Power assembly with bearing wave pad protection function and electric vehicle

Abstract

The utility model provides a power assembly with a bearing wave pad protection function and an electric vehicle. A shell of the power assembly comprises a bearing groove, one bearing groove is used for containing one ball bearing and one annular bearing wave pad, the outer ring of one ball bearing is embedded into one bearing groove, and the inner ring of one ball bearing is fixedly arranged on the peripheral face of a motor shaft of a driving motor in the power assembly in a sleeving mode. One side of one bearing wave pad in the axial direction of the motor shaft is used for abutting against one side of one ball bearing, and the other side of the bearing wave pad is used for abutting against the groove bottom of the bearing groove. And the peripheral surface of one bearing wave pad is spaced from the groove wall of one bearing groove in the radial direction of the motor shaft. According to the power assembly provided by the invention, the bearing wave pad is protected by reserving the deformation space, so that the motor shaft is reliably buffered.

Description

Technical Field

[0001] This application relates to the field of electric vehicle technology, specifically to a powertrain with bearing pad protection function and an electric vehicle. Background Technology

[0002] With the development of electric vehicles, the power density of powertrains is constantly increasing, and the requirements for noise and vibration control (NVH) performance of electric vehicles are also rising. To ensure the NVH performance of electric vehicles during long-term operation, reliable buffering is needed for vibration sources in the powertrain. Utility Model Content

[0003] This application provides a powertrain with bearing gasket protection and an electric vehicle, which protects the bearing gasket by reserving deformation space, thereby achieving reliable buffering of the motor shaft. Specifically, this application includes the following solutions:

[0004] In a first aspect, this application provides a powertrain with a bearing washer protection function. The powertrain housing includes a bearing groove for accommodating a ball bearing and an annular bearing washer. The outer ring of the ball bearing is embedded in the bearing groove, and the inner ring of the ball bearing is fixedly sleeved on the outer circumferential surface of the motor shaft of the drive motor in the powertrain. Along the axial direction of the motor shaft, one side of the bearing washer abuts against one side of the ball bearing, and the other side of the bearing washer abuts against the bottom of the bearing groove. Along the radial direction of the motor shaft, the outer circumferential surface of the bearing washer is spaced apart from the groove wall of the bearing groove.

[0005] The powertrain provided in this application accommodates a ball bearing and a bearing washer via a bearing groove on the housing. The ball bearing supports the motor shaft of the drive motor in the powertrain, and the bearing washer abuts against the ball bearing and the bottom of the bearing groove on both sides along the axial direction of the motor shaft. Therefore, during operation, the displacement of the ball bearing caused by the vibration of the motor shaft can be buffered by the bearing washer.

[0006] The powertrain provided in this application also provides protection for the bearing pad by pre-setting a gap between the outer peripheral surface of the bearing pad and the groove wall of the bearing groove, so that the bearing pad can absorb the impact force of the ball bearing by deforming radially along the motor shaft, and avoid interference between the bearing pad and the groove wall of the bearing groove, thereby extending the service life of the powertrain provided in this application.

[0007] In one implementation, the cross-sectional shape of the bearing groove wall is circular, and the groove wall is used to fit the outer circumferential surface of the outer ring of the ball bearing.

[0008] In one implementation, the gap between the outer peripheral surface of the bearing pad and the groove wall of the bearing groove is greater than the increase in the outer diameter of the bearing pad after compression.

[0009] In this implementation, the outer diameter of the bearing gasket increases to its maximum when it is compressed to its minimum length along the motor shaft. Setting the difference between the outer diameter of the bearing gasket and the inner diameter of the bearing groove wall to be greater than the increase in the outer diameter of the bearing gasket after compression ensures that the bearing gasket remains spaced from the bearing groove wall to avoid interference.

[0010] In one implementation, the bearing groove is also used to accommodate an annular transition plate, and the axial bearing washer along the motor shaft is used to abut against the outer ring of the ball bearing via the transition plate.

[0011] In this implementation, the compressed bearing pad undergoes radial displacement. By using an annular adapter plate to abut between the bearing pad and the ball bearing, the ball bearing is prevented from rubbing against the bearing pad, thus protecting the ball bearing.

[0012] In one implementation, the outer diameter of the adapter plate is smaller than the inner diameter of the bearing groove and larger than the outer diameter of the bearing wave pad.

[0013] In this implementation, the outer peripheral surface of the adapter plate is located between the groove wall of the bearing groove and the outer peripheral surface of the bearing washer. The adapter plate, moving with the ball bearing, is prevented from interfering with the groove wall of the bearing groove. This also ensures a consistent contact area between the adapter plate and the compressed bearing washer, allowing the adapter plate to more evenly transfer the cushioning force of the bearing washer to the ball bearing.

[0014] In one implementation, the difference between the outer diameter of the adapter plate and the inner diameter of the bearing groove wall is less than the difference between the outer diameter of the adapter plate and the outer diameter of the bearing pad.

[0015] In this implementation, the outer circumferential surface of the adapter plate along the radial direction of the motor shaft is closer to the groove wall of the bearing groove than the outer circumferential surface of the bearing pad. This results in a relatively large area for the adapter plate, better accommodating the increased outer diameter of the compressed bearing pad. The groove wall of the bearing groove provides better positioning for the adapter plate, preventing significant radial displacement of the adapter plate along the motor shaft and ensuring reliable contact between the adapter plate and the bearing pad.

[0016] In one implementation, the inner diameter of the adapter plate is larger than the outer diameter of the inner ring of the ball bearing.

[0017] In this implementation, the outer ring of the ball bearing is fitted against the wall of the bearing groove, while the inner ring of the ball bearing rotates with the motor shaft. A radially spaced adapter plate along the motor shaft is positioned between the inner ring of the ball bearing and the adapter plate to prevent continuous friction between the inner ring and the adapter plate.

[0018] In one implementation, the adapter plate includes an annular pad, the side of the annular pad facing the ball bearing for abutting against the outer ring of the ball bearing, and the other side of the annular pad facing the bearing wave pad for abutting against the bearing wave pad.

[0019] In this implementation, the adapter plate abuts against the bearing wave pad and the ball bearing via an annular pad.

[0020] In one implementation, the inner diameter of the annular pad is greater than the outer diameter of the inner ring of the ball bearing and less than or equal to the inner diameter of the bearing diaphragm.

[0021] In this implementation, the radial annular pad along the motor shaft is spaced apart from the inner ring of the ball bearing to prevent the inner ring of the ball bearing from continuously rubbing against the annular pad. The inner diameter of the compressed bearing washer increases, and the inner diameter of the bearing washer is always greater than or equal to the inner diameter of the annular pad to ensure the contact area between the annular pad and the bearing washer.

[0022] In one implementation, the outer diameter of the annular pad is larger than the outer diameter of the bearing wave pad.

[0023] In this implementation, the outer diameter of the compressed bearing pad is increased to increase the contact area between the annular pad and the compressed bearing pad.

[0024] In one implementation, the difference between the outer diameter of the annular pad and the outer diameter of the bearing wave pad is greater than the difference between the inner diameter of the annular pad and the inner diameter of the bearing wave pad.

[0025] In this implementation, the outer circumferential surface of the annular pad along the motor shaft is closer to the groove wall of the bearing groove than the outer circumferential surface of the bearing wave pad. This results in a relatively large area for the annular pad, better accommodating the increased outer diameter of the compressed bearing wave pad. The groove wall of the bearing groove provides better positioning for the annular pad, preventing significant radial displacement of the annular pad along the motor shaft and ensuring reliable contact between the annular pad and the bearing wave pad.

[0026] In one implementation, the adapter plate includes an annular baffle that protrudes from the annular pad along the axial direction of the motor shaft toward the bottom of the bearing groove. The outer diameter of the annular baffle is smaller than the inner diameter of the bearing washer, and the inner diameter of the annular baffle is larger than the outer diameter of the inner ring of the ball bearing.

[0027] In this implementation, the adapter plate is embedded in the inner hole of the bearing washer via an annular baffle. The annular baffle can abut against the inner hole of the bearing washer along the radial direction of the motor shaft to limit the relative displacement between the annular baffle and the bearing washer, ensuring reliable contact between the annular baffle and the bearing washer. The annular baffle is also spaced apart from the inner ring of the ball bearing along the radial direction of the motor shaft to prevent the inner ring of the ball bearing from continuously rubbing against the annular baffle.

[0028] In one implementation, the difference between the outer diameter of the annular baffle and the inner diameter of the bearing gasket is less than the difference between the outer diameter of the bearing gasket and the inner diameter of the bearing groove wall.

[0029] In this implementation, the gap between the annular baffle and the inner hole of the bearing gasket is smaller than the gap between the outer circumferential surface of the bearing gasket and the groove wall of the bearing groove. The annular baffle can abut against the inner hole of the bearing gasket along the radial direction of the motor shaft to limit interference between the bearing gasket and the groove wall of the bearing groove, thereby protecting the bearing gasket.

[0030] In one implementation, an annular baffle is arranged axially along the motor shaft between the annular pad and the bottom of the bearing groove. The annular baffle limits the distance the ball bearing can move axially toward the bottom of the bearing groove along the motor shaft.

[0031] In this implementation, the annular baffle is also used to move synchronously with the ball bearing and abut against the bottom of the bearing groove along the axial direction of the motor shaft, thereby limiting the maximum compression of the bearing pad to protect the bearing pad.

[0032] In one implementation, an annular baffle is used to be embedded in the inner hole of the bearing gasket along the axial direction of the motor shaft. The length of the annular baffle along the axial direction of the motor shaft is less than the natural length of the bearing gasket in its uncompressed state and greater than the length of the bearing gasket in its under-compressed state.

[0033] In this implementation, the length of the annular baffle along the motor shaft is less than the natural length of the bearing pad in its uncompressed state, allowing the bearing pad to cushion the ball bearing through axial deformation after compression. The length of the annular baffle along the motor shaft is greater than the length of the bearing pad in its ultimate compression state, preventing the bearing pad from being compressed and losing its elasticity, thus affecting the cushioning effect.

[0034] In one implementation, the outer diameter of the annular baffle gradually decreases along the axial direction of the motor shaft away from the ball bearing.

[0035] In this implementation, the outer circumferential surface of the annular baffle is conical. Because the bearing pad is floatingly installed in the bearing groove along the radial direction of the motor shaft, the bearing pad may be offset relative to the axis of the motor shaft. During the displacement of the annular baffle toward the bottom of the bearing groove, the conical outer circumferential surface of the baffle can abut against the inner circumferential surface of the bearing pad to correct the bearing pad, so that the buffering force of the bearing pad is more evenly transmitted to the ball bearing through the annular baffle.

[0036] In one implementation, the outer circumferential surface of the annular baffle at one end facing the bottom of the bearing groove includes a chamfer.

[0037] In this implementation, because the bearing pad is floatingly installed in the bearing groove along the radial direction of the motor shaft, the bearing pad may be offset relative to the axis of the motor shaft. During the displacement of the annular baffle toward the bottom of the bearing groove, the chamfer can form a guiding effect, preventing the annular baffle from directly abutting against the bearing pad shim along the axial direction of the motor shaft.

[0038] In one implementation, the outer circumferential surface of one of the two adjacent motor shafts along the axial direction is used to fix the inner ring of the ball bearing. The outer diameter of the other motor shaft is larger than that of the first motor shaft, thus forming an annular limiting step. The limiting step is used to abut against the other side of the ball bearing.

[0039] In this implementation, the motor shaft abuts against the ball bearing via an annular limiting step to restrict the relative displacement of the ball bearing. Conversely, the ball bearing transmits the buffering force of the bearing pad to the motor shaft by abutting against the limiting step.

[0040] In one implementation, the outer diameter of the other motor shaft is smaller than the inner diameter of the outer ring of the ball bearing, and greater than or equal to the outer diameter of the inner ring of the ball bearing.

[0041] In this implementation, the other section of the motor shaft is fully engaged with the inner ring of the ball bearing and is radially spaced from the outer ring of the ball bearing along the motor shaft. This allows the motor shaft and ball bearing to better transmit buffering force along the axial direction of the motor shaft and prevents continuous friction between the motor shaft and the outer ring of the ball bearing.

[0042] In one implementation, the bearing groove includes a through hole that extends through the bottom of the bearing groove along the axial direction of the motor shaft, and the motor shaft is used to pass through the through hole along the axial direction of the motor shaft.

[0043] In this implementation, a section of the motor shaft passes through the ball bearing and reliably engages with the inner ring of the ball bearing. The motor shaft also passes through the inner bore of the bearing washer to limit the radial displacement of the bearing washer. A through hole at the bottom of the bearing slot is used to allow passage for a section of the motor shaft.

[0044] In one implementation, the inner diameter of the bearing gasket is larger than the diameter of the through hole.

[0045] In this implementation, the bearing gasket can be completely fitted to the bottom of the bearing groove to improve the stress conditions of the bearing gasket, thereby protecting the bearing gasket.

[0046] In one implementation, the difference between the inner diameter of the bearing gasket and the diameter of the through hole is less than the difference between the outer diameter of the bearing gasket and the inner diameter of the bearing groove wall.

[0047] In this implementation, the gap between the inner hole and the through hole of the bearing wave pad along the radial direction of the motor shaft is smaller than the gap between the outer circumferential surface of the bearing wave pad and the groove wall of the bearing groove. When the compressed bearing wave pad abuts against the groove wall of the bearing groove, it can also ensure that the bearing wave pad and the bottom of the bearing groove are completely in contact, thereby ensuring that the bearing wave pad is always in a state with good stress conditions.

[0048] In one implementation, the powertrain housing includes another bearing groove for accommodating another ball bearing. The inner ring of this second ball bearing is fixedly fitted onto the outer circumferential surface of the motor shaft. The second ball bearing and the first ball bearing are respectively arranged on opposite sides of the rotor core of the drive motor. The second bearing groove includes another through-hole that extends axially through the bottom of the second bearing groove along the bottom of the motor shaft. One through-hole passes through one end of the motor shaft, which is used to drive the reducer of the powertrain. The other through-hole passes through the other end of the motor shaft.

[0049] In this implementation, the powertrain uses two ball bearings arranged at intervals to support the motor shaft. A bearing washer is located at the end of the motor shaft that connects to the reducer, ensuring the motor shaft's axial orientation is relatively fixed and guaranteeing the powertrain's transmission accuracy. The other bearing passes through the bottom of the other bearing slot via a through hole, providing sufficient space for axial displacement of the motor shaft to release stress and extend its service life. The bearing washer also provides a buffering effect at one end of the motor shaft, improving the reliability of the connection between the motor shaft and the reducer.

[0050] Secondly, this application provides an electric vehicle, which includes wheels and a powertrain provided by any of the above implementations, the powertrain being used to drive the wheels.

[0051] The electric vehicle provided in this application has higher reliability and a longer service life. Attached Figure Description

[0052] To more clearly illustrate the technical solution of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0053] Figure 1 This is a schematic diagram of the external structure of an electric vehicle provided in one embodiment of this application;

[0054] Figure 2 This is a schematic diagram of the transmission structure of the powertrain provided in one embodiment of this application;

[0055] Figure 3 This is a schematic cross-sectional view of the powertrain provided in one embodiment of this application;

[0056] Figure 4 This is a cross-sectional structural schematic diagram of the powertrain provided in another embodiment of this application;

[0057] Figure 5 This is a partially enlarged structural schematic diagram of the powertrain provided in one embodiment of this application;

[0058] Figure 6 This is a cross-sectional structural schematic diagram of the powertrain provided in another embodiment of this application;

[0059] Figure 7 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0060] Figure 8 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0061] Figure 9 This is a cross-sectional structural schematic diagram of the powertrain provided in another embodiment of this application;

[0062] Figure 10 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0063] Figure 11 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0064] Figure 12 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0065] Figure 13 This is a partially enlarged structural schematic diagram of the powertrain provided in another embodiment of this application;

[0066] Figure 14 This is a partially enlarged structural diagram of the powertrain provided in another embodiment of this application.

[0067] Reference numerals: 1000 - Electric vehicle; 1001 - Wheel; 1002 - Frame; 1003 - Battery pack; 100 - Powertrain; 10 - Housing; 11 - Bearing groove; 111 - First bearing groove; 112 - Second bearing groove; 113 - Groove wall; 114 - Groove bottom; 115 - Through hole; 20 - Drive motor; 21 - Motor shaft; 211 - First section; 212 - Second section; 2121 - Third end face; 22 - Motor stator 23-Motor rotor; 30-Reducer; 31-Gear set; 32-Input shaft; 33-Output shaft; 40-Ball bearing; 41-First ball bearing; 411-Inner ring; 412-Outer ring; 42-Second ball bearing; 421-Inner ring; 422-Outer ring; 50-Bearing washer; 60-Adapter plate; 61-Annular pad; 611-First end face; 612-Second end face; 62-Annular baffle; 621-Chamfer. Detailed Implementation

[0068] The technical solutions of the embodiments of this application will now be described with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application.

[0069] This application provides a powertrain with bearing gasket protection. The powertrain housing includes a bearing groove for accommodating a ball bearing and an annular bearing gasket. The outer ring of the ball bearing is embedded in the bearing groove, and the inner ring of the ball bearing is fixedly sleeved on the outer circumferential surface of the motor shaft of the drive motor in the powertrain. Along the axial direction of the motor shaft, one side of the bearing gasket abuts against one side of the ball bearing, and the other side of the bearing gasket abuts against the bottom of the bearing groove. Along the radial direction of the motor shaft, the outer circumferential surface of the bearing gasket is spaced apart from the groove wall of the bearing groove.

[0070] In the powertrain provided by this application, the displacement of the ball bearing caused by the vibration of the motor shaft during operation can be buffered by the bearing gasket. The bearing gasket can absorb the impact force of the ball bearing by deforming radially along the motor shaft. By pre-setting a gap between the outer circumferential surface of the bearing gasket and the groove wall of the bearing groove, interference between the bearing gasket and the groove wall of the bearing groove is avoided, thereby protecting the bearing gasket and extending the service life of the powertrain provided by this application.

[0071] This application provides an electric vehicle, which includes wheels and a powertrain provided in this application, the powertrain being used to drive the wheels. The electric vehicle provided in this application has higher reliability and a longer service life.

[0072] Please see Figure 1 , Figure 1 This is a schematic diagram of the external structure of an electric vehicle 1000 provided in one embodiment of this application.

[0073] like Figure 1 As shown, the electric vehicle 1000 provided in this application includes wheels 1001 and a powertrain 100. The powertrain 100 is fixed to the frame 1002 and is drively connected to one or more wheels 1001. The powertrain 100 is used to drive one or more wheels 1001 of the electric vehicle 1000 to rotate, thereby driving the electric vehicle 1000 to travel.

[0074] In one embodiment, the electric vehicle 1000 provided in this application includes a battery pack 1003, which is fixed to a frame 1002 and used to provide electrical energy to other functional components on the electric vehicle 1000. Exemplarily, the battery pack 1003 is electrically connected to a powertrain 100 to provide electrical energy to the powertrain 100. The powertrain 100 receives the electrical energy provided by the battery pack 1003 to drive one or more wheels 1001 to rotate.

[0075] In one embodiment, the electric vehicle 1000 provided in this application includes a powertrain 100 for driving a plurality of wheels 1001 to rotate. In another embodiment, the electric vehicle 1000 provided in this application includes a plurality of powertrains 100, each powertrain 100 being used to drive a portion of the plurality of wheels 1001 to rotate.

[0076] Please see Figure 2 , Figure 2 This is a schematic diagram of the transmission structure of the powertrain 100 provided in one embodiment of this application.

[0077] like Figure 2 As shown, the powertrain 100 provided in this application includes a housing 10 and a drive motor 20. The housing 10 houses the drive motor 20. The drive motor 20 is electrically connected to a battery pack 1003, and its motor shaft 21 is connected to one or more wheels 1001 via a transmission mechanism. The drive motor 20 receives electrical energy from the battery pack 1003 and provides driving force to one or more wheels 1001 via its motor shaft 21.

[0078] In one embodiment, the powertrain 100 provided in this application includes a reducer 30 in its transmission mechanism. A gear set 31 of the reducer 30 is partially housed within a housing 10. The reducer 30 is used to drive the motor shaft 21 of a drive motor 20 and to drive one or more wheels 1001 via a rear-end transmission mechanism. The gear set 31 of the reducer 30 is used to adjust the speed and torque of the driving force output from the motor shaft 21 of the drive motor 20, and to transmit the adjusted driving force to one or more wheels 1001 via the rear-end transmission mechanism.

[0079] In one embodiment, the reducer 30 includes an input shaft 32, a gear set 31, and an output shaft 33. The input shaft 32 and gear set 31 are housed within a housing 10, and the output shaft 33 is partially housed within the housing 10. The input shaft 32 is used to drive the motor shaft 21 and the gear set 31, and the output shaft 33 is used to drive the gear set 31 and the rear drive mechanism wheel 1001. Thus, the reducer 30 can receive the driving force from the motor shaft 21 via the input shaft 32 and transmit it to the gear set 31. The gear set 31 is used to adjust the speed and torque of the driving force transmitted by the input shaft 32 and transmit the adjusted driving force to the output shaft 33. The drive motor 20 outputs driving force to the wheel 1001 via the output shaft 33 of the reducer 30.

[0080] Please refer to the above. Figure 3 , Figure 3 This is a cross-sectional structural diagram of the powertrain 100 provided in one embodiment of this application.

[0081] like Figure 3 As shown, the drive motor 20 includes a motor stator 22 and a motor rotor 23. The housing 10 is used to accommodate the motor stator 22 and the motor rotor 23, and partially accommodates the motor shaft 21. The housing 10 is also used to fix the motor stator 22. Along the radial direction of the motor shaft 21, the motor stator 22 is used to be sleeved on the outer peripheral surface of the motor rotor 23, and the motor rotor 23 is used to coaxially fix the motor shaft 21.

[0082] The powertrain 100 provided in this application also includes a ball bearing 40. The housing 10 includes a bearing groove 11 for accommodating the ball bearing 40. The axis of the ball bearing 40 coincides with the axis of the motor shaft 21. The outer ring of the ball bearing 40 is embedded in the bearing groove 11, and the inner ring of the ball bearing 40 is fixedly sleeved on the outer circumferential surface of the motor shaft 21. That is, the powertrain 100 provided in this application supports the motor shaft 21 and the motor rotor 23 through the ball bearing 40, and allows the motor shaft 21 to rotate with the motor rotor 23 within the housing 10.

[0083] In one embodiment, there are two ball bearings 40, which are arranged axially along the motor shaft 21 on both sides of the rotor core of the motor rotor 23. That is, one ball bearing 40 is located on the side of the rotor core closer to the reducer 30, and the other ball bearing 40 is located on the side of the rotor core away from the reducer 30. The powertrain 100 provided in this application supports the motor shaft 21 through the two ball bearings 40 arranged at intervals.

[0084] That is, along the axial direction of the motor shaft 21, the housing 10 includes two bearing grooves 11. Along the axial direction of the motor shaft 21, the two bearing grooves 11 are arranged opposite to each other, and the opening of one bearing groove 11 faces the other bearing groove 11. Each bearing groove 11 is used to accommodate a ball bearing 40.

[0085] For ease of explanation, the two bearing grooves 11 will be referred to as the first bearing groove 111 and the second bearing groove 112, respectively. Along the axial direction of the motor shaft 21, the first bearing groove 111 is closer to the reducer 30 than the second bearing groove 112. The two ball bearings 40 are defined as the first ball bearing 41 and the second ball bearing 42, respectively. The first ball bearing 41 is accommodated in the first bearing groove 111, and the second ball bearing 42 is accommodated in the second bearing groove 112.

[0086] In one embodiment, the first ball bearing 41 includes an inner ring 411 and an outer ring 412. The outer ring 412 of the first ball bearing 41 is embedded in the first bearing groove 111 and can slide relative to the groove wall 113 of the first bearing groove 111 along the axial direction of the motor shaft 21. The inner ring 411 of the first ball bearing 41 is used to fixally connect to the motor shaft 21. The second ball bearing 42 includes an inner ring 421 and an outer ring 422. The outer ring 422 of the second ball bearing 42 is used to fixally connect to the groove wall 113 of the second bearing groove 112, and the inner ring 421 of the second ball bearing 42 is used to fixally connect to the motor shaft 21. That is, the two opposite ends of the motor shaft 21 along its own axial direction are respectively slidable relative to the housing 10 as floating ends and fixed relative to the housing 10 as fixed ends via the first ball bearing 41 and the second ball bearing 42.

[0087] During the operation of the powertrain 100, the drive motor 20 outputs driving force through the reducer 30. The motor shaft 21 will experience axial stress due to the heat generated by the drive motor 20 or the meshing force of the reducer 30. The powertrain 100 provided in this application fixes the outer ring 422 of the second ball bearing 42 to the groove wall 113 of the second bearing groove 112, and slides the outer ring 412 of the first ball bearing 41 to the groove wall 113 of the first bearing groove 111. This ensures that the two ball bearings 40 support the motor shaft 21, while allowing the motor shaft 21 to slide relative to the housing 10 along the axial direction of the motor shaft 21 through the first ball bearing 41, thereby releasing the axial stress on the motor shaft 21.

[0088] The powertrain 100 provided in this application also includes an annular bearing washer 50, which is accommodated within a first bearing groove 111 and also fitted onto the outer circumferential surface of the motor shaft 21. Along the axial direction of the motor shaft 21, the bearing washer 50 is located on the side of the first ball bearing 41 away from the rotor core. One side of the bearing washer 50 abuts against one side of the first ball bearing 41, and the other side of the bearing washer 50 abuts against the bottom 114 of the first bearing groove 111. During operation, the displacement of the first ball bearing 41 caused by the vibration of the motor shaft 21 can be buffered by the bearing washer 50.

[0089] Specifically, when the motor shaft 21 releases axial stress, the motor shaft 21 will drive the first ball bearing 41 to slide axially relative to the housing 10 along its own axial direction, compressing the bearing washer 50. The bearing washer 50 is used to absorb the axial stress of the motor shaft 21 through elastic deformation. That is, the bearing washer 50 is used to buffer the axial sliding of the motor shaft 21, so as to reduce the impact of the motor shaft 21 on the other structure of the powertrain 100 provided in this application during the release of axial stress, thereby improving the smoothness and reliability of the operation of the drive motor 20.

[0090] Please refer to the above. Figure 4 , Figure 4 This is a cross-sectional structural diagram of the powertrain 100 provided in another embodiment of this application.

[0091] like Figure 4 As shown, the outer ring 412 of the first ball bearing 41 is used to fixally connect to the groove wall 113 of the first bearing groove 111, and the inner ring 411 of the first ball bearing 41 is used to fixally connect to the motor shaft 21. The outer ring 422 of the second ball bearing 42 is used to slidely connect to the groove wall 113 of the second bearing groove 112, and the inner ring 421 of the second ball bearing 42 is used to fixally connect to the motor shaft 21. The bearing washer 50 is used to be accommodated in the second bearing groove 112. Along the axial direction of the motor shaft 21, the bearing washer 50 is located on the side of the second ball bearing 42 away from the reducer 30. One side of the bearing washer 50 is used to abut against one side of the second ball bearing 42, and the other side of the bearing washer 50 is used to abut against the bottom 114 of the second bearing groove 112. That is, the end of the motor shaft 21 close to the reducer 30 along its own axial direction is fixed relative to the housing 10 as a fixed end, and the end of the motor shaft 21 away from the reducer 30 along its own axial direction can slide relative to the housing 10 along its own axial direction as a floating end.

[0092] Therefore, during the operation of the powertrain 100 provided in this application, the motor shaft 21 can also slide relative to the housing 10 through the floating end away from the reducer 30 to achieve the effect of releasing axial stress. In addition, placing the bearing washer 50 in the second bearing groove 112 away from the reducer 30 can also achieve a buffering effect, reducing the impact of the motor shaft 21 on the other structures of the powertrain 100 provided in this application during the release of axial stress.

[0093] It should be noted that designating the end of the motor shaft 21 closest to the reducer 30 along its own axial direction as the fixed end and the end furthest from the reducer 30 along its own axial direction as the floating end can improve the fit accuracy between the motor shaft 21 and the input shaft 32 of the reducer 30, reduce the impact of the axial expansion caused by the heat generated by the drive motor 20 on the axial runout of the input shaft 32 of the reducer 30, and ensure that the motor shaft 21 is reliably connected to the reducer 30. Conversely, designating the end of the motor shaft 21 closest to the reducer 30 along its own axial direction as the floating end and the end furthest from the reducer 30 along its own axial direction as the fixed end is beneficial for the output torque of the drive motor 20 and improves the transmission efficiency.

[0094] For ease of description, the following embodiments of this application are based on the example of the first ball bearing 41 and the bearing washer 50 being accommodated in the first bearing groove 111, and the outer ring 412 of the first ball bearing 41 being slidably connected to the groove wall 113 of the first bearing groove 111.

[0095] In one embodiment, the cross-sectional shape of the groove wall 113 of the bearing groove 11 (first bearing groove 111) is circular, and the groove wall 113 of the bearing groove 11 (first bearing groove 111) is used to fit the outer peripheral surface of the outer ring 412 of the ball bearing 40 (first ball bearing 41). Based on the fact that the outer peripheral surface of the outer ring 412 of the first ball bearing 41 is circular, the cross-sectional shape of the groove wall 113 of the first bearing groove 111 is set to be circular to ensure the fitting effect between the groove wall 113 of the first bearing groove 111 and the outer ring 412 of the first ball bearing 41, thereby ensuring the radial positioning of the outer ring 412 of the first ball bearing 41 relative to the housing 10 of the motor shaft 21.

[0096] Please refer to the above. Figure 5 , Figure 5 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in one embodiment of this application.

[0097] like Figure 5 As shown, along the radial direction of the motor shaft 21, the outer circumferential surface of the bearing washer 50 is spaced apart from the groove wall 113 of the bearing groove 11 (first bearing groove 111). That is, along the radial direction of the motor shaft 21, the outer diameter of the bearing washer 50 is smaller than the inner diameter of the first bearing groove 111.

[0098] Understandably, when the motor shaft 21 drives the first ball bearing 41 to slide axially relative to the housing 10, the bottom 114 of the first ball bearing 41 and the first bearing groove 111 will compress the bearing pad 50. Based on the wavy surface of the bearing pad 50 parallel to the radial direction of the motor shaft 21 and its inherent elasticity, the wavy shape of the compressed bearing pad 50 tends to be flattened. The radial deformation of the bearing pad 50 along the motor shaft 21 after compression will increase the outer diameter of the bearing pad 50. In the prior art, the space provided within the bearing groove is relatively small, which affects the stress release of the bearing pad, thereby shortening the service life of the bearing pad and the powertrain provided in this application. Compared with the prior art, this application provides a gap between the outer peripheral surface of the bearing pad 50 and the groove wall 113 of the first bearing groove 111, so that the bearing pad 50 can absorb the impact force of the first ball bearing 41 by deforming radially along the motor shaft 21, and avoid interference between the bearing pad 50 and the groove wall 113 of the first bearing groove 111, thereby protecting the bearing pad 50 and extending the service life of the powertrain 100 provided by this application.

[0099] In one embodiment, the distance between the outer peripheral surface of the bearing washer 50 and the groove wall 113 of the first bearing groove 111 is greater than the increase in the outer diameter of the bearing washer 50 after compression. That is, along the radial direction of the motor shaft 21, the difference between the outer diameter of the bearing washer 50 in its initial state and the inner diameter of the groove wall 113 of the first bearing groove 111 is greater than the difference between the outer diameter of the bearing washer 50 after compression and the outer diameter of the bearing washer 50 in its initial state. It should be noted that the bearing washer 50 has a certain amount of pre-compression after being installed in the first bearing groove 111, meaning that the bearing washer 50 abuts against the first ball bearing 41 and the bottom 114 of the first bearing groove 111 at opposite ends along the axial direction of the motor shaft 21, respectively. The initial state of the bearing washer 50 refers to the state of the bearing washer 50 when the distance between the first ball bearing 41 and the bottom 114 of the first bearing groove 111 is at its maximum along the axial direction of the motor shaft 21. The state of the compressed bearing pad 50 mentioned later in this application refers to the state of the bearing pad 50 when the distance between the first ball bearing 41 and the bottom 114 of the first bearing groove 111 is less than the maximum distance between them along the axial direction of the motor shaft 21.

[0100] Understandably, when the bearing washer 50 is compressed to its minimum length along the axial direction of the motor shaft 21, the outer diameter of the bearing washer 50 increases to its maximum. This application sets the difference between the outer diameter of the bearing washer 50 in its initial state and the inner diameter of the groove wall 113 of the first bearing groove 111 to be greater than the difference between the outer diameter of the bearing washer 50 after compression and the outer diameter of the bearing washer 50 in its initial state. This ensures that the bearing washer 50 is always spaced apart from the groove wall 113 of the first bearing groove 111, avoiding interference between the bearing washer 50 and the groove wall 113 of the first bearing groove 111, thereby providing better protection for the bearing washer 50.

[0101] In one embodiment, the bearing groove 11 is also used to accommodate an annular transition plate 60 along the axial direction of the motor shaft 21, and the bearing washer 50 is used to abut against the outer ring 412 of the ball bearing 40 via the transition plate 60.

[0102] Please refer to the above. Figure 6 and Figure 7 ,in Figure 6 This is a cross-sectional structural schematic diagram of the powertrain 100 provided in another embodiment of this application; Figure 7 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application.

[0103] like Figure 6 and Figure 7 As shown, the annular adapter plate 60 is accommodated within the first bearing groove 111 and fitted onto the outer circumferential surface of the motor shaft 21. Along the axial direction of the motor shaft 21, the bearing washer 50 abuts against the outer ring 412 of the first ball bearing 41 via the adapter plate 60. Specifically, along the axial direction of the motor shaft 21, the adapter plate 60 and the bearing washer 50 are arranged between the first ball bearing 41 and the bottom 114 of the first bearing groove 111, with the adapter plate 60 being closer to the first ball bearing 41 relative to the bearing washer 50. The adapter plate 60 can slide relative to the groove wall 113 of the first bearing groove 111.

[0104] When the motor shaft 21 releases axial stress, causing the first ball bearing 41 to slide axially relative to the housing 10, the first ball bearing 41 pushes the adapter plate 60 to slide axially relative to the groove wall 113 of the first bearing groove 111 and squeezes the bearing washer 50. Alternatively, it can be described that when the motor shaft 21 releases axial stress, along the axial direction of the motor shaft 21, the opposite sides of the adapter plate 60 abut against the bearing washer 50 and the outer ring 412 of the first ball bearing 41, respectively.

[0105] Understandably, the bearing washer 50 will undergo radial displacement relative to the first ball bearing 41 after being compressed. The powertrain 100 provided in this application abuts against the bearing washer 50 and the first ball bearing 41 via an annular adapter plate 60, which prevents the first ball bearing 41 and the bearing washer 50 from rubbing against each other, thereby protecting both the first ball bearing 41 and the bearing washer 50. Furthermore, since the inner ring 411 of the first ball bearing 41 is fixedly connected to the motor shaft 21, and the inner ring 411 of the first ball bearing 41 is rotatably connected to the outer ring 412 of the first ball bearing 41... This application, by setting the adapter plate 60 to abut against the outer ring 412 of the first ball bearing 41 along the axial direction of the motor shaft 21, can avoid interference friction between the inner ring 411 of the first ball bearing 41 and the adapter plate 60 and the bearing washer 50 when the motor shaft 21 rotates relative to the groove wall 113 of the first bearing groove 111. This ensures smooth transmission of the motor shaft 21 and can also extend the service life of the first ball bearing 41, the adapter plate 60 and the bearing washer 50.

[0106] Please refer to the above. Figure 8 , Figure 8 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application.

[0107] like Figure 8 As shown, the outer diameter of the adapter plate 60 is smaller than the inner diameter of the first bearing groove 111 and larger than the outer diameter of the bearing washer 50. For ease of explanation, this application will subsequently define the outer diameter of the bearing washer 50 as R1, the outer diameter of the adapter plate 60 as R2, and the inner diameter of the groove wall 113 of the first bearing groove 111 as R3, where R1 < R2 < R3. That is, along the radial direction of the motor shaft 21, the outer circumferential surface of the adapter plate 60 is located between the groove wall 113 of the first bearing groove 111 and the outer circumferential surface of the bearing washer 50.

[0108] Understandably, by limiting the outer diameter R2 of the adapter plate 60 to be between the inner diameter R3 of the first bearing groove 111 and the outer diameter R1 of the bearing washer 50, it is possible to ensure that, when the axial stress of the motor shaft 21 is released, the adapter plate 60, which moves with the first ball bearing 41, does not interfere with the groove wall 113 of the first bearing groove 111. On the other hand, it also ensures the contact area between the adapter plate 60 and the compressed bearing washer 50, allowing the adapter plate 60 to more evenly transmit the buffering force of the bearing washer 50 to the first ball bearing 41.

[0109] In one embodiment, the difference between the outer diameter R2 of the adapter plate 60 and the inner diameter R3 of the groove wall 113 of the first bearing groove 111 is less than the difference between the outer diameter R2 of the adapter plate 60 and the outer diameter R1 of the bearing wave pad 50, i.e., (R3-R2) < (R2-R1). That is, along the radial direction of the motor shaft 21, the outer peripheral surface of the adapter plate 60 is closer to the groove wall 113 of the first bearing groove 111 than the outer peripheral surface of the bearing wave pad 50.

[0110] Understandably, since the outer peripheral surface of the axial adapter plate 60 along the motor shaft 21 is located between the outer peripheral surface of the bearing pad 50 and the groove wall 113 of the first bearing groove 111, setting the outer peripheral surface of the adapter plate 60 closer to the groove wall 113 of the first bearing groove 111 allows the surface area of ​​the adapter plate 60 parallel to the radial direction of the motor shaft 21 to be relatively large, so as to better fit the bearing pad 50 whose outer diameter has increased after compression, thereby ensuring the contact area between the bearing pad 50 and the adapter plate 60. On the other hand, when the axial stress of the motor shaft 21 is released, the groove wall 113 of the first bearing groove 111 can provide a better limiting effect on the adapter plate 60, preventing the adapter plate 60 from shifting significantly along the radial direction of the motor shaft 21, and ensuring reliable contact between the adapter plate 60 and the bearing pad 50.

[0111] In one embodiment, the inner diameter of the adapter plate 60 is larger than the outer diameter of the inner ring 411 of the first ball bearing 41. For ease of explanation, the inner diameter of the adapter plate 60 will be defined as R4, and the outer diameter of the inner ring 411 of the first ball bearing 41 will be defined as R5, where R4 > R5. That is, along the radial direction of the motor shaft 21, the inner circumferential surface of the adapter plate 60 is spaced apart from the outer circumferential surface of the inner ring 411 of the first ball bearing 41. When the axial stress of the motor shaft 21 is released, along the axial direction of the motor shaft 21, the side of the adapter plate 60 closest to the first ball bearing 41 abuts against the outer ring 412 of the first ball bearing 41.

[0112] Understandably, since the outer ring 412 of the first ball bearing 41 is attached to the groove wall 113 of the first bearing groove 111, and the inner ring 411 of the first ball bearing 41 rotates with the motor shaft 21, this application provides a transition plate 60 along the radial direction of the motor shaft 21, which is spaced apart from the inner ring 411 of the first ball bearing 41. This can prevent the inner ring 411 of the first ball bearing 41 from continuously rubbing against the transition plate 60 when rotating with the motor shaft 21, thereby protecting the first ball bearing 41 and the transition plate 60.

[0113] Please refer to the above. Figure 9 and Figure 10 ,in Figure 9 This is a cross-sectional structural schematic diagram of the powertrain 100 provided in another embodiment of this application; Figure 10 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application.

[0114] like Figure 9 and Figure 10 As shown, the adapter plate 60 includes an annular pad 61. Along the axial direction of the motor shaft 21, the side of the annular pad 61 facing the first ball bearing 41 abuts against the outer ring 412 of the first ball bearing 41, and the other side of the annular pad 61 facing the bearing washer 50 abuts against the bearing washer 50. That is, the adapter plate 60 of this application abuts against the bearing washer 50 and the first ball bearing 41 through the annular pad 61.

[0115] In this embodiment, the annular pad 61 includes two end faces along the axial direction of the motor shaft 21. For ease of explanation, the two end faces of the annular pad 61 are defined as a first end face 611 and a second end face 612. Exemplarily, along the axial direction of the motor shaft 21, the first end face 611 faces the bottom 114 of the first bearing groove 111, and the second end face 612 faces the outer ring 412 of the first ball bearing 41. That is, when the motor shaft 21 releases axial stress, along the axial direction of the motor shaft 21, the second end face 612 of the annular pad 61 is used to abut against the outer ring 412 of the first ball bearing 41, so that the annular pad 61 can transmit the axial displacement generated when the axial stress of the motor shaft 21 is released from the first ball bearing 41 to the bearing washer 50.

[0116] Since the inner ring 411 of the first ball bearing 41 is fixedly connected to the motor shaft 21, and the inner ring 411 of the first ball bearing 41 is rotatably connected to the outer ring 412 of the first ball bearing 41, it is understandable that the second end face 612 of the annular pad 61 faces the outer ring 412 of the first ball bearing 41, which can prevent interference friction when the inner ring 411 of the first ball bearing 41 rotates relative to the second end face 612.

[0117] In one embodiment, the adapter plate 60 includes an annular baffle 62 that protrudes from the annular pad 61 along the axial direction of the motor shaft 21 toward the bottom 114 of the first bearing groove 111. That is, along the axial direction of the motor shaft 21, the annular baffle 62 is located between the annular pad 61 and the bottom 114 of the first bearing groove 111. The annular baffle 62 is used to limit the relative displacement between the annular pad 61 and the bearing washer 50.

[0118] Please refer to the above. Figure 11 , Figure 11 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application. For example... Figure 11As shown, the outer diameter of the annular baffle 62 is smaller than the inner diameter of the bearing washer 50, and the inner diameter of the annular baffle 62 is larger than the outer diameter R5 of the inner ring 411 of the first ball bearing 41. For ease of explanation, this application will subsequently define the inner diameter of the bearing washer 50 as R6, the outer diameter of the annular baffle 62 as R7, and the inner diameter of the annular baffle 62 as R8, where R7 < R6 and R8 > R5. That is, along the radial direction of the motor shaft 21, the annular baffle 62 is located between the outer circumferential surface of the inner ring 411 of the first ball bearing 41 and the bearing washer 50.

[0119] Understandably, the adapter plate 60 of this application is embedded in the inner hole of the bearing pad 50 via an annular baffle 62. When the axial stress of the motor shaft 21 is released, the annular baffle 62 can abut against the inner hole of the bearing pad 50 along the radial direction of the motor shaft 21. Because the bearing pad 50 is floatingly installed in the first bearing groove 111 along the radial direction of the motor shaft 21, the bearing pad 50 may be offset relative to the axis of the motor shaft 21. By setting the annular baffle 62 embedded in the inner hole of the bearing pad 50, this application can, on the one hand, isolate the bearing pad 50 from the motor shaft 21 along the radial direction of the motor shaft 21, avoiding interference friction between the bearing pad 50 and the motor shaft 21. On the other hand, the annular baffle 62 can be used to limit the displacement of the annular pad 61 and the bearing pad 50 along the radial direction of the motor shaft 21, to ensure the contact area between the annular pad 61 and the bearing pad 50, thereby ensuring reliable contact between the annular pad 61 and the bearing pad 50. In addition, the inner diameter R8 of the annular baffle 62 is set to be larger than the outer diameter R5 of the inner ring 411 of the first ball bearing 41. The annular baffle 62 is spaced apart from the inner ring 411 of the first ball bearing 41 along the radial direction of the motor shaft 21, which can prevent the inner ring 411 of the first ball bearing 41 from continuously rubbing against the annular baffle 62 when it rotates with the motor shaft 21, so as to protect the first ball bearing 41 and the annular baffle 62.

[0120] In another description, along the axial direction of the motor shaft 21, the annular pad 61 includes an annular protrusion on the side facing the bottom 114 of the first bearing groove 111. Along the radial direction of the motor shaft 21, the annular protrusion is located between the outer circumferential surface of the inner ring 411 of the first ball bearing 41 and the inner circumferential surface of the bearing washer 50. The annular protrusion limits the radial offset of the bearing washer 50 relative to the motor shaft 21, thereby limiting the relative displacement between the annular pad 61 and the bearing washer 50 and ensuring reliable contact between them. The annular protrusion also serves to radially isolate the bearing washer 50 and the inner ring 411 of the first ball bearing 41 along the motor shaft 21 to avoid interference friction between the bearing washer 50 and the motor shaft 21 and the inner ring 411 of the first ball bearing 41.

[0121] Please refer to the above. Figure 12 , Figure 12This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application. For example... Figure 12 As shown, the inner diameter of the annular pad 61 is larger than the outer diameter R5 of the inner ring 411 of the first ball bearing 41 and smaller than or equal to the inner diameter R6 of the bearing wave pad 50. For ease of explanation, the inner diameter of the annular pad 61 is defined as R9, where R5 < R9 ≤ R6. That is, along the radial direction of the motor shaft 21, the inner circumferential surface of the annular pad 61 is located on the side of the outer circumferential surface of the inner ring 411 of the first ball bearing 41 away from the motor shaft 21, and is located on the side of the inner circumferential surface of the bearing wave pad 50 close to the motor shaft 21. In other words, along the radial direction of the motor shaft 21, the annular pad 61 is spaced apart from the inner ring 411 of the first ball bearing 41, and the inner circumferential surface of the annular pad 61 is spaced apart from the inner circumferential surface of the bearing wave pad 50. It can be understood that by limiting the size of the inner diameter of the annular pad 61 and the outer diameter of the inner ring 411 of the first ball bearing 41, the continuous friction between the inner ring 411 of the first ball bearing 41 and the annular pad 61 when rotating with the motor shaft 21 can be avoided. Furthermore, since the inner diameter of the bearing wave pad 50 increases after compression, by limiting the size of the inner diameter of the annular pad 61 and the inner diameter of the bearing wave pad 50, the inner diameter R6 of the bearing wave pad 50 is always greater than or equal to the inner diameter R9 of the annular pad 61, so as to ensure the contact area between the annular pad 61 and the bearing wave pad 50.

[0122] In one embodiment, the outer diameter of the annular pad 61 is larger than the outer diameter R1 of the bearing wave pad 50. For ease of explanation, the outer diameter of the annular pad 61 is defined as R10, where R10 > R1. That is, along the radial direction of the motor shaft 21, the outer circumferential surface of the annular pad 61 is located on the side of the outer circumferential surface of the bearing wave pad 50 away from the motor shaft 21. It can be understood that the outer diameter of the bearing wave pad 50 increases after compression. By setting the outer diameter R10 of the annular pad 61 to be larger than the outer diameter R1 of the bearing wave pad 50, this application can increase the contact area between the annular pad 61 and the compressed bearing wave pad 50.

[0123] In one embodiment, the difference between the outer diameter R10 of the annular pad 61 and the outer diameter R1 of the bearing wave pad 50 is greater than the difference between the inner diameter R9 of the annular pad 61 and the inner diameter R6 of the bearing wave pad 50. That is, (R10-R1)>(R6-R9). Alternatively, it can be described that, along the radial direction of the motor shaft 21, the outer circumferential surface of the annular pad 61 is closer to the groove wall 113 of the first bearing groove 111 than the outer circumferential surface of the bearing wave pad 50.

[0124] Understandably, given that the outer circumferential surface of the annular pad 61 along the radial direction of the motor shaft 21 is located between the outer circumferential surface of the bearing wave pad 50 and the groove wall 113 of the first bearing groove 111, setting the outer circumferential surface of the annular pad 61 closer to the groove wall 113 of the first bearing groove allows for a relatively larger surface area of ​​the annular pad 61 parallel to the radial direction of the motor shaft 21, better accommodating the bearing wave pad 50 whose outer diameter has increased after compression. Furthermore, the groove wall 113 of the first bearing groove 111 provides better positioning for the annular pad 61, preventing significant radial displacement of the annular pad 61 along the motor shaft 21 and ensuring reliable contact between the annular pad 61 and the bearing wave pad 50.

[0125] In one embodiment, the difference between the outer diameter R7 of the annular baffle 62 and the inner diameter R6 of the bearing pad 50 is less than the difference between the outer diameter R1 of the bearing pad 50 and the inner diameter R3 of the groove wall 113 of the first bearing groove 111. That is, (R6-R7) < (R3-R1). Alternatively, it can be described that, along the radial direction of the motor shaft 21, the gap between the outer circumferential surface of the annular baffle 62 and the inner circumferential surface of the bearing pad 50 is less than the gap between the outer circumferential surface of the bearing pad 50 and the groove wall 113 of the first bearing groove 111. This ensures that when the axial stress of the motor shaft 21 is released, the annular baffle 62 can abut against the inner hole of the bearing pad 50 along the radial direction of the motor shaft 21, thereby limiting the offset of the bearing pad 50 along the motor shaft 21. On the one hand, this ensures the contact area between the bearing pad 50 and the annular baffle 61, and on the other hand, it prevents interference between the bearing pad 50 and the groove wall 113 of the first bearing groove 111, thus protecting the bearing pad 50.

[0126] In one embodiment, an annular baffle 62 is arranged axially along the motor shaft 21 between the annular pad 61 and the bottom 114 of the first bearing groove 111. The annular baffle 62 limits the distance the first ball bearing 41 can move axially along the motor shaft 21 toward the bottom 114 of the first bearing groove 111. It is understood that when the motor shaft 21 releases axial stress, the motor shaft 21 will cause the first ball bearing 41 to slide relative to the housing 10 axially toward the bottom 114 of the first bearing groove 111, and drive the annular pad 61 to press against the bearing washer 50. This application provides an annular baffle 62 along the axial direction of the motor shaft 21 between the first ball bearing 41 and the bottom 114 of the first bearing groove 111. The annular baffle 62 can abut against the bottom 114 of the first bearing groove 111 after the first ball bearing 41 slides to a certain distance, thereby limiting the first ball bearing 41 from continuing to slide. This limits the maximum compression of the bearing washer 50 and prevents the bearing washer 50 from being broken due to excessive pressure, thus affecting the service life of the powertrain 100 provided by this application.

[0127] In one embodiment, an annular baffle 62 is used to be embedded in the inner hole of the bearing pad 50 along the axial direction of the motor shaft 21. The length of the annular baffle 62 along the axial direction of the motor shaft 21 is less than the natural length of the bearing pad 50 in its uncompressed state but greater than the length of the bearing pad 50 in its fully compressed state. It is understood that by embedding the annular baffle 62 into the inner hole of the bearing pad 50, on the one hand, the annular baffle 62 can radially isolate the bearing pad 50 from the motor shaft 21, preventing interference friction between the bearing pad 50 and the motor shaft 21. On the other hand, the annular baffle 62 can limit the radial displacement of the annular pad 61 and the bearing pad 50 along the motor shaft 21, ensuring the contact area between the annular pad 61 and the bearing pad 50, thereby ensuring reliable contact between the annular pad 61 and the bearing pad 50.

[0128] Furthermore, since both the annular baffle 62 and the bearing washer 50 are located along the axial direction of the motor shaft 21 between the bottom 114 of the first ball bearing 41 and the first bearing groove 111, this application limits the length of the annular baffle 62 along the axial direction of the motor shaft 21 to be less than the natural length of the bearing washer 50 in its uncompressed state. This allows the bearing washer 50 to be compressed to cushion the ball bearing 40 through axial deformation. Limiting the length of the annular baffle 62 along the axial direction of the motor shaft 21 to be greater than the length of the bearing washer 50 in its ultimate compression state can prevent the bearing washer 50 from being compressed and losing its elasticity, thus affecting the cushioning effect.

[0129] Please refer to the above. Figure 13 , Figure 13 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application.

[0130] like Figure 13 As shown, the outer diameter R7 of the annular baffle 62 gradually decreases along the axial direction of the motor shaft 21 towards the direction away from the first ball bearing 41. That is, the outer circumferential surface of the annular baffle 62 is conical, and along the axial direction of the motor shaft 21, the end of the annular baffle 62 with a smaller outer diameter is relatively far away from the first ball bearing 41. Because the bearing pad 50 is floatingly installed in the first bearing groove 111 along the radial direction of the motor shaft 21, the bearing pad 50 may be offset relative to the axis of the motor shaft 21. During the displacement of the annular baffle 62 towards the bottom 114 of the first bearing groove 111, the bearing pad 50 can be aligned by its own conical outer circumferential surface abutting against the inner circumferential surface of the bearing pad 50, so that the buffering force of the bearing pad 50 is more evenly transmitted to the ball bearing 40 through the annular baffle 61.

[0131] In one embodiment, the bearing shim 50 includes a plurality of annular shims arranged axially along the motor shaft 21.

[0132] In one embodiment, the outer peripheral surface of the annular baffle 62 facing the bottom 114 of the first bearing groove 111 includes a chamfer 621. Because the bearing pad 50 is radially mounted within the first bearing groove 111 along the motor shaft 21, the bearing pad 50 may offset relative to the axis of the motor shaft 21. During the displacement of the annular baffle 62 towards the bottom 114 of the first bearing groove 111, the chamfer 62 on its outer peripheral surface provides a guiding effect, preventing the annular baffle 62 from directly abutting against the pad of the bearing pad 50 along the axial direction of the motor shaft 21.

[0133] In one embodiment, the outer circumferential surface of one of the two adjacent motor shafts 21 arranged axially is used to fix the inner ring 411 of the first ball bearing 41. The outer diameter of the other motor shaft 21 is larger than the outer diameter of the first motor shaft 21, thus forming an annular limiting step. The limiting step is used to abut against the other side of the first ball bearing 41.

[0134] Please refer to the above. Figure 14 , Figure 14 This is a partially enlarged structural schematic diagram of the powertrain 100 provided in another embodiment of this application. For example... Figure 14 As shown, for ease of explanation, one segment of the two motor shafts 21 is defined as segment 211, and the other segment is defined as segment 212. Along the axial direction of the motor shafts 21, segment 211 is closer to the bottom 114 of the first bearing groove 111 than segment 212. Segment 211 is used to accommodate the inner ring 411 of the first ball bearing 41, and segment 212 is used to accommodate the motor rotor 23. Along the radial direction of the motor shafts 21, the outer diameter of segment 212 is larger than the outer diameter of segment 211.

[0135] The second segment 212 includes a third end face 2121, which is positioned along the axial direction of the motor shaft 21 towards the bottom 114 of the first bearing groove 111. The third end face 2121 of the first segment 211 abuts against the first ball bearing 41 to limit the relative displacement of the first ball bearing 41 along the axial direction of the motor shaft 21. That is, an annular limiting step is formed between the first segment 211 and the second segment 212, which abuts against the first ball bearing 41 to limit the relative displacement of the first ball bearing 41 along the axial direction of the motor shaft 21. Conversely, the first ball bearing 41 transmits the buffering force of the bearing pad 50 to the motor shaft 21 by abutting against the limiting step, thereby achieving a vibration damping effect on the motor shaft 21.

[0136] In one embodiment, the outer diameter of the other segment of the motor shaft 21 is smaller than the inner diameter of the outer ring 412 of the ball bearing 40, but greater than or equal to the outer diameter of the inner ring 411 of the ball bearing 40. That is, along the radial direction of the motor shaft 21, the outer diameter of the second segment 212 is smaller than the inner diameter of the outer ring 412 of the first ball bearing 41, but greater than or equal to the outer diameter of the inner ring 411 of the first ball bearing 41. Alternatively, it can be described that, along the radial direction of the motor shaft 21, the outer circumferential surface of the second segment 212 is located between the outer circumferential surface of the inner ring 411 of the first ball bearing 41 and the inner circumferential surface of the outer ring 412, or the outer circumferential surface of the second segment 212 is aligned with the outer circumferential surface of the inner ring 411 of the first ball bearing 41. The third end face 2121 can completely fit against the inner ring 411 of the first ball bearing 41 and is spaced apart from the outer ring 412 of the first ball bearing 41 along the radial direction of the motor shaft 21. Therefore, the motor shaft 21 and the first ball bearing 41 can better transmit the buffer force along the axial direction of the motor shaft 21, and avoid the second section 212 continuously rubbing against the outer ring 412 of the first ball bearing 41 when the motor shaft 21 rotates, thereby extending the service life of the first ball bearing 41.

[0137] In one embodiment, the first bearing groove 111 includes a through hole 115, which extends through the bottom 114 of the first bearing groove 111 along the axial direction of the motor shaft 21. The through hole 115 is used to avoid the first section 211 of the motor shaft 21. That is, the motor shaft 21 is used to drive through the through hole 115 and connect to the input shaft 32 of the reducer 30. Specifically, the first section 211 passes through the first ball bearing 41 and reliably fits against the inner ring 411 of the first ball bearing 41. The first section 211 passes through the inner hole of the bearing washer 50 to limit the radial displacement of the bearing washer 50, and also passes through the through hole 115 in the bottom 114 of the first bearing groove 111 to drive through the input shaft 32 of the reducer 30.

[0138] In one embodiment, the inner diameter of the bearing washer 50 is larger than the diameter of the through hole 115. This allows the bearing washer 50 to fully conform to the bottom 114 of the first bearing groove 111, improving the stress conditions of the bearing washer 50 and thus protecting it.

[0139] In one embodiment, the difference between the inner diameter of the bearing washer 50 and the diameter of the through hole 115 is less than the difference between the outer diameter of the bearing washer 50 and the inner diameter of the groove wall 113 of the first bearing groove 111. That is, along the radial direction of the motor shaft 21, the gap between the inner circumferential surface of the bearing washer 50 and the inner circumferential surface of the through hole 115 is less than the gap between the outer circumferential surface of the bearing washer 50 and the inner circumferential surface of the groove wall 113 of the first bearing groove 111. Therefore, even when the compressed bearing washer 50 abuts against the groove wall 113 of the first bearing groove 111, it can be ensured that the bearing washer 50 is completely in contact with the bottom 114 of the first bearing groove 111, thereby ensuring that the bearing washer 50 is always in a state with good stress conditions.

[0140] In one embodiment, the second bearing groove 112 includes another through hole 115, which extends through the bottom 114 of the second bearing groove 112 along the axial direction of the motor shaft 21. One through hole 115 of the first bearing groove 111 is used to pass through one end of the motor shaft 21, which is used to drive the reducer 30 of the powertrain 100. The other through hole 115 of the second bearing groove 112 is used to pass through the other end of the motor shaft 21. That is, the opposite ends of the motor shaft 21 pass through the through holes 115 of the first bearing groove 111 and the second bearing groove 112, respectively, to connect to corresponding transmission mechanisms.

[0141] Obviously, those skilled in the art can make various modifications and variations to this application without departing from the scope of protection of this application. Therefore, if such modifications and variations fall within the scope of the claims of this application and their equivalents, this application also intends to include such modifications and variations.

Claims

1. A powertrain with bearing diaphragm protection function, characterized in that, The powertrain housing includes a bearing groove for accommodating a ball bearing and an annular bearing washer. The outer ring of the ball bearing is embedded in the bearing groove, and the inner ring of the ball bearing is fixedly sleeved on the outer circumferential surface of the motor shaft of the drive motor in the powertrain. Along the axial direction of the motor shaft, one side of a bearing washer is used to abut against one side of a ball bearing, and the other side of the bearing washer is used to abut against the bottom of the bearing groove. The outer peripheral surface of one bearing pad is spaced apart from the groove wall of one bearing groove along the radial direction of the motor shaft.

2. The powertrain according to claim 1, characterized in that, The distance between the outer peripheral surface of the bearing pad and the groove wall of the bearing groove is greater than the increase in the outer diameter of the bearing pad after compression.

3. The powertrain according to claim 1, characterized in that, The bearing groove is also used to accommodate an annular transition plate, and the bearing washer along the axial direction of the motor shaft is used to abut against the outer ring of the ball bearing via the transition plate, wherein: The outer diameter of the adapter plate is smaller than the inner diameter of the bearing groove and larger than the outer diameter of the bearing wave pad. The inner diameter of the adapter plate is larger than the outer diameter of the inner ring of the ball bearing.

4. The powertrain according to claim 3, characterized in that, The difference between the outer diameter of the adapter plate and the inner diameter of the bearing groove wall is less than the difference between the outer diameter of the adapter plate and the outer diameter of the bearing pad.

5. The powertrain according to claim 3, characterized in that, The adapter plate includes an annular washer, the side of the annular washer facing the ball bearing is used to abut against the outer ring of the ball bearing, and the other side of the annular washer facing the bearing washer is used to abut against the bearing washer, wherein: The inner diameter of the annular pad is greater than the outer diameter of the inner ring of the ball bearing and less than or equal to the inner diameter of the bearing diaphragm; the outer diameter of the annular pad is greater than the outer diameter of the bearing diaphragm. The difference between the outer diameter of the annular pad and the outer diameter of the bearing wave pad is greater than the difference between the inner diameter of the annular pad and the inner diameter of the bearing wave pad.

6. The powertrain according to claim 5, characterized in that, The adapter plate includes an annular baffle that protrudes from the annular pad along the axial direction of the motor shaft toward the bottom of the bearing groove, wherein: The outer diameter of the annular baffle is smaller than the inner diameter of the bearing washer, and the inner diameter of the annular baffle is larger than the outer diameter of the inner ring of the ball bearing.

7. The powertrain according to claim 6, characterized in that, The difference between the outer diameter of the annular baffle and the inner diameter of the bearing pad is less than the difference between the outer diameter of the bearing pad and the inner diameter of the bearing groove wall.

8. The powertrain according to claim 6, characterized in that, The annular baffle is arranged axially along the motor shaft between the annular pad and the bottom of the bearing groove, wherein: The annular baffle is used to limit the distance that the ball bearing can move along the axial direction of the motor shaft toward the bottom of the bearing groove.

9. The powertrain according to claim 6, characterized in that, The annular baffle is used to be embedded in the inner hole of the bearing washer along the axial direction of the motor shaft, wherein: Along the axial direction of the motor shaft, the length of the annular baffle is less than the natural length of the bearing pad in the uncompressed state, but greater than the length of the bearing pad in the ultimate compression state.

10. The powertrain according to claim 6, characterized in that, The outer diameter of the annular baffle gradually decreases along the axial direction of the motor shaft away from the ball bearing; or, the outer circumferential surface of the annular baffle at one end facing the bottom of the bearing groove includes a chamfer.

11. The powertrain according to any one of claims 1-10, characterized in that, The outer circumferential surface of one of the two adjacent motor shafts along the axial direction is used to fix the inner ring of the ball bearing. The outer diameter of the other motor shaft is larger than the outer diameter of the first motor shaft, thus forming an annular limiting step. The limiting step is used to abut against the other side of the ball bearing.

12. The powertrain according to claim 11, characterized in that, The outer diameter of the other motor shaft is smaller than the inner diameter of the outer ring of the ball bearing, but greater than or equal to the outer diameter of the inner ring of the ball bearing.

13. The powertrain according to any one of claims 1-10, characterized in that, The bearing groove includes a through hole that extends through the bottom of the bearing groove along the axial direction of the motor shaft. The motor shaft passes through the through hole along the axial direction of the motor shaft. The inner diameter of the bearing washer is larger than the diameter of the through hole. The difference between the inner diameter of the bearing washer and the diameter of the through hole is smaller than the difference between the outer diameter of the bearing washer and the inner diameter of the groove wall of the bearing groove.

14. The powertrain according to claim 13, characterized in that, The powertrain housing includes another bearing groove for accommodating another ball bearing. The inner ring of this other ball bearing is fixedly fitted onto the outer circumferential surface of the motor shaft. This other ball bearing and the first ball bearing are respectively arranged on both sides of the rotor core of the drive motor. The other bearing groove includes another through hole that extends axially through the bottom of the other bearing groove along the motor shaft. The through hole is used to pass through one end of the motor shaft, and the one end of the motor shaft is used to drive the reducer of the powertrain; The other through hole is used to pass through the other end of the motor shaft.

15. An electric vehicle, characterized in that, The electric vehicle includes wheels and a powertrain as described in any one of claims 1-14, the powertrain being used to drive the wheels.

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