Power assembly and electric vehicle
By setting abutting columns in the bearing groove of the powertrain and setting grooves on the side of the bearing outer ring, the problem of the bearing outer ring running ring is solved, and the performance improvement of the powertrain and the manufacturing cost reduction are achieved.
Patent Information
- Application Number
- CN202421836659.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-07-30
- Publication Date
- 2025-06-20
- Estimated Expiration
- 2034-07-30
AI Technical Summary
In existing powertrains, the outer ring of the bearing is prone to run the ring, resulting in a short bearing life, affecting the performance of the powertrain, and the measures to prevent the running ring cannot be normalized, which increases manufacturing costs.
A powertrain is designed in which a groove at the bottom of the bearing groove is provided with a groove to accommodate the abutment column. The outer ring side of the bearing is also provided with a groove. When the outer ring of the bearing runs, the abutment column can enter the groove of the outer ring of the bearing to prevent the running ring.
Through this structure, the outer ring of the powertrain cannot rotate in the circumference of the powertrain, effectively preventing the running ring. Regardless of the load condition, the running ring phenomenon of the outer ring of the bearing can be avoided, reducing the manufacturing cost of the powertrain.
Smart Images
Figure CN223004391U_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the technical field of powertrains, and more specifically, to a powertrain and an electric vehicle. Background Art
[0002] The powertrain is the power source of an electric vehicle. The powertrain includes a motor and a speed reducer. The motor shaft of the motor is drivingly connected to the input shaft of the speed reducer to achieve the power output of the powertrain. To ensure the stable operation of the powertrain, bearings are usually provided on each shaft of the powertrain. However, when the interference amount between the bearing and the bearing cavity is insufficient, the frictional force between the outer ring of the bearing and the bearing cavity is insufficient, resulting in the outer ring of the bearing running in circles, shortening the service life of the bearing, affecting the performance of the powertrain, and further making the performance of the electric vehicle poor.
[0003] In the existing solutions, different measures to prevent the outer ring of the bearing from running in circles need to be adopted according to the load conditions under which the bearing works. For all scenarios in which the bearing works, the measures to prevent the outer ring of the bearing from running in circles cannot be designed in a normalized manner. Furthermore, the manufacturing cost of the powertrain is relatively high. Summary of the Utility Model
[0004] The present application provides a powertrain and an electric vehicle, and the structure for preventing the outer ring of the bearing from running in circles can be designed in a normalized manner, so that the manufacturing cost of the powertrain is relatively low. Furthermore, the manufacturing cost of the electric vehicle is reduced.
[0005] In a first aspect, a powertrain is provided. The powertrain includes a bearing groove. A bearing groove includes a notch and a bottom arranged oppositely along the axial direction of the powertrain. The bottom of a bearing groove includes a recess for accommodating a contact post, and a contact post protrudes from the recess along the axial direction of the powertrain. A bearing groove is used for accommodating a bearing. The outer ring of a bearing includes two sides arranged away from each other along the axial direction of the powertrain. One side faces the bottom of a bearing groove, and one side includes another recess.
[0006] Wherein, the size of a contact post along the circumferential direction of the powertrain is less than or equal to the size of another recess. The size of another recess along the radial direction of the powertrain is greater than or equal to the size of the recess, and the distance between another recess and the axis of a bearing along the radial direction of the powertrain is less than or equal to the distance between the recess and the axis of the bearing. In other words, when the outer ring of the bearing runs in circles, another recess on the outer ring of the bearing can rotate to a position aligned with the contact post along the axial direction of the powertrain.
[0007] The powertrain provided by this application is provided with abutting columns exposed in the grooves at the bottom of the bearing grooves, and grooves are provided on the side surface of the outer ring of the bearing as a structure to prevent the outer ring of the bearing from running. When the outer ring of the bearing rotates circumferentially along the powertrain to a position where another groove on it aligns axially with the abutting column along the powertrain, the abutting column can enter another groove of the outer ring of the bearing, so that the outer ring of the bearing cannot rotate circumferentially along the powertrain, preventing the outer ring of the bearing from running. In this way, whether the bearing is in a light load condition or a heavy load condition, it can avoid the phenomenon of the outer ring of the bearing running, enabling the structure for preventing the outer ring of the bearing from running to achieve a normalized design, and reducing the manufacturing cost of the powertrain.
[0008] In addition, the structure for preventing the outer ring of the bearing from running provided by this application has a relatively simple installation process, reducing the assembly process of the powertrain and improving the assembly efficiency of the powertrain.
[0009] In one implementation, an abutting column is fixedly connected to a groove through a connecting piece. A connecting piece includes an opening and a bottom of a cylinder arranged opposite to each other along the axial direction of the powertrain, and an abutting column is exposed from an opening.
[0010] Among them, the size of a connecting piece along the radial direction of the powertrain is greater than or equal to the size of a groove. In other words, an interference fit exists between the connecting piece and a groove.
[0011] The abutting column is fixedly connected to a groove through a connecting piece with an interference fit with a groove. In this way, through the installation and disassembly of the connecting piece, the installation and disassembly of the abutting column can be achieved, making the installation and disassembly of the abutting column relatively convenient. In addition, it is also convenient for replacing the abutting column, reducing the cost of replacing the abutting column, and thus reducing the maintenance cost of the powertrain.
[0012] In one implementation, the outer peripheral surface of a connecting piece includes an annular protrusion, and along the axial direction of the powertrain, an annular protrusion is distributed at one end of a connecting piece.
[0013] During the process of installing the connecting piece into a groove, when the annular protrusion on the outer peripheral surface of the connecting piece contacts the bottom of the bearing groove, the installation of the connecting piece can be completed, simplifying the assembly process of the connecting piece and a groove. In addition, due to the existence of the annular protrusion on the connecting piece, the disassembly process of the abutting column is also relatively simple.
[0014] In one implementation, the outer peripheral surface of an abutting column includes another annular protrusion, and along the radial direction of the powertrain, the size of another annular protrusion is equal to the size of the inner wall of the connecting piece.
[0015] In this way, when the abutting column can move, another annular protrusion on the outer peripheral surface of the abutting column can move along the axial direction of the power assembly against the inner wall of the connecting piece, so that the abutting force of the abutting column against the outer ring of a bearing reaches the maximum. In addition, it is not necessary to set the dimensions of the abutting column in the radial direction of the power assembly to be the same as those of the inner wall of the connecting piece, which can reduce the mass of the abutting column and thus reduce the mass of the power assembly.
[0016] In one implementation, an abutting column is used to fixedly connect a spring. Along the axial direction of the power assembly, a spring is arranged between an abutting column and the bottom of a groove, and a spring is used to fixedly connect a groove.
[0017] On the one hand, the bearing can be blindly installed in the bearing groove, simplifying the assembly process of the power assembly. On the other hand, after the bearing is installed in the bearing groove, the abutting column can compress the spring so that the abutting column can abut against the outer ring of the bearing. When the outer ring of the bearing runs, and when the outer ring of the bearing rotates circumferentially along the power assembly to a position where another groove on it is aligned with the abutting column along the axial direction of the power assembly, under the action of the spring, the abutting column can spring into another groove of the outer ring of the bearing, thereby preventing the outer ring of the bearing from running. In this way, according to the different clearances between the bearing and the bottom of the bearing groove, the spring can adaptively adjust the length of the abutting column exposed from a groove, improving the flexibility of the structure for preventing the outer ring of the bearing from running.
[0018] In one implementation, a bearing groove is also used to accommodate a retaining ring. Along the axial direction of the power assembly, a retaining ring is arranged between a bearing and a bottom of a bearing groove. Along the circumferential direction of the power assembly, a retaining ring has an opening, and the size of an opening along the circumferential direction of the power assembly is larger than the size of another groove. In this way, the abutting column can also prevent the retaining ring from running circumferentially along the power assembly.
[0019] In one implementation, the inner diameter of a retaining ring is greater than or equal to the inner diameter of the outer ring of a bearing. The outer diameter of a retaining ring is larger than the dimension of the bearing groove in the radial direction of the power assembly. In this way, along the axial direction of the power assembly, the retaining ring can abut against the outer ring of the bearing to prevent the outer ring of the bearing from moving axially along the power assembly.
[0020] In one implementation, along the axial direction of the power assembly, the dimension of a retaining ring is smaller than the length of an abutting column exposed from a groove, and along the axial direction of the power assembly, an abutting column passes through an opening. In this way, the installation of the retaining ring is more convenient, and the abutting column can also prevent the retaining ring from running.
[0021] In one implementation, the outer peripheral surface of the input shaft of the speed reducer of the power assembly is used to fixedly connect the inner ring of a bearing, and one end of the input shaft of the speed reducer is used to drive and connect the motor shaft of the motor.
[0022] Generally, an oil inlet passage for the powertrain needs to be provided on the reducer side. Therefore, in order to reduce the complexity of the powertrain structure, a bearing pressure plate is provided on the motor side to prevent the outer ring of the bearing on the motor shaft from running. A structure for preventing the outer ring of the bearing from running provided by the present application is provided on the reducer side to prevent the outer ring of the bearing on the reducer shaft from running.
[0023] In one implementation, the reducer end cover and the intermediate housing of the powertrain are arranged along the axial direction of the powertrain. The reducer end cover includes an end face facing the intermediate housing, and the end face includes a bearing groove. The intermediate housing is used to accommodate the input shaft of the reducer and the motor shaft of the motor. Setting the bearing groove on the reducer end cover can facilitate the installation and disassembly of the reducer shaft.
[0024] In one implementation, the maximum dimension of a butting post along the radial direction of the powertrain is equal to the dimension of a groove.
[0025] In this way, when the butting post can move, the butting post can move along the axial direction of the powertrain against the groove wall of a groove, so that the butting force of the butting post on the outer ring of a bearing reaches the maximum. In addition, it is not necessary to set the dimension of the butting post along the radial direction of the powertrain to be the same as the dimension of a groove, which can reduce the mass of the butting post and thus reduce the mass of the powertrain.
[0026] In one implementation, another groove communicates with the outer peripheral surface of the outer ring of a bearing. In this way, not only can the influence of another groove on the load transfer of the rolling elements of the bearing be avoided, but also the butting post can easily enter another groove.
[0027] In one implementation, another groove includes a notch and a groove wall arranged oppositely along the axial direction of the powertrain. Among them, the length of a butting post exposed from a groove along the axial direction of the powertrain is greater than the distance between a side face and the bottom of a bearing groove and less than or equal to the distance between the groove wall of another groove and the bottom of a bearing groove. In this way, along the axial direction of the powertrain, the butting post can enter another groove of the outer ring of the bearing, so that the outer ring of the bearing cannot rotate circumferentially along the powertrain, preventing the outer ring of the bearing from running.
[0028] In a second aspect, an electric vehicle is provided. The electric vehicle includes wheels, a transmission mechanism, and a powertrain as described in any one of the first aspect and the possible implementations of the first aspect. The powertrain drives the wheels through the transmission mechanism.
[0029] Since the manufacturing cost of the powertrain provided in the first aspect is relatively low, the manufacturing cost of the electric vehicle provided in the second aspect is also relatively low. Description of the Drawings
[0030] Figure 1 Structural schematic diagram of an electric vehicle provided by an embodiment of the present application.
[0031] Figure 2 Exploded structural schematic diagram of a powertrain provided by an embodiment of the present application.
[0032] Figure 3 For Figure 2 Structural schematic diagram of the reducer end cover of the powertrain shown.
[0033] Figure 4 For Figure 3 Enlarged schematic diagram of part A of the reducer end cover shown.
[0034] Figure 5 For Figure 2 Structural schematic diagram of the bearing of the powertrain shown.
[0035] Figure 6 For Figure 2 Exploded schematic diagram of a part of the powertrain shown.
[0036] Figure 7 For Figure 6 Assembly schematic diagram of a part of the powertrain shown.
[0037] Figure 8 For Figure 2 Cross-sectional schematic diagram of the powertrain shown.
[0038] Figure 9 For Figure 8 Enlarged schematic diagram of part B of the powertrain shown.
[0039] Figure 10 For Figure 2 Assembly schematic diagram of a part of the powertrain shown.
[0040] Figure 11 For Figure 10 Enlarged schematic diagram of part C of the powertrain shown. Detailed implementation manners
[0041] Next, the technical solutions in the present application will be described with reference to the accompanying drawings.
[0042] In the description of the embodiments of the present application, unless otherwise specified, " / " means "or". For example, A / B may mean A or B. Herein, "and / or" is only a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B may mean: A exists alone, A and B exist simultaneously, and B exists alone.
[0043] The orientation or positional relationship indicated by terms such as "upper", "lower", "inner", "outer", etc. in the embodiments of the present application is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or component referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.
[0044] The reference to "some embodiments" and the like described in this specification means that in one or more embodiments of the present application, specific features, structures, or characteristics described in connection with that embodiment are included. Thus, the statements "in some embodiments" and the like that appear in different places in this specification do not necessarily all refer to the same embodiment, but mean "one or more but not all embodiments", unless otherwise specifically emphasized in other ways. The terms "include", "comprise", "have" and their variants all mean "including but not limited to", unless otherwise specifically emphasized in other ways.
[0045] The "equal / to be equal to" involved in the present application is not strictly equal / to be equal to, but within the allowable error range. The "parallel" is not strictly parallel, but within the allowable error range. The "perpendicular" is not strictly perpendicular, but within the allowable error range.
[0046] In the embodiments of the present application, the same reference numeral represents the same component or the same part. In the embodiments of the present application, for multiple identical parts, only one of the parts may be marked with a reference numeral in the drawings. The reference numeral is equally applicable to other identical parts or components. In addition, the dimensions and sizes of the parts shown in the drawings are only exemplary.
[0047] The embodiments of the present application provide a powertrain. The powertrain includes a bearing groove. A bearing groove includes a notch and a bottom arranged axially opposite to each other along the powertrain. The bottom of a bearing groove includes a recess. The recess is used to accommodate an abutting post. An abutting post axially along the powertrain protrudes from the recess. A bearing groove is used to accommodate a bearing. The outer ring of a bearing includes two sides arranged axially away from each other along the powertrain. One side faces the bottom of a bearing groove. One side includes another recess.
[0048] Wherein, the size of an abutting post circumferentially along the powertrain is less than or equal to the size of another recess. The size of another recess radially along the powertrain is greater than or equal to the size of the recess. The distance between another recess and the axis of a bearing radially along the powertrain is less than or equal to the distance between the recess and the axis of the bearing. In other words, when the outer ring of the bearing runs out of circle, another recess on the outer ring of the bearing can rotate to a position axially aligned with the abutting post along the powertrain.
[0049] For the powertrain provided by this application, a contact post exposed outside the groove is provided in the groove at the bottom of the bearing groove, and a groove is provided on the side surface of the outer ring of the bearing as a structure to prevent the outer ring of the bearing from running. When the outer ring of the bearing rotates circumferentially along the powertrain to a position where another groove on it is axially aligned with the contact post along the powertrain, the contact post can enter another groove of the outer ring of the bearing, so that the outer ring of the bearing cannot rotate circumferentially along the powertrain, preventing the outer ring of the bearing from running. In this way, whether the bearing is in a light load condition or a heavy load condition, it can avoid the phenomenon of the outer ring of the bearing running, enabling the structure for preventing the outer ring of the bearing from running to achieve a normalized design and reducing the manufacturing cost of the powertrain.
[0050] In addition, the structure for preventing the outer ring of the bearing from running provided by this application has a relatively simple installation process, reducing the assembly process of the powertrain and improving the assembly efficiency of the powertrain.
[0051] The embodiment of this application also provides an electric vehicle. The following will be combined with Figure 1 to elaborate in detail on the electric vehicle provided by the embodiment of this application.
[0052] Figure 1 It is a schematic structural diagram of an electric vehicle provided by the embodiment of this application. As Figure 1 shown, the electric vehicle includes one or more powertrains 10, a battery 20, and wheels 30. Among them, the powertrain 10 is used to receive power supply from the battery 20 and drive the wheels 30, and the powertrain 10 is used to convert electrical energy into mechanical energy.
[0053] The electric vehicle provided by the embodiment of this application includes pure electric vehicles, hybrid vehicles, range extended electric vehicles, plug-in hybrid vehicles, or new energy vehicles, etc. Among them, a pure electric vehicle is also called a pure electric vehicle / battery electric vehicle, or simply referred to as a pure EV / battery EV. A hybrid vehicle is also called a hybrid electric vehicle, or simply referred to as an HEV. A range extended electric vehicle is also called a range extended electric vehicle, or simply referred to as a REEV. A plug-in hybrid vehicle is also called a plug-in hybrid electric vehicle, or simply referred to as a PHEV. A new energy vehicle is also called a new energy vehicle, or simply referred to as a NEV.
[0054] In some embodiments, the powertrain 10 is an integrated powertrain. In other words, the powertrain 10 includes a speed reducer and an electric motor, and the input shaft of the speed reducer is drivingly connected to the motor shaft of the electric motor. The rotation of the motor shaft of the electric motor can drive the rotation of the input shaft of the speed reducer. The axial direction of the input shaft of the speed reducer is parallel to the axial direction of the motor shaft of the electric motor.
[0055] Exemplarily, the speed reducer and the electric motor can share a housing, that is, the housing of the powertrain 10 is used to accommodate the speed reducer and the electric motor. For example, the housing of the powertrain 10 includes a speed reducer end cover, an intermediate housing, and a motor end cover. The speed reducer end cover is used to fix the bearings of the respective shafts of the speed reducer, the motor end cover is used to fix the bearings of the respective shafts of the electric motor, and the intermediate housing is used to accommodate the speed reducer and the electric motor. The intermediate housing includes two openings arranged along the axial direction of the powertrain. The speed reducer end cover and the motor end cover respectively cover the two openings of the intermediate housing to form the accommodation cavity of the powertrain 10. In this way, the accommodation cavity of the powertrain 10 includes a speed reducer accommodation cavity and a motor accommodation cavity, and the speed reducer accommodation cavity and the motor accommodation cavity are arranged along the axial direction of the powertrain.
[0056] In some embodiments, the powertrain 10 is a three-in-one powertrain. In other words, in addition to including a speed reducer and an electric motor, the powertrain 10 further includes a motor controller, and the motor controller is used to control the start or stop, forward or reverse rotation, speed increase or decrease, drive torque increase or decrease, braking torque increase or decrease, etc. of the electric motor.
[0057] Exemplarily, the motor controller, the speed reducer, and the electric motor can share a housing, that is, the housing of the powertrain 10 is used to accommodate the motor controller, the speed reducer, and the electric motor. For example, the housing of the powertrain 10 includes a speed reducer end cover, an intermediate housing, a controller end cover, and a motor end cover. The speed reducer end cover is used to fix the bearings of the respective shafts of the speed reducer, the motor end cover is used to fix the bearings of the respective shafts of the electric motor, and the intermediate housing is used to accommodate the speed reducer and the electric motor. The intermediate housing includes two openings arranged along a first direction and another opening facing a second direction. The speed reducer end cover and the motor end cover respectively cover the two openings of the intermediate housing, and the controller end cover covers the other opening of the intermediate housing to form the accommodation cavity of the powertrain 10. In this way, the accommodation cavity of the powertrain 10 includes a speed reducer accommodation cavity, a motor accommodation cavity, and a motor controller accommodation cavity. The speed reducer accommodation cavity and the motor accommodation cavity are arranged along the first direction, and the motor accommodation cavity and the motor controller accommodation cavity are arranged along the second direction. Among them, the first direction intersects with the second direction. For example, the first direction is parallel to the axial direction of the powertrain 10, and the second direction is perpendicular to the axial direction of the powertrain 10.
[0058] In one example, the reducer involved in the embodiments of the present application is a two-shaft parallel-axis reducer, that is, the reducer includes an input shaft and an output shaft, the axial directions of the input shaft and the output shaft of the reducer are parallel, and the gears on the input shaft of the reducer and the gears on the output shaft of the reducer mesh with each other, so as to realize the rotation of the output shaft of the reducer driven by the input shaft of the reducer.
[0059] In another example, the reducer involved in the embodiments of the present application is a three-shaft parallel-axis reducer, that is, the reducer includes an input shaft, an intermediate shaft and an output shaft, the axial directions of the input shaft, the intermediate shaft and the output shaft of the reducer are respectively parallel, and the gears on the input shaft of the reducer and the gears on the intermediate shaft of the reducer mesh with each other, so as to realize the rotation of the intermediate shaft of the reducer driven by the input shaft of the reducer. The gears on the intermediate shaft of the reducer and the gears on the output shaft of the reducer mesh with each other, so as to realize the rotation of the output shaft of the reducer driven by the intermediate shaft of the reducer.
[0060] A bearing groove is provided on the housing of the powertrain 10. Here, the bearing groove on the reducer end cover 110 of the powertrain 10 will be described in detail as an example.
[0061] As Figure 2 shown, the powertrain 10 includes a reducer end cover 110. As Figure 3 and Figure 4 shown, one side of the reducer end cover 110 facing the intermediate housing of the powertrain 10 includes a bearing groove G. Along the axial direction of the powertrain, the bearing groove G is recessed from the side facing the intermediate housing towards the inside of the reducer end cover 110. The bearing groove G includes a notch G1 and a groove bottom G2 arranged opposite to each other along the axial direction of the powertrain. Setting the bearing groove G on the reducer end cover 110 can facilitate the installation and disassembly of each shaft of the reducer.
[0062] As Figure 2 shown, the powertrain 10 further includes a bearing 120. Along the axial direction of the powertrain, the depth of the bearing groove G is greater than the width of the bearing 120, and the bearing groove G is used to accommodate the bearing 120. As Figure 2 and Figure 5 shown, the bearing 120 includes an outer ring 121, an inner ring 122 and a plurality of rolling elements 123. The plurality of rolling elements 123 are spaced apart along the circumferential direction of the powertrain, and the plurality of rolling elements 123 are distributed between the outer ring 121 and the inner ring 122 along the radial direction of the powertrain. The outer ring 121 includes two side surfaces E1 to E2 arranged opposite to each other along the axial direction of the powertrain. The side surface E1 of the outer ring 121 of the bearing 120 faces the groove bottom G2 of the bearing groove G, and the side surface E1 includes a groove G3. Along the radial direction of the powertrain, the size of the groove G3 of the outer ring 121 of the bearing 120 is greater than or equal to the groove G of the groove bottom G2 of the bearing groove G 21The distance between the groove G3 of the outer ring 121 of the powertrain radial bearing 120 and the axis of the bearing 120 is less than or equal to the groove G of the groove bottom G2 of the bearing groove G. 21 The distance from the axis of the bearing 120.
[0063] In some embodiments, Figure 2 and Figure 5 As shown, the groove G3 of the outer ring 121 of the bearing 120 is connected to the outer peripheral surface of the outer ring 121 of the bearing 120, that is, the groove G3 of the outer ring 121 of the bearing 120 includes a notch and a groove wall arranged oppositely along the axial direction of the power assembly and another notch and another groove wall arranged oppositely along the radial direction of the power assembly. In this way, not only can the groove G3 of the outer ring 121 of the bearing 120 be prevented from affecting the load transmission of the rolling element 123 of the bearing 120, but also the abutment column 130 can easily enter the groove G3 of the outer ring 121 of the bearing 120.
[0064] like Figure 3 and Figure 4 As shown, the groove bottom G2 of the bearing groove G is provided with a groove G 21 , Groove G 21 The groove G is recessed from the groove bottom G2 of the bearing groove G in a direction away from the groove bottom G2 of the bearing groove G. 21 It is used to accommodate the abutment column 130, and the abutment column 130 is exposed in the groove G along the axial direction of the powertrain. 21 .
[0065] The size of the abutment column 130 along the circumferential direction of the powertrain is less than or equal to the size of the groove G3 of the outer ring 121 of the bearing 120. In other words, when the outer ring 121 of the bearing 120 runs, the groove G3 on the outer ring 121 of the bearing 120 can rotate to a position aligned with the abutment column 130 along the axial direction of the powertrain.
[0066] In this way, the groove G at the bottom G2 of the bearing groove G 21 The middle setting is exposed in the groove G 21 The abutment column 130 is provided, and a groove G3 is provided on the side E1 of the outer ring 121 of the bearing 120 as a structure to prevent the outer ring 121 of the bearing 120 from running in circles. When the outer ring 121 of the bearing 120 rotates along the circumferential direction of the powertrain to a position where the groove G3 thereon is aligned with the abutment column 130 along the axial direction of the powertrain, the abutment column 130 can enter the groove G3 of the outer ring 121 of the bearing 120, so that the outer ring 121 of the bearing 120 cannot rotate along the circumferential direction of the powertrain, thereby preventing the outer ring 121 of the bearing 120 from running in circles. In this way, whether the bearing 120 is under light load or heavy load conditions, it can prevent the outer ring 121 of the bearing 120 from running in circles, so that the structure to prevent the outer ring 121 of the bearing 120 from running in circles can be standardized in design, thereby reducing the manufacturing cost of the powertrain 10.
[0067] In addition, the structural installation process for preventing the outer ring 121 of the bearing 120 from running around provided in the present application is relatively simple, which reduces the assembly process of the power assembly 10 and improves the assembly efficiency of the power assembly 10.
[0068] In some embodiments, Figure 2 As shown, groove G 21 The reducer end cover 110 is recessed from one side facing the intermediate housing, and protrudes from the side of the reducer end cover 110 away from the intermediate housing. In this way, even if the reducer end cover 110 is insufficient in the axial direction of the powertrain, the reliability of the structure for preventing the outer ring 121 of the bearing 120 from running can be ensured.
[0069] In some embodiments, the groove G of the bottom G2 of the bearing groove G is exposed along the axial direction of the powertrain abutting the column 130. 21 The length is greater than the distance between the side surface E1 of the outer ring 121 of the bearing 120 and the groove bottom G2 of the bearing groove G, and less than or equal to the distance between the groove wall of the groove G3 of the outer ring 121 of the bearing 120 and the groove bottom G2 of the bearing groove G. In this way, the abutment column 130 can enter the groove G3 of the outer ring 121 of the bearing 120 along the axial direction of the power assembly, so that the outer ring 121 of the bearing 120 cannot rotate along the circumferential direction of the power assembly, thereby preventing the outer ring 121 of the bearing 120 from running in circles.
[0070] In one example, the length of the abutment column 130 along the axial direction of the powertrain is greater than the length of the groove G. 21 Depth.
[0071] In an example, Figure 6 and Figure 7 As shown, a spring 150 is provided between the abutment column 130 and the groove bottom G2 of the bearing groove G. The sum of the length of the abutment column 130 and the length of the spring 150 along the axial direction of the powertrain is greater than the groove G. 21 One end of the spring 150 is used to fix the connection with the abutment column 130, and the other end of the spring 150 is used to fix the connection with the bearing groove G.
[0072] In this way, on the one hand, the bearing 120 can be blindly installed in the bearing groove G, simplifying the assembly process of the powertrain 10. On the other hand, after the bearing 120 is installed in the bearing groove G, the abutting column 130 can compress the spring 150 so that the abutting column 130 can abut against the outer ring 121 of the bearing 120. When the outer ring 121 of the bearing 120 runs, and when the outer ring 121 of the bearing 120 rotates circumferentially along the powertrain to a position where the groove G3 on it is aligned with the abutting column 130 axially along the powertrain, under the action of the spring 150, the abutting column 130 can spring into the groove G3 of the outer ring 121 of the bearing 120, thereby preventing the outer ring 121 of the bearing 120 from running. In this way, according to the different clearances between the bearing 120 and the bottom G2 of the bearing groove G, the spring 150 can adaptively adjust the length of the abutting column 130 exposed from the bottom G2 of the bearing groove G, improving the flexibility of the structure for preventing the outer ring 121 of the bearing 120 from running. 21 The length of the groove G improves the flexibility of the structure for preventing the outer ring 121 of the bearing 120 from running.
[0073] In some embodiments, the abutting column 130 is provided as detachable. For example, as shown in Figure 2 , Figure 6 and Figure 7 , a connecting member 140 is sleeved outside the abutting column 130, and the length of the connecting member 140 along the powertrain axis is greater than or equal to the depth of the groove G 21 . The connecting member 140 includes an opening and a bottom of the cylinder arranged oppositely along the powertrain axis, and the abutting column 130 is exposed from the opening of the connecting member 140. In addition, the size of the connecting member 140 along the powertrain radial direction is greater than or equal to the size of the groove G 21 . In other words, an interference fit exists between the connecting member 140 and the groove G 21 , and the connecting member 140 realizes the fixed connection between the abutting column 130 and the groove G 21 through the interference fit with the groove G 21 . In this way, through the installation and disassembly of the connecting member 140, the installation and disassembly of the abutting column 130 can be realized, making the installation and disassembly of the abutting column 130 relatively convenient. In addition, it is also convenient for replacing the abutting column 130, reducing the cost of replacing the abutting column 130, and thus reducing the maintenance cost of the powertrain 10.
[0074] In one example, the length of the abutting column 130 along the powertrain axis is greater than the length of the connecting member 140, and the abutting column 130 is fixedly connected to the connecting member 140. In one example, the sum of the length of the abutting column 130 along the powertrain axis and the length of the spring 150 is greater than the length of the connecting member 140. In this example, one end of the spring 150 is fixedly connected to the abutting column 130, and the other end of the spring 150 is fixedly connected to the bottom of the cylinder of the connecting member 140. In this way, the spring 150 is fixedly connected to the groove G 21 through the connecting member 140.
[0075] In some embodiments, in the embodiment where the connecting member 140 is not provided outside the abutting column 130, the maximum dimension of the abutting column 130 in the radial direction of the power assembly is equal to the dimension of the groove G 21 For example, as Figure 6 and Figure 7 shown, the outer peripheral surface of the abutting column 130 includes an annular protrusion P1. The annular protrusion P1 on the outer peripheral surface of the abutting column 130 protrudes from the outer peripheral surface of the abutting column 130 towards the outside away from the inside of the abutting column 130. The dimension of the annular protrusion P1 on the outer peripheral surface of the abutting column 130 in the radial direction of the power assembly is equal to the dimension of the groove G 21 In this way, when the abutting column 130 can move, the annular protrusion P1 on the outer peripheral surface of the abutting column 130 can move along the axial direction of the power assembly against the groove wall of the groove G 21 so that the abutting force of the abutting column 130 on the outer ring 121 of the bearing 120 reaches the maximum. In addition, it is not necessary to set the dimension of the abutting column 130 in the radial direction of the power assembly to be the same as the dimension of the groove G 21 so that the mass of the abutting column 130 can be reduced, and further the mass of the power assembly 10 can be reduced.
[0076] In some embodiments, in the embodiment where the connecting member 140 is provided outside the abutting column 130, the maximum dimension of the abutting column 130 in the radial direction of the power assembly is equal to the dimension of the inner wall of the connecting member 140. For example, as Figure 6 and Figure 7 shown, the dimension of the annular protrusion P1 on the outer peripheral surface of the abutting column 130 in the radial direction of the power assembly is equal to the dimension of the inner wall of the connecting member 140. In this way, when the abutting column 130 can move, the annular protrusion P1 on the outer peripheral surface of the abutting column 130 can move along the axial direction of the power assembly against the inner wall of the connecting member 140, so that the abutting force of the abutting column 130 on the outer ring 121 of the bearing 120 reaches the maximum. In addition, it is not necessary to set the dimension of the abutting column 130 in the radial direction of the power assembly to be the same as the dimension of the inner wall of the connecting member 140, and the mass of the abutting column 130 can be reduced, and further the mass of the power assembly 10 can be reduced.
[0077] In some embodiments, the annular protrusion P1 on the outer peripheral surface of the abutting column 130 in the axial direction of the power assembly is distributed at one end of the abutting column 130. In this way, the processing technology of the abutting column 130 can be simplified.
[0078] In some embodiments, as Figure 6 and Figure 7 shown, the outer peripheral surface of the connecting member 140 includes an annular protrusion P2. The annular protrusion P2 on the outer peripheral surface of the connecting member 140 protrudes from the outer peripheral surface of the connecting member 140 towards the outside away from the inside of the connecting member 140. The dimension of the annular protrusion P2 on the outer peripheral surface of the connecting member 140 in the radial direction of the power assembly is greater than the groove G of the groove bottom G2 of the bearing groove G21 Dimensions. In this way, during the process of installing the connecting member 140 into the groove G 21 when the annular protrusion P2 contacts the bottom G2 of the bearing groove G, the annular protrusions P2 on the outer peripheral surface of the connecting member 140 along the axial direction of the powertrain are arranged between the groove G 21 and the notch G1 of the bearing groove G, the installation of the connecting member 140 can be completed, simplifying the assembly process of the connecting member 140 and the groove G 21 . In addition, due to the existence of the annular protrusion P2 on the connecting member 140, the disassembly process of the abutting post 130 is also relatively simple.
[0079] In some embodiments, the annular protrusions P2 on the outer peripheral surface of the connecting member 140 along the axial direction of the powertrain are distributed at one end of the connecting member 140. In this way, the processing technology of the connecting member 140 can be simplified.
[0080] In some embodiments, as Figure 2 shown, the powertrain 10 further includes a retaining ring 160. As Figure 8 and Figure 9 shown, the bearing groove G is also used to accommodate a retaining ring 160. Along the axial direction of the powertrain, a retaining ring 160 is arranged between the bearing 120 and the bottom G2 of the bearing groove G. There is a gap J between the bearing 120 and the bottom G2 of the bearing groove G along the axial direction of the powertrain, and the gap J is used to accommodate the retaining ring 160.
[0081] As Figure 10 and Figure 11 shown, the retaining ring 160 has an opening O along the circumferential direction of the powertrain. In some embodiments, the size of the opening O along the circumferential direction of the powertrain is larger than the size of the groove G3 of the outer ring 121 of the bearing 120. In this way, the installation of the retaining ring 160 is more convenient. Along the axial direction of the powertrain, the size of the retaining ring 160 is smaller than the length of the abutting post 130 exposed from the groove G 21 . Along the axial direction of the powertrain, the abutting post 130 passes through the opening O. In this way, the abutting post 130 can prevent the retaining ring 160 from running around along the circumferential direction of the powertrain. The retaining ring 160 in the embodiments of the present application can be called a C-shaped retaining ring.
[0082] In some embodiments, as Figure 3 shown, the size of the retaining ring 160 along the axial direction of the powertrain is equal to the size of the gap J. In this way, the retaining ring 160 can prevent the bearing 120 from moving along the axial direction of the powertrain, realizing the axial positioning of the bearing 120.
[0083] In some embodiments, the inner diameter of the retaining ring 160 is greater than or equal to the inner diameter of the outer ring 121 of the bearing 120, and the outer diameter of the retaining ring 160 is greater than the dimension of the bearing groove G in the radial direction of the powertrain. In this way, along the axial direction of the powertrain, the retaining ring 160 can abut against the outer ring 121 of the bearing 120 to prevent the outer ring 121 of the bearing 120 from moving along the axial direction of the powertrain.
[0084] Generally, bearing pressure plates can be provided at both ends of other shafts of the reducer except the input shaft to prevent the outer ring of the bearing on the motor shaft from running. Since the input shaft of the reducer and the motor shaft of the motor are arranged along the axial direction of the powertrain, and the input shaft of the reducer is in transmission connection with the motor shaft of the motor. In addition, an oil inlet passage for the powertrain 10 needs to be provided on the input shaft side of the reducer to provide a cooling and lubrication system for the powertrain 10. Therefore, in some embodiments, in order to reduce the complexity of the structure of the powertrain 10, a bearing pressure plate is provided on the motor side to prevent the outer ring of the bearing on the motor shaft from running. On the input shaft side of the reducer, the structure provided in this application for preventing the outer ring of the bearing from running is provided to prevent the outer ring of the bearing on the reducer shaft from running.
[0085] In this way, the outer peripheral surface of the input shaft of the reducer is used for fixedly connecting the inner ring 122 of the bearing 120, and the bearing 120 is distributed at one end of the input shaft of the reducer, and the other end of the input shaft of the reducer is used for transmission connection with the motor shaft of the motor.
[0086] It should be noted that the axial direction of the powertrain can be understood as the axial direction of the powertrain 10, the axial direction of the reducer, and the axial direction of the motor. The axial direction of the reducer refers to the axial directions of the respective shafts of the reducer, and the axial direction of the motor refers to the axial direction of the motor shaft of the motor. The radial direction of the powertrain can be understood as the radial direction of the powertrain 10, the radial direction of the reducer, and the radial direction of the motor. The radial direction of the reducer refers to the radial directions of the respective shafts of the reducer, and the radial direction of the motor refers to the radial direction of the motor shaft of the motor. The circumferential direction of the powertrain can be understood as the circumferential direction of the powertrain 10, the circumferential direction of the reducer, and the circumferential direction of the motor. The circumferential direction of the reducer refers to the circumferential directions of the respective shafts of the reducer, and the circumferential direction of the motor refers to the circumferential direction of the motor shaft of the motor. The circumferential direction can also be understood as the circumferential direction.
[0087] The above is only the specific implementation manner of the present application, but the protection scope of the present application is not limited thereto. Any person skilled in the art within the technical scope disclosed in the present application can easily think of changes or substitutions, which should all 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 power assembly includes a bearing groove, the bearing groove includes a notch and a groove bottom arranged opposite to each other along the axial direction of the power assembly, a groove bottom of the bearing groove includes a groove, the groove is used to accommodate an abutment column, the abutment column is exposed from the groove along the axial direction of the power assembly, the bearing groove is used to accommodate a bearing, the outer ring of the bearing includes two side surfaces arranged opposite to each other along the axial direction of the power assembly, one of the side surfaces faces a groove bottom of the bearing groove, the side surface includes another groove, wherein: The dimension of the one abutment column along the circumference of the powertrain is smaller than or equal to the dimension of the other groove; The size of the other groove along the radial direction of the powertrain is greater than or equal to the size of the one groove, and the distance between the other groove and the axis center of the one bearing along the radial direction of the powertrain is less than or equal to the distance between the one groove and the axis center of the one bearing.
2. The powertrain according to claim 1, characterized in that: The abutment column is fixedly connected to the groove through a connecting member, the connecting member includes an opening and a cylinder bottom arranged opposite to each other along the axial direction of the power assembly, and the abutment column is exposed from the opening, wherein: A dimension of the one connecting member along the radial direction of the power assembly is greater than or equal to a dimension of the one groove.
3. The powertrain according to claim 2, characterized in that: The outer peripheral surface of the one connecting member comprises an annular protrusion, and the one annular protrusion is distributed at one end of the one connecting member along the axial direction of the power assembly.
4. The powertrain according to claim 2, characterized in that: The outer peripheral surface of the one abutting column includes another annular protrusion, and the size of the other annular protrusion along the radial direction of the power assembly is equal to the size of the inner wall of the one connecting member.
5. The powertrain according to claim 1, characterized in that: The abutment column is used for fixedly connecting a spring, and the spring is arranged between the abutment column and the bottom of the groove along the axial direction of the power assembly, and the spring is used for fixedly connecting the groove.
6. The powertrain according to claim 1, characterized in that: The one bearing groove is also used to accommodate a retaining ring, and the one retaining ring is arranged between the one bearing and a groove bottom of the one bearing groove along the axial direction of the power assembly, wherein: The one retaining ring has an opening along the circumference of the powertrain, and the size of the one opening along the circumference of the powertrain is larger than the size of the other groove.
7. The powertrain according to claim 6, characterized in that: The inner diameter of the retaining ring is greater than or equal to the inner diameter of the outer ring of the bearing.
8. The powertrain according to claim 6, characterized in that: The outer diameter of the retaining ring is greater than the radial dimension of the bearing groove along the power assembly.
9. The powertrain according to claim 6, characterized in that: The dimension of the retaining ring along the axial direction of the power assembly is smaller than the length of the abutting column exposed from the groove, and the abutting column passes through the opening along the axial direction of the power assembly.
10. The powertrain according to claim 1, characterized in that: The outer peripheral surface of the input shaft of the reducer of the power assembly is used for fixedly connecting to the inner ring of the one bearing, and one end of the input shaft of the reducer is used for transmission connection to the motor shaft of the motor.
11. The powertrain according to claim 1, characterized in that: The reducer end cover and the intermediate housing of the power assembly are arranged axially along the power assembly, the reducer end cover includes an end face facing the intermediate housing, the end face includes the bearing groove, and the intermediate housing is used to accommodate the input shaft of the reducer and the motor shaft of the motor.
12. The powertrain according to claim 1, characterized in that: The maximum dimension of the one abutting column along the radial direction of the powertrain is equal to the dimension of the one groove.
13. The powertrain according to claim 1, characterized in that: The other groove is in communication with the outer peripheral surface of the outer ring of the one bearing.
14. The power assembly according to any one of claims 1 to 13, characterized in that: The other groove comprises a notch and a groove wall which are arranged opposite to each other along the axial direction of the powertrain, wherein: The length of the abutment column exposed in the groove along the axial direction of the powertrain is greater than the distance between the side surface and a groove bottom of the bearing groove, and less than or equal to the distance between a groove wall of the other groove and a groove bottom of the bearing groove.
15. An electric vehicle, characterized in that: The electric vehicle comprises wheels, a transmission mechanism, and a powertrain according to any one of claims 1 to 14, wherein the powertrain drives the wheels via the transmission mechanism.