiment of the present application, the oil pipe 4 of the power assembly 100 can extend from the outside of the housing 00 into the inside of the housing 00 (for example, from the side of the housing 02 away from the motor into the housing 02), and then extend into the shaft cavity 2120 of the output shaft 212 of the planet carrier 21. In this way, the oil can be delivered to the shaft cavity 2120 of the output shaft 212 of the planet carrier 21 through the oil pipe 4.

[0152] In an embodiment of the present application, please refer to Figure 8The oil is delivered into the shaft cavity 110 of the motor shaft 11 through the oil pipe 4 from the shaft end face of the motor shaft 11 towards the inlet of the planet carrier 21, and is delivered into the shaft cavity 2120 of the output shaft 212 of the planet carrier 21 through one or more oil outlets on the pipe wall of the oil pipe 4.

[0153] Figure 10 For Figure 8 The structural diagram of the planet carrier in the embodiment is shown in one view. Referring to Figure 10 and the foregoing Figure 6 In one embodiment of the present application, the output shaft 212 of the planet carrier 21 comprises a plurality of first oil holes T1, and the protrusion on the side of the planet carrier 21 away from the motor 1 comprises a plurality of second oil holes T2, one end of each first oil hole T1 is used to communicate with the shaft cavity 2120 of the output shaft 212, the other end of each first oil hole T1 is used to communicate with one end of a corresponding second oil hole T2, and the other end of each second oil hole T2 is used to output oil. In the axial direction of the motor 1, the other end of each second oil hole T2 is located between one end of an oil baffle ring 3 towards the output shaft 212 and the planet carrier 21.

[0154] In the embodiment of the present application, the oil in the shaft cavity 2120 of the output shaft 212 of the planet carrier 21 is discharged through the plurality of first oil holes T1 of the output shaft 212 of the planet carrier 21 and the plurality of second oil holes T2 comprised by the protrusion on the side of the planet carrier 21 away from the motor 1. Specifically, under the action of the centrifugal force generated by the rotation of the output shaft 212 of the planet carrier 21, the oil flows through the first oil holes T1 and the second oil holes T2 in turn. Since the second oil holes T2 are located on the protrusion on the side of the planet carrier 21 away from the motor 1 (as shown in Figure 10 Therefore, the oil flowing out of the second oil holes T2 is more convenient to flow into the gap g3 comprised between the oil baffle ring 3 and the planet carrier 21. In this way, sufficient oil can be provided into the gap g3, which is conducive to delivering more oil into the planet carrier 21, fully lubricating the teeth of the sun gear 23, the teeth of the planet gears 22, the planet gear bearings 222 and other components in the planet carrier 21, making the planetary reducer 2 operate stably for a long time, prolonging the service life of the planetary reducer 2, and further ensuring the power assembly 100 to operate stably for a long time.

[0155] In the above-mentioned embodiment, the planet carrier 21 and the output shaft 212 of the planet carrier 21 are designed in a split type, i.e. combined Figure 6 , a weld is comprised between the planet carrier 21 and the output shaft 212 of the planet carrier 21. At this time, both the first oil holes T1 and the second oil holes T2 are comprised. The part of the output shaft 212 of the planet carrier 21 towards one end of the planet carrier 21 protrudes into the central hole of the planet carrier 21, and the L-shaped surface of the output shaft 212 of the planet carrier 21 towards one end of the planet carrier 21 is welded with the peripheral surface of the central hole of the planet carrier 21 and the end face on the side of the planet carrier 21 away from the motor 1, so that the connection is highly reliable.

[0156] In another embodiment of the present application, the planet carrier 21 and the output shaft 212 of the planet carrier 21 are designed in one piece (not shown), such as casted in one piece, so that the planet carrier and the output shaft do not need to be assembled subsequently, and the assembly process can be simplified. In this embodiment, it is not distinguished which is the first oil hole T1 and which is the second oil hole T2, that is, only the whole oil hole formed after combination communicates the shaft cavity 2120 of the output shaft 212 of the planet carrier 21, and the oil liquid in the shaft cavity 2120 of the output shaft 212 of the planet carrier 21 is guided out to the gap g3 included between the oil baffle 3 and the planet carrier 21. This whole oil hole can be considered to be on the planet carrier 21 or on the output shaft 212 of the planet carrier 21, and the boundary between the planet carrier 21 and the output shaft 212 of the planet carrier 21 does not need to be defined.

[0157] In an embodiment of the present application, continuing to refer to Figure 6 , the peripheral surface of the shaft cavity 2120 of the output shaft 212 of the planet carrier 21 includes an inclined section E3 and a groove C2, the large end of an inclined section E3 is connected to a groove C2, and a groove C2 is recessed towards the output shaft 212 in the radial direction of the motor 1, and the end of each first oil hole T1 for communicating the shaft cavity 2120 of the output shaft 212 is located at the bottom surface of a groove C2.

[0158] In an embodiment of the present application, an inclined section E3 includes a large end with a large radial dimension and a small end with a small radial dimension, and since the large end of an inclined section E3 is connected to a groove C2, the oil liquid flowing into the output shaft 212 from the oil pipe 4 can flow to a groove C2 through an inclined section E3. Since the end of each first oil hole T1 for communicating the shaft cavity 2120 of the output shaft 212 is located at the bottom surface of a groove C2, the oil liquid accumulated in the groove C2 can flow into the gap g3 included between the oil baffle 3 and the planet carrier 21 through the first oil hole T1 and the second oil hole T2 in turn, so that sufficient oil liquid can be provided to the gap g3.

[0159] In an embodiment of the present application, continuing to refer to Figure 6 , the end of the shaft cavity 2120 of the output shaft 212 towards the inner cavity of the planet carrier 21 in the axial direction of the motor 1 includes a bell mouth E2, and the large end of the bell mouth E2 is towards the inner cavity of the planet carrier 21.

[0160] In an embodiment of the present application, in combination with Figure 6 and Figure 8As shown, the flared end E2 refers to a hollow structure with a small opening at one end (called the small opening end) and a large opening at the other end (called the large opening end). Since the large opening end of the flared end E2 faces the inner cavity of the planetary carrier 21, the oil flowing into the output shaft 212 through the oil pipe 4 can flow through the flared end E2 into the inner cavity of the planetary carrier 21, providing sufficient lubrication for the teeth of the sun gear 23, the teeth of the planetary gears 22, the planetary gear bearings 222, and other components inside the planetary carrier 21. This ensures the long-term stable operation of the planetary reducer 2, extends the service life of the planetary reducer 2, and thus guarantees the long-term stable operation of the powertrain.

[0161] In one embodiment of this application, along the axial direction of the planetary carrier 21 of the motor 1 toward the motor 1, an inclined segment E3, a groove C2, and a flared mouth E2 are connected in series.

[0162] The following is combined with Figures 8-12 This paper will introduce some relevant features of the planetary carrier 21 on the side away from the motor 1 in the embodiments of this application.

[0163] Figure 11 for Figure 8 A structural diagram of the planetary carrier 21 in the embodiment from another perspective. Figure 12 for Figure 8 An assembly structure diagram of a portion of the structure in the embodiment. (Combined with...) Figure 8 , Figures 10-12 As shown, in one embodiment of this application, the planetary carrier 21 includes a plurality of planetary shaft holes 201 on the side away from the motor 1. One end of each planetary shaft hole 201 along the axial direction of the motor 1 is connected to a gap g3, and the other end is connected to the inner cavity of the planetary carrier 21. One end of each planetary shaft 221 of the planetary reducer 2 along the axial direction of the motor 1 extends into a corresponding planetary shaft hole 201. Each planetary gear 22 of the planetary reducer 2 is connected to the outer peripheral surface of a corresponding planetary shaft 221 through a bearing 222. The interior of each planetary shaft 221 includes a flow channel 220. The inlet of the flow channel 220 of each planetary shaft 221 is located on the shaft end face of the planetary shaft 221 facing a gap g3, and one or more outlets of the flow channel 220 of each planetary shaft 221 are located on the outer peripheral surface of the planetary shaft 221.

[0164] In the embodiments of this application, since each planetary shaft 221 includes a flow channel 220 inside, the oil collected in a gap g3 between an oil baffle ring 3 and the planet carrier 21 can flow through the flow channel of each planetary shaft 221 to the planetary gear bearing 222 on the outer circumference of the planetary shaft 221, thereby achieving sufficient lubrication of the planetary gear bearing 222, extending the service life of the planetary gear bearing 222, and ensuring the smooth and reliable operation of the planetary reducer 2. In the embodiments of this application, the oil after lubricating the planetary gear bearing 222 can also flow to the gear ring 24 to lubricate the inner tooth surface of the gear ring 24 and the teeth of the planetary gears 22.

[0165] In an embodiment of the present application, as shown in Figure 8 each flow channel 220 of the planetary shaft 221 comprises an axial flow channel 220a parallel to the axial direction of the motor 1 and one or more radial flow channels 220b parallel to the radial direction of the motor 1, one end of the axial flow channel 220a is the inlet of the flow channel 220 of the planetary shaft 221, and one end of each radial flow channel 220b is connected to one axial flow channel 220a, and the other end of each radial flow channel 220b is an outlet of the flow channel 220 of the planetary shaft 221.

[0166] In an embodiment of the present application, the oil first flows into an axial flow channel 220a from a gap g3, and then flows to the planetary wheel bearing 222 through one or more radial flow channels 220b under the centrifugal force generated by the rotation of the planetary shaft 221, thereby achieving sufficient lubrication of the planetary wheel bearing 222.

[0167] In an embodiment of the present application, continuing to refer to Figure 8 the flow cross section of the axial flow channel 220a of each planetary shaft 221 is larger than the flow cross section of the radial flow channel 220b of the planetary shaft 221. In an embodiment of the present application, since the flow cross section of the axial flow channel 220a is larger than the flow cross section of the radial flow channel 220b, more oil can be accumulated in the axial flow channel 220a, so that each radial flow channel 220b has sufficient oil output, thereby achieving sufficient lubrication of different positions of the planetary wheel bearing 222.

[0168] In an embodiment of the present application, referring to Figure 12 the shaft end face of the planetary shaft 221 facing the gap g3 further comprises a threaded hole s2, the threaded hole s2 is offset from the central axis of the planetary shaft 221 along the axial direction of the motor 1, and the inlet s0 of the planetary shaft 221 surrounds the central axis of the planetary shaft 221.

[0169] In an embodiment of the present application, since the shaft end face of the planetary shaft 221 facing the gap g3 further comprises a threaded hole s2, each planetary shaft 221 can be fixed with a oil retaining ring 3 by a connecting member s21 such as a bolt or a screw. Since the threaded hole s2 is offset from the central axis of the planetary shaft 221 along the axial direction of the motor 1, the oil retaining ring 3 achieves axial and circumferential positioning of each fixed planetary shaft 221, and since the inlet s0 of the planetary shaft 221 surrounds the central axis of the planetary shaft 221, the inlet of the planetary shaft 221 is not easily displaced, and the oil in the gap g3 between the oil retaining ring 3 and the planet carrier 21 can be stably transported from the inlet of the planetary shaft 221 to the flow channel 220 of the planetary shaft 221, thereby facilitating the lubrication of the planetary wheel bearing 222.

[0170] In the embodiments of the present application, in combination with Figure 12 As shown in the figure, the oil baffle 3 includes a waist-shaped hole s20, which is used to pass through the threaded hole s2 of the planet shaft 221 by bolt connection. By arranging the waist-shaped hole s20, the oil baffle 3 is easier to install and position when connected with the planet shaft 221, and has high practicability.

[0171] In the embodiments of the present application, continuing to refer to Figure 12 The oil baffle 3 includes a hole s10, and the planet carrier 21 away from the motor 1 side includes a hole s1. A bolt or screw connector s11 can pass through the hole s10 and the hole s1 to fix the oil baffle 3 with the planet carrier 21. The bolt or screw connector has the advantages of convenient installation and reliable connection.

[0172] In an embodiment of the present application, in combination with Figures 8-12 As shown in the figure, the planet carrier 21 away from the motor 1 side further includes a plurality of recessed holes 202. The openings of the plurality of recessed holes 202 are directed to a gap g3 along the axial direction of the motor 1. The side wall of each recessed hole 202 away from the sun gear 23 along the radial direction of the motor 1 includes one or more through holes 202a, which are used to deliver oil to the ring gear 24 of the planetary reducer 2.

[0173] In the embodiments of the present application, since the planet carrier 21 away from the motor 1 side includes a plurality of recessed holes 202, the openings of the plurality of recessed holes 202 are directed to a gap g3 between the oil baffle 3 and the planet carrier 21, so that the oil in the gap g3 can also enter the plurality of recessed holes 202. Since the side wall of each recessed hole 202 away from the motor shaft 11 along the radial direction of the motor 1 includes one or more through holes 202a, the oil in each recessed hole 202 is thrown to the inner tooth surface of the ring gear 24 through the one or more through holes 202a under the centrifugal force of the rotation of the planet carrier 21, so as to realize the lubrication of the inner tooth surface of the ring gear 24. Moreover, since the planetary gear 22 is engaged with the ring gear 24 and the sun gear 23, the oil can also lubricate the gear teeth of the planetary gear 22 and the gear teeth of the sun gear 23.

[0174] In an embodiment of the present application, in combination with Figures 10-12 As shown in the figure, along the axial direction of the motor 1, the plurality of recessed holes 202 are distributed between the plurality of planetary gears 22. In this way, the volume of the recessed hole 202 can be enlarged to accommodate more oil, the axial space of the planet carrier 21 occupied by the recessed hole 202 can be reduced, the weight of the planet carrier 21 is also reduced, and the lightweight design of the planet carrier 21 is realized.

[0175] In the embodiments of the present application, referring to Figure 11 The bottom wall of the plurality of recessed holes 202 includes a baffle 2021. In combination with Figure 5As shown, the baffle 2021 separates the two recesses 202 on both sides of the planet carrier 21 along the axial direction of the motor 1. In this way, the recess 202 on the side of the planet carrier 21 facing the motor 1 is used to receive oil in the gap g2, and the recess 202 on the side of the planet carrier 21 facing away from the motor 1 is used to receive oil in the gap g3.

[0176] The following will be described in detail Figures 12-19 The oil baffle 3 in some embodiments of the present application will be described in detail.

[0177] Figure 13 A structural diagram of the oil baffle 3 provided in an embodiment of the present application is shown in Figure 13 As shown in Figure 12 The side of the oil baffle 3 facing the planet carrier in an embodiment of the present application is shown in Figure 13 and Figure 12 As shown, in an embodiment of the present application, the end d0 of the oil baffle 3 facing the output shaft 212 is inclined toward the side away from the planet carrier 21 along the axial direction of the motor 1 from the end d01 of the output shaft 212 away from the planet carrier 21 to the end d02 of the output shaft 212 close to the planet carrier 21.

[0178] In an embodiment of the present application, since the end d0 of the oil baffle 3 facing the output shaft 212 is inclined toward the side away from the planet carrier 21 along the axial direction of the motor 1 from the end d01 of the output shaft 212 away from the planet carrier 21 to the end d02 of the output shaft 212 close to the planet carrier 21, the inner circumferential end of the oil baffle 3 includes an oil guiding inclined surface m2. After the oil is thrown to the inclined surface m2, the oil will flow into a gap g3 between the oil baffle 3 and the planet carrier 21 through the inclined surface m2, thereby achieving better oil collection effect.

[0179] In an embodiment of the present application, since the end d0 of the oil baffle 3 facing the output shaft 212 is inclined toward the side away from the planet carrier 21 along the axial direction of the motor 1 from the end d01 of the output shaft 212 away from the planet carrier 21 to the end d02 of the output shaft 212 close to the planet carrier 21, on the one hand, the inclined surface m2 is formed, and on the other hand, the part of the oil baffle 3 facing the output shaft 212 of the planet carrier 21 can be made thinner while ensuring that the inclined surface m2 has a larger inclination angle and better oil receiving effect, thereby achieving the lightweight design of the oil baffle 3.

[0180] In an embodiment of the present application, referring to Figure 13 and in combination with Figure 12 As shown, the part of the oil baffle 3 facing the output shaft 212 includes an annular groove C3, the annular groove C3 surrounds the output shaft 212, the side of the annular groove C3 facing the planet carrier 21 and the side of the annular groove C3 facing the output shaft 212 are both open, and a gap g3 is formed between the annular groove C3 and the planet carrier 21.

[0181] In the embodiment of the present application, the portion of the oil baffle ring 3 towards the side of the output shaft 212 comprises an annular groove C3, which surrounds the output shaft 212 and is open towards the side of the planet carrier 21 and the side of the output shaft 212, so that the annular groove C3 and the planet carrier 21 can form the gap g3 described above, and the end of the gap g3 towards the output shaft 212 of the planet carrier 21 is the opening for collecting oil. Here, only a simple machining of the oil baffle ring 3 is required to form an annular groove on the oil baffle ring 3, and then a gap g3 for collecting oil can be generated between the oil baffle ring 3 and the planet carrier 21, so that the oil baffle ring 3 is easy to machine and produce, and the cost is low.

[0182] In a combined embodiment of the present application, referring to Figure 13 , and combining Figure 12 , the portion of the side wall of the annular groove C3 towards the center of the oil baffle ring 3 (i.e. towards the output shaft 212) is the inclined surface m2 described above.

[0183] In an embodiment of the present application, continuing to refer to Figure 13 and Figure 12 , the annular groove C3 comprises a ring of annular bottom surfaces m3, which is arranged along the radial direction of the motor 1 and towards the output shaft 212; wherein: the ring of annular bottom surfaces m3 along the circumferential direction of the motor 1 comprises a plurality of bottom surfaces m31, the radial dimension of the leading end of each bottom surface m31 is smaller than the radial dimension of the trailing end, the leading end of each adjacent two bottom surfaces m31 is connected, the trailing end of each adjacent two bottom surfaces m31 is connected, and a gap g3 is arranged in the region between the trailing ends of each adjacent two bottom surfaces m31 for conveying oil to the planet carrier 21.

[0184] In a combined embodiment of the present application, combining Figure 13 and the above Figure 8 , the oil is conveyed to the flow channel 220 of the corresponding planet shaft 221 through the region between the trailing ends of each adjacent two bottom surfaces m31. In this combined embodiment, more oil can flow into the flow channel of each planet shaft 221, fully lubricate each planet wheel bearing 222, prolong the service life of each planet wheel bearing 222, and ensure the smooth and reliable operation of the planetary reducer 2.

[0185] In the embodiment of the present application, the annular groove C3 comprises a ring-shaped bottom surface m3, and the ring-shaped bottom surface m3 along the circumferential direction of the motor 1 comprises a plurality of bottom surfaces m31, and the radial dimension of the leading end of each bottom surface m31 is smaller than the radial dimension of the trailing end, so that under the action of the rotational centrifugal force of the oil baffle 3, the oil can flow from the leading end of each bottom surface m31 to the trailing end along the bottom surface m31, and further flow to a gap g3 between the trailing ends of each adjacent two bottom surfaces m31, and then transport the oil to the inside of the carrier 21 along the axial direction of the motor 1. Compared with the scheme of arranging a complex oil passage in the inside of an oil baffle 3, the annular groove C3 of the embodiment of the present application is simpler, easier to process, lower in cost, and higher in practicability.

[0186] In an embodiment of the present application, the annular groove C3 comprises a ring-shaped bottom surface m3, and the ring-shaped bottom surface m3 along the radial direction of the motor 1 is directed towards the output shaft 212; wherein: the ring-shaped bottom surface m3 along the circumferential direction of the motor 1 comprises a plurality of bottom surfaces m31, and the radial dimension of the leading end of each bottom surface m31 is smaller than the radial dimension of the trailing end, and the leading ends of each adjacent two bottom surfaces m31 are connected, and the trailing ends of each adjacent two bottom surfaces m31 are connected. A groove 302 is arranged between the leading ends of each adjacent two bottom surfaces m31, and the groove 302 along the radial direction of the motor 1 is recessed in a direction away from the output shaft 212, and the groove 302 along the axial direction of the motor 1 is open to one side of the carrier 21, and the opening of each groove 302 is used to output oil.

[0187] In the embodiment of the present application, the annular groove C3 comprises a ring-shaped bottom surface m3, and the ring-shaped bottom surface m3 along the circumferential direction of the motor 1 comprises a plurality of bottom surfaces m31, and the radial dimension of the leading end of each bottom surface m31 is smaller than the radial dimension of the trailing end, and a groove is arranged between the leading ends of each adjacent two bottom surfaces m31, so that under the action of the rotational centrifugal force of the oil baffle 3, the oil between the leading ends of each adjacent two bottom surfaces m31 can fall into the groove 302 arranged between the leading ends of each adjacent two bottom surfaces m31, and then transport the oil to the inside of the carrier 21 through the opening of the groove 302 to one side of the carrier 21. Compared with the scheme of arranging a complex oil passage in the inside of an oil baffle 3, the annular groove C3 of the embodiment of the present application is simpler, easier to process, lower in cost, and higher in practicability.

[0188] In an embodiment of the present application, continuing to refer to Figure 13, one side of the oil baffle ring 3 facing the planetary carrier 21 includes a plurality of protrusions 301, each protrusion 301 protrudes towards one side of the motor 1 along the axial direction of the motor 1. Each protrusion 301 includes another groove 303, the other groove 303 is recessed towards the direction away from the output shaft 212 along the radial direction of the motor 1, one end of the other groove 303 is used to communicate with the opening of the corresponding one groove 302 towards the side of the planetary carrier 21 along the axial direction of the motor 1, and the other end of the other groove 303 is used to output oil into the planetary carrier 21.

[0189] In the embodiment of the present application, since one side of the oil baffle ring 3 facing the planetary carrier 21 includes a plurality of protrusions 301, each protrusion 301 includes another groove 303, and the other groove 303 communicates with one groove 302 included between the first end of each adjacent two bottom surfaces m31 along the axial direction of the motor 1, the oil in the one groove 302 can flow into the planetary carrier 21 through the other groove 303, the oil transmission is more stable, and it is easier to realize the lubrication of some teeth and bearings in the planetary carrier 21. For example, the teeth of the sun gear 23, the teeth of the planetary gear 22, the planetary gear bearing 222 and other components in the planetary carrier 21 are fully lubricated, so that the planetary reducer 2 can operate stably for a long time, the service life of the planetary reducer 2 is prolonged, and the long-term stable operation of the power assembly 100 is ensured.

[0190] In a combined embodiment of the present application, in combination with Figure 13 and the foregoing Figure 8 , Figure 9 , the oil is transported to the corresponding plurality of recessed holes 202 through one groove 302 (or one groove 302+another groove 303) between the first end of each adjacent two bottom surfaces m31 by the foregoing gap g3. In this combined embodiment, more oil can flow into the plurality of recessed holes 202, and then the inner tooth surface of the ring gear 24 can be lubricated through one or more through holes 202a.

[0191] Figure 14 Another partial structure sectional view of a power assembly provided in an embodiment of the present application is provided, specifically, Figure 14 is also a sectional view cut along the central axis of the motor shaft along the axial direction of the motor, Figure 14 compared with Figure 8 , the single-layer structure oil baffle ring 3 is replaced by a multi-layer structure oil baffle ring 3.

[0192] In an embodiment of the present application, as shown in Figure 14 , one oil baffle ring 3 includes two outer layers (31, 33) and one intermediate layer 32, and one intermediate layer 32 is located between the two outer layers (31, 33) along the axial direction of the motor 1; wherein: the material of one intermediate layer 32 includes damping material, and the material of the two outer layers (31, 33) includes metal material.

[0193] In the embodiment of the present application, since one oil retaining ring 3 comprises two outer layers (31, 33) and one intermediate layer 32, the material of one intermediate layer 32 comprises damping material, and the material of two outer layers (31, 33) comprises metal material, the vibration of the planet carrier 21 can be absorbed by one intermediate layer 32, and the NVH (Noise, Vibration, Harshness) performance of the power assembly 100 is improved.

[0194] In one embodiment of the present application, the damping material comprises butyl rubber. The molecular chain structure of butyl rubber endows the material with good viscoelasticity, and when subjected to stress, the mechanical energy is converted into heat energy and dissipated through intermolecular friction, thereby effectively reducing the vibration amplitude of the planet carrier 21 and inhibiting the propagation of noise. Butyl rubber has the advantages of aging resistance, deformation resistance, slow damping effect attenuation, and long service life.

[0195] Figure 15 An exploded view of one oil retaining ring 3 provided in an embodiment of the present application from the side facing away from the motor 1, Figure 16 An exploded view of one oil retaining ring 3 provided in an embodiment of the present application from the side facing the motor 1, Figure 17 A structural view of one outer layer of an oil retaining ring provided in an embodiment of the present application, Figure 18 A structural view of another outer layer of an oil retaining ring provided in an embodiment of the present application, Figure 19 A structural view of one intermediate layer of an oil retaining ring provided in an embodiment of the present application. In combination Figures 15-19 As shown in the figure, in one embodiment of the present application, one oil retaining ring 3 comprises holes s10 and waist-shaped holes s20, which are respectively formed by the combination of three hole structures on two outer layers (31, 33) and one intermediate layer 32 of one oil retaining ring 3. In the embodiment of the present application, as shown in the figure, Figure 15 As shown in the figure, the waist-shaped hole s20 comprises a baffle in the hole structure of the outer layer 33, which is used to limit the bolts passing through the waist-shaped hole s20 from escaping towards the side of the motor 1.

[0196] In one embodiment of the present application, in combination Figure 16 As shown in the figure, the side of the oil retaining ring 3 in the embodiment of the present application facing the planet carrier 21 comprises a plurality of protrusions 301 located near one outer layer 31 of the planet carrier.

[0197] In one embodiment of the present application, the two surfaces of the two outer layers (31, 33) opposite along the axial direction of the motor 1 respectively comprise two annular protrusions (z1, z2, z3, z4) protruding towards the opposite side, and the two annular protrusions (z1, z2) in one surface along the axial direction of the motor 1 are opposite to the two annular protrusions (z3, z4) in the other surface to enclose a cavity, such as Figure 17 the annular protrusion z1 in the figure Figure 18 The annular protrusion z3 in the middle is in contact. Figure 17 The annular protrusion z2 in the middle and Figure 18 The annular protrusion z3 contacts to enclose a cavity, and the intermediate layer 32 is interference-fitted into a cavity.

[0198] In the embodiments of this application, a cavity is formed by two annular protrusions (z1, z2, z3, z4) on the two opposing surfaces of the two outer layers (31, 33). The middle layer 32 is interference-fitted into this cavity, making the three-layer structure design simple and easy to assemble. Furthermore, the middle layer 32 included in the oil baffle ring 3 does not easily affect the function of the gap g3 between the oil baffle ring 3 and the planetary carrier 21 for collecting oil and conveying oil to the planetary carrier 21.

[0199] In the embodiments of this application, combined with Figure 17 and Figure 18 As shown, a portion of a groove 302 of the oil baffle ring 3 is located on an outer layer 33, and another portion is located on another outer layer 31. The other groove 303 of the oil baffle ring 3 and the protrusion where the other groove 303 is located are located on another outer layer 31.

[0200] In the embodiments of this application, such as Figure 19 As shown, the intermediate layer includes a groove 304, which is used to avoid the portion of the annular protrusions (z2, z4) protruding in the direction away from the output shaft 212 of the planet carrier 21, so as to form a groove 302 on the side of the annular protrusions (z2, z4) facing the output shaft 212 of the planet carrier 21.

[0201] In one embodiment of this application, the two outer layers (31, 33) are radially close to the output shaft 212 of the planetary carrier 21, and the surfaces of the two annular protrusions (z2, z4) facing the output shaft 212 of the planetary carrier 21 are an annular bottom surface m3 of an oil baffle ring 3 (see reference). Figure 13 Of the two outer layers (31, 33), the outer layer 33, which is farther from the planet carrier 21, has a side surface facing the planet carrier 21. This side surface, together with a ring bottom surface m3, forms an annular groove C3 on an oil baffle ring 3 as described above.

[0202] In the embodiment of the present application, since the two outer layers (31, 33) are close to the two annular protrusions (z2, z4) of the output shaft 212 of the planetary carrier 21 along the radial direction of the motor 1, the surface of the two outer layers (31, 33) away from the output shaft 212 of the planetary carrier 21 is a ring-shaped bottom surface m3 of a ring-shaped groove C3 of an oil baffle ring 3, and the surface of one outer layer 33 of the two outer layers (31, 33) away from the planetary carrier 21 is a side surface of a ring-shaped groove C3, so that the ring-shaped groove C3 included in the oil baffle ring 3 is easier to form, and since the structure of the two outer layers (31, 33) of the oil baffle ring 3 is simplified, the two outer layers (31, 33) are simple in structure and low in processing difficulty.

[0203] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, and any person skilled in the art can easily think of changes or replacements within the technical scope disclosed in the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A powertrain, characterized in that, The powertrain housing includes a bearing chamber. The motor shaft of the motor in the powertrain passes through the bearing chamber and extends into the planetary carrier of the planetary reducer in the powertrain. A portion of the planetary carrier facing the motor extends into the bearing chamber. One bearing in the bearing chamber connects to the portion of the planetary carrier extending into the bearing chamber, and another bearing connects to the motor shaft. Wherein: The motor shaft includes a plurality of first holes for outputting oil from the shaft cavity of the motor shaft. A gap is included between the motor shaft and the portion of the planetary carrier that extends into the bearing chamber, and the gap is used to connect the plurality of first holes and the bearing chamber.

2. The powertrain according to claim 1, characterized in that, The planetary carrier extends into the bearing housing, and the end of the portion of the planetary carrier that is closer to the motor is a flared end, with the larger end of the flared end facing the other bearing.

3. The powertrain according to claim 2, characterized in that, The horn-shaped opening includes two horn sections. The larger end of the first horn section is connected to the smaller end of the second horn section, and the larger end of the second horn section faces the other bearing. Along the axial direction of the motor, the length of the second horn section is greater than the length of the first horn section, and the inclination of the second horn section is greater than the inclination of the first horn section.

4. The powertrain according to any one of claims 1-3, characterized in that, The inner circumferential surface of the portion of the planetary carrier extending into the bearing chamber includes a ring of protrusions. Along the radial direction of the motor, the ring of protrusions protrudes toward the motor shaft and surrounds the motor shaft. Along the axial direction of the motor, the outlet of a portion of the plurality of first holes is located on the side of the ring of protrusions facing the motor, and the outlet of another portion of the first holes is located on the side of the ring of protrusions away from the motor.

5. The powertrain according to claim 4, characterized in that, The distance from the axial portion of the protrusion along the motor to the end of the planetary carrier that extends into the bearing chamber near the motor is less than the distance to the inner wall of the planetary carrier's cavity near the motor.

6. The powertrain according to any one of claims 1-5, characterized in that, The thickness of the portion of the planetary carrier extending into the bearing housing along the radial direction of the motor is less than the thickness of the portion of the planetary carrier on the side facing the motor that is opposite to the planetary gear of the planetary reducer along the axial direction of the motor.

7. The powertrain according to any one of claims 1-6, characterized in that, Along the axial direction of the motor, one bearing and the other bearing are spaced apart. The outer diameter of the one bearing is larger than that of the other bearing, and the inner diameter of the one bearing is smaller than that of the other bearing.

8. The powertrain according to any one of claims 1-7, characterized in that, One of the bearings is a tapered roller bearing, and the tapered bottom of the tapered roller bearing faces away from the other bearing.

9. The powertrain according to any one of claims 1-8, characterized in that, The planetary carrier facing the motor includes another gap between itself and the housing along the motor axis. One end of the other gap is used to connect the side of the bearing facing away from the motor, and the other end is used to connect the gap between the planetary carrier and the gear ring of the planetary reducer.

10. The powertrain according to claim 9, characterized in that, The planetary carrier includes a plurality of recesses on the side facing the motor, with the openings of the plurality of recesses facing the other gap along the axial direction of the motor. Along the radial direction of the motor, each recess includes one or more through holes on the sidewall away from the motor shaft. The one or more through holes are used to deliver oil to the inner tooth surface of the gear ring of the planetary reducer.

11. The powertrain according to any one of claims 1-10, characterized in that, The outer peripheral surface of the motor shaft includes a groove, which is recessed into the motor shaft radially from the motor, and the inner wall of the groove and the portion of the planetary carrier extending into the bearing chamber form a gap.

12. The powertrain according to claim 11, characterized in that, Along the axial direction of the motor, a groove is located near the side wall of the motor, not extending beyond the portion of the planetary carrier that extends into the bearing chamber near one end of the motor.

13. The powertrain according to claim 11 or 12, characterized in that, The sun gear of the planetary reducer is integrated with the motor shaft as a single shaft; wherein: along the axial direction of the motor, a groove away from the side wall of the motor is the end face of the sun gear facing the motor.

14. The powertrain according to any one of claims 1-13, characterized in that, The motor shaft includes a plurality of second holes, one end of which is used to communicate with the shaft cavity of the motor shaft, and the other end is used to supply oil to the rotor of the motor; wherein: The plurality of first holes are used to connect the shaft cavity of the portion of the motor shaft that extends into the planetary carrier, and the plurality of second holes are used to connect the shaft cavity of the portion of the motor shaft that does not extend into the planetary carrier; The radial dimension of the cavity of the portion of the motor shaft that extends into the planetary carrier is smaller than the radial dimension of the cavity of the portion of the motor shaft that does not extend into the planetary carrier, and the diameter of each first hole is smaller than the diameter of each second hole.

15. A vehicle, characterized in that, include: The wheel and the powertrain as described in any one of claims 1-14, the powertrain being used to drive the wheel to rotate.

Images