Bearing ring running prevention power assembly and electric vehicle

Abstract

A power assembly shell comprises a bearing groove, the bearing groove is used for containing a bearing outer ring, a bearing inner ring is used for fixing a transmission shaft, the inner circumferential face of the bearing groove comprises a groove used for containing one end of a pin, the outer circumferential face of the outer ring comprises another groove used for containing one end of the pin, and the other end of the pin is used for containing the other end of the pin. The distance between the groove bottom of the other groove and the inner circumferential surface of the bearing groove in the radial direction of the outer ring is smaller than the length of the pin, and the width in the circumferential direction of the outer ring is smaller than the outer circumference of the outer ring and larger than or equal to the width of the other end of the pin. When the bearing outer ring runs, the pin is fixedly connected with the other groove in the peripheral surface of the bearing outer ring to limit the sliding of the bearing outer ring relative to the bearing groove; and the pin is utilized, so that the outer ring and the groove of the bearing groove do not need to be aligned deliberately when the bearing is mounted, the mounting difficulty of the bearing is reduced, and the mounting efficiency of the power assembly is improved.

Description

Technical Field

[0001] This application relates to the field of electric vehicles, and in particular to a powertrain for preventing bearing slippage and an electric vehicle. Background Technology

[0002] In the electric vehicle industry, bearings are widely used in powertrains. During long-term use, bearing outer ring slippage often occurs, where the outer ring rotates with the shaft, causing relative friction between the outer ring and the bearing groove, generating particulate matter. This foreign matter not only makes cleaning the powertrain difficult but also affects the bearing's lifespan. Simultaneously, bearing outer ring slippage can also cause noise, vibration, and harshness (NVH) problems, impacting production line yield. Utility Model Content

[0003] This application provides a powertrain assembly to prevent bearing raceage. The housing of the powertrain includes at least one bearing groove for accommodating the outer ring of a bearing. The inner ring of the bearing is used to fix a drive shaft. The inner circumferential surface of the bearing groove includes a recess for accommodating one end of a pin. The outer circumferential surface of the outer ring includes another recess for accommodating the other end of the pin. The radial distance between the bottom of the other recess and the inner circumferential surface of the bearing groove is less than the length of the pin, and the circumferential width of the other recess is less than the outer circumference of the outer ring and greater than or equal to the width of the other end of the pin. In the powertrain assembly provided by this application, when bearing raceage occurs, the pin is fixedly connected to another recess on the outer circumferential surface of the bearing outer ring, preventing the outer ring from racing relative to the bearing groove. Furthermore, the use of the pin eliminates the need for deliberate alignment of the outer ring and the recess in the bearing groove during bearing installation, reducing the difficulty of bearing installation and improving the installation efficiency of the powertrain.

[0004] In one possible implementation, the groove accommodates an elastic element, with its two ends connected to the inner wall of the groove and one end of a pin, respectively. The radial length of the elastic element along the bearing groove is less than the length of the groove. The elastic element is a flexible structure, eliminating the need for precise alignment between the outer ring's groove and the bearing groove during bearing installation. This reduces the difficulty of bearing installation, improves the installation efficiency between the bearing and the bearing groove, and ultimately enhances the installation efficiency of the powertrain.

[0005] In one possible implementation, the groove is used to accommodate a sleeve, the width of the groove is equal to the width of the sleeve in at least one direction (circumferential and axial) of the bearing groove, the radial length of the sleeve along the bearing groove is less than or equal to the depth of the groove, the inner cavity of the sleeve is used to accommodate an elastic element, and the inner wall of the sleeve is used to fix one end of the elastic element. Pre-fixing the sleeve, pin, and elastic element as a single assembly makes external assembly of the sleeve, elastic element, and pin more convenient, simplifies installation steps, and reduces workload during on-site installation. The insertion method of the sleeve makes the installation process more intuitive and reduces installation difficulty. Inserting the assembly as a whole into the groove ensures the accurate positioning of the pin and elastic element, avoiding deviations during installation. The interference fit between the groove and the sleeve provides additional positioning stability, ensuring that the assembly will not move or misalign during installation. Furthermore, the elastic element and pin can be pre-installed in the sleeve, and the assembly of the pin and the groove can be achieved simply by inserting the sleeve equipped with the elastic element and pin into the groove, thereby improving the assembly efficiency of the powertrain.

[0006] In one possible implementation, the inner cavity of the sleeve is used to accommodate one end of the pin. The depth of the inner cavity of the sleeve along the radial direction of the bearing groove is greater than the length of the elastic element, and the width along at least one direction of the bearing groove (circumferential and axial) is greater than or equal to the width of one end of the pin. This method ensures that the inner cavity of the sleeve has sufficient space to accommodate at least one end of the pin; when the sleeve is inserted into the groove, the pin is accommodated in the inner cavity of the sleeve and can be inserted into the groove along with the sleeve, without the pin being stuck outside the groove of the bearing groove.

[0007] In one possible implementation, the groove along the radial direction of the bearing groove includes two inner sidewalls, wherein the width of one inner sidewall along at least one direction of the bearing groove (circumferential and axial) is greater than the width of the elastic element, less than the width of the other inner sidewall, and less than the width of the pin. The inner sidewall is used to connect with the groove opening of the groove on both sides of the other inner sidewall along the radial direction of the bearing groove. The width of the other inner sidewall along at least one direction of the bearing groove (circumferential and axial) is greater than or equal to the width of the pin, and the length along the radial direction of the bearing groove is greater than or equal to the length of the pin. A partial groove formed by one inner sidewall can accommodate at least a portion of the elastic element and hold the pin outside the inner sidewall; another partial groove formed by the other inner sidewall can completely accommodate the pin, which can be fully retracted into the other partial groove formed by the other inner sidewall, preventing the pin from being stuck in a deeper part of the groove and unable to extend into the other groove. One inner sidewall can also limit the elastic element to a certain extent, preventing the elastic element from bending laterally after being compressed, preventing the elastic element from deforming and causing a large frictional force between the pin and the sidewall of the groove, ensuring that the pin can be smoothly ejected from one groove to another.

[0008] In one possible implementation, the outer peripheral surface of the bearing groove includes a reinforcing rib. The groove opening is positioned on opposite sides of the reinforcing rib along the radial direction of the bearing groove's circumferential sidewall. The depth of the groove along the radial direction of the bearing groove is less than the radial distance between the inner peripheral surface of the bearing groove and the outer wall of the reinforcing rib. The reinforcing rib enhances the strength and rigidity of the housing containing the bearing groove, effectively improving the structural strength and rigidity of both the bearing groove and the housing. The reinforcing rib can overcome the torsional deformation caused by uneven stress due to differences in wall thickness within the bearing groove. The groove, located on the inner side of the bearing groove opposite the original reinforcing rib, prevents a significant reduction in the structural strength of the bearing groove and housing due to the groove.

[0009] In one possible implementation, the other end of one pin includes a ball head, the outer diameter of which is less than or equal to the inner diameter of the groove opening. The other groove includes an arc-shaped sidewall, the inner diameter of which is equal to the outer diameter of the ball head. The ball head has sufficient space within the groove for smooth expansion and contraction. If the groove opening diameter is too small, it will restrict the range of motion of the ball head, potentially causing jamming and affecting the effectiveness of fixing the outer ring of the bearing. The spherical surface of the ball head can tightly fit against the arc-shaped sidewall of the other groove, providing a stable connection. The arc-shaped sidewall ensures that the ball head will not loosen or fall out after insertion, while the friction between the spherical surface and the arc-shaped sidewall prevents the ball head from detaching from the other groove. The tight fit between the spherical surface and the arc-shaped sidewall ensures the stability of the connection, preventing the ball head from loosening or falling out due to vibration or impact.

[0010] In one possible implementation, along the radial direction of one bearing groove, the length of the portion of the ball head protruding from one groove is greater than or equal to the radius of the ball head, and the depth of the other groove is greater than or equal to the radius of the ball head. A larger contact area between the ball head and the other groove helps enhance the stability of the fixed connection between the ball head and the other groove; furthermore, the inner diameter of the groove opening is less than or equal to the radius of the ball head or the radius of the arcuate sidewall, which helps to more firmly hold the ball head in the arcuate sidewall, preventing the ball head from easily falling off or loosening under external force, thereby improving the reliability and durability of the connection. The tight connection between the ball head and the arcuate sidewall enhances the stability of the bearing, making it smoother and vibration-free during operation; the larger contact area between the ball head and the arcuate sidewall allows the bearing to withstand greater loads, thereby improving its load-bearing capacity; the tight connection and stable operation between the ball head and the arcuate sidewall reduce bearing wear and failure rate, thereby extending its service life.

[0011] In one possible implementation, the outer circumferential surface of the outer ring includes a chamfer or a fillet, located at one axial end of the outer circumferential surface of the outer ring. The chamfer or fillet is used to surround one end face of the outer ring circumferentially, and the length of the chamfer or fillet along the axial direction of the outer ring is greater than or equal to the length of the portion of the pin protruding from the groove. The chamfer and fillet make the axial edges of the outer ring smoother, facilitating contact with the pin and making it easier to press the pin into the groove during bearing installation. This prevents the pin from interfering with bearing installation and reduces installation difficulty. Under the pressure of the chamfer and fillet at both axial ends of the outer ring, the pin causes the elastic element to deform, making it easier to adapt to the installation process. The chamfer and fillet design enhances the adaptability of the pin and makes it less susceptible to damage during installation. Chamfers and fillets reduce the frictional area between the outer ring's axial ends and the pin, decreasing heat and wear generated by friction. This helps extend the service life of the bearing and pin, and reduces metal debris generated by friction. Chamfers and fillets also help optimize the contact state between the outer ring's axial ends and the pin, ensuring that stress is evenly distributed on the contact surface when the bearing is under load, avoiding excessive local stress that leads to wear and metal debris generation.

[0012] In one possible implementation, the other groove, along the axial direction of one bearing groove, extends through both end faces of the outer ring. This facilitates easier alignment and insertion of the pin into the other groove. The groove design extending through the end faces increases the contact area between the engaging components, thereby improving the strength and stability of the connection. When disassembling or replacing the bearing, the pin can slide out more easily from the other groove extending through the end faces of the outer ring without being subjected to excessive friction or compression. The bearing can engage with the pin at any axial position, reducing the risk of damage to the bearing or pin during disassembly and facilitating blind disassembly of the bearing.

[0013] In one possible implementation, the length of the other groove along the axial direction of the first bearing groove is less than the length of the outer ring. The other groove along the axial direction of the first bearing groove is used to penetrate one end face of the outer ring and to connect the gap between the outer ring and the bottom of the bearing groove. At least one end of the bearing is not penetrated by the other groove, forming a shielding enclosure structure that helps prevent external substances from entering the bearing groove and also limits the escape of internal substances, such as debris generated by sliding friction between the outer ring and the pin.

[0014] In one possible implementation, the number of grooves includes multiple grooves arranged circumferentially along the bearing groove, each groove accommodating one pin. The multiple grooves spaced circumferentially along the bearing groove allow the pin to engage and secure itself more quickly with another groove. When the outer ring of the bearing runs out of space, the pin can be more easily inserted into another groove and secured by the engagement with that groove, limiting the circumferential rotation of the outer ring. The multiple grooves spaced circumferentially along the bearing groove accommodate multiple pins, ensuring that if one pin fails, other available pins are securely connected to another groove.

[0015] In one possible implementation, multiple grooves are arranged at non-equidistant intervals along the circumference of the bearing groove. This facilitates the alignment of the grooves and the non-equidistant reinforcing ribs, ensuring a more stable structure between the reinforcing ribs and the grooves, thereby improving the overall performance of the housing.

[0016] In one possible implementation, the number of the additional grooves includes multiple grooves, which are arranged at equal intervals along the circumference of the outer ring. Multiple additional grooves can form a tighter engagement with the pin, enhancing the stability of the fixed connection between the groove and the pin. Under stress or vibration, the multiple additional grooves can distribute stress, reducing relative movement between the pin and one groove, thereby effectively preventing loosening or detachment and ensuring a safe and reliable engagement. The multiple additional grooves arranged circumferentially along the outer circumference of the outer ring make the engagement of the pin with the other groove easier; the pin can be more easily inserted into the other groove, and the bearing is fixed by engaging with the other groove.

[0017] In one possible implementation, the drive shaft includes a motor shaft of a drive motor or an input shaft of a reducer, and the inner ring of the bearing is used to fix the motor shaft of the drive motor or the input shaft of the reducer. A pin structure is provided between the outer ring of the bearing and the bearing groove of the outer ring of the input shaft with a relatively high rotational speed to prevent the outer ring from running off-center when the high-speed input shaft drives the inner ring of the bearing to rotate at high speed.

[0018] This application also provides an electric vehicle, which includes multiple wheels and a powertrain. The powertrain drives the multiple wheels. The powertrain generates power and transmits the power to the wheels, which then use the power to propel the electric vehicle forward. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of an electric vehicle provided in an embodiment of this application;

[0020] Figure 2 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0021] Figure 3 This is an exploded schematic diagram of a powertrain provided in an embodiment of this application;

[0022] Figure 4 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0023] Figure 5 yes Figure 4 Cross-sectional view at point AA;

[0024] Figure 6 yes Figure 5 Enlarged view of section I;

[0025] Figure 7 This is a schematic diagram of a bearing provided in an embodiment of this application;

[0026] Figure 8 This is a front view of the bearing provided in an embodiment of this application;

[0027] Figure 9 This is a side view of the bearing provided in an embodiment of this application;

[0028] Figure 10 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0029] Figure 11 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0030] Figure 12 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0031] Figure 13 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0032] Figure 14 This is a schematic diagram of a sleeve provided in an embodiment of this application;

[0033] Figure 15 yes Figure 14 Cross-sectional view at point BB;

[0034] Figure 16 This is a schematic diagram of a sleeve and bearing fit provided in an embodiment of this application;

[0035] Figure 17 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0036] Figure 18 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0037] Figure 19 yes Figure 18 Cross-sectional view at point CC;

[0038] Figure 20 This is a schematic diagram of a bearing provided in an embodiment of this application;

[0039] Figure 21 This is a schematic diagram of a powertrain provided in an embodiment of this application;

[0040] Figure 22 This is a schematic diagram of a bearing provided in an embodiment of this application. Detailed Implementation

[0041] The embodiments of this application are described below with reference to the accompanying drawings.

[0042] In the field of electric vehicles, bearings are a critical component of the powertrain system. The powertrain encompasses the motor, reducer, and related transmission mechanisms, which work together to convert electrical energy into driving force for the vehicle. Bearings are widely used in this process due to their ability to support rotating components and reduce friction and wear. In practical applications, bearings are subjected to complex and variable loads and operating environments for extended periods, often resulting in bearing outer ring slippage. Specifically, during bearing operation, the outer ring fails to maintain its stationary state and rotates with the shaft. This outer ring slippage leads to unnecessary relative friction between the bearing outer ring and the bearing groove. This friction not only accelerates the wear of the bearing material but also generates fine metal particles and other foreign matter, increasing the difficulty and cost of cleaning and affecting the service life of the bearing and even the entire powertrain. Furthermore, bearing outer ring slippage can trigger a series of problems related to noise, vibration, and harshness (NVH), resulting in additional vibration and noise within the system.

[0043] In response to the above-mentioned issues, this application provides a powertrain, the housing of which includes at least one bearing groove. One bearing groove is used to receive the outer ring of a bearing, and the inner ring of a bearing is used to fix a drive shaft. The inner circumferential surface of the bearing groove includes a groove for receiving one end of a pin. The outer circumferential surface of the outer ring includes another groove for receiving the other end of a pin. The radial distance between the bottom of the other groove and the inner circumferential surface of the bearing groove is less than the length of a pin, and the circumferential width of the other groove is less than the outer circumference of the outer ring and greater than or equal to the width of the other end of the pin. The powertrain provided in this application embodiment, when the outer ring of the bearing runs off-center, has a pin fixedly connected to another groove on the outer circumferential surface of the outer ring, restricting the relative rotation of the outer ring of the bearing with respect to the bearing groove; and the pin is located between the outer circumferential surface of the outer ring and the inner circumferential surface of the bearing groove, so that the pin on the radial side of the bearing will not interfere with the annular washer installed on the axial side, and there is no need to change the shape and structure of the annular washer for the pin, thereby improving the support and fixing stability of the annular washer for the inner ring of the bearing and facilitating the installation of the bearing and the bearing groove.

[0044] This application provides an electric vehicle 1, please refer to... Figure 1 , Figure 1 This is a schematic diagram of an electric vehicle provided in an embodiment of this application. In this embodiment, the electric vehicle 1 includes a powertrain 10 and a plurality of wheels 20. The powertrain 10 generates power and transmits the power to the wheels 20, which then drive the electric vehicle 1 forward. In one embodiment, the electric vehicle 1 further includes a power battery 30 connected to the powertrain 10. The powertrain 10 receives electrical energy from the power battery 30, converts it into mechanical energy, and then transmits the mechanical energy to the wheels 20.

[0045] In this embodiment, the powertrain 10 is used to drive the two front wheels 210 of the electric vehicle 1, or to drive the two rear wheels 220 of the electric vehicle 1. In one embodiment, there are two powertrains 10, one powertrain 10 is used to drive the two front wheels 210 of the electric vehicle 1, and the other powertrain 10 is used to drive the two rear wheels 220 of the electric vehicle 1.

[0046] In one embodiment, the electric vehicle 1 has at least two wheels 20, such as a two-wheeled, three-wheeled, or four-wheeled vehicle. In another embodiment, the electric vehicle 1 includes a battery electric vehicle (BEV), a hybrid electric vehicle (HEV), and a range-extended electric vehicle (REEV).

[0047] This application provides a powertrain 10, please refer to... Figure 2 , Figure 2 This is a schematic diagram of a powertrain provided in an embodiment of this application. The powertrain 10 includes a drive motor 110 and a reducer 120. The drive motor 110 converts the electrical energy of the power battery 30 into mechanical energy. The motor shaft 111 of the drive motor 110 generates rotational power. The reducer 120 adjusts the power and enables the power to be effectively transmitted to the wheels 20, driving the electric vehicle 1 forward.

[0048] In this embodiment, the reducer 120 includes an input shaft 121, an intermediate shaft 122, and an output shaft 123. The motor shaft 111 is connected to the input shaft 121, and the gears on the input shaft 121 mesh with the gears on the intermediate shaft 122 to transmit power. The intermediate shaft 122 is connected to the output shaft 123 and transmits power to it. The output shaft 123 is connected to the wheels 20 to drive the electric vehicle 1 forward. In one embodiment, the motor shaft 111 of the drive motor 110, the input shaft 121, the intermediate shaft 122, and the output shaft 123 of the reducer 120 are referred to as the drive shafts (111, 121, 122, 123) of the powertrain 10. In one embodiment, the output shaft 123 of the reducer 120 is connected to two wheels 20 via two half-shafts 124. In one embodiment, the reducer 120 includes a single-speed reducer, a two-speed reducer, or a gearbox.

[0049] This application provides a powertrain embodiment; please refer to [link / reference]. Figure 3 , Figure 4 , Figure 5 and Figure 6 , Figure 3 This is an exploded view of a powertrain provided in an embodiment of this application. Figure 4 This is a schematic diagram of a powertrain provided in an embodiment of this application. Figure 5 yes Figure 4 Cross-sectional view at point AA. Figure 6 yes Figure 5 Enlarged view of section I in the middle.

[0050] In this embodiment, the powertrain 10 includes a housing 130, and the housing 130 includes at least one bearing groove 140 located inside the housing 130. The interior of the housing 130 of the powertrain 10 refers to the enclosed or semi-enclosed space surrounded by the walls of the housing 130, used to accommodate and support the various key components of the powertrain 10. In one embodiment, the housing 130 of the powertrain 10 includes a reducer end cover 125, and the cavity enclosed by the reducer end cover 125 and the reducer groove in the housing 130 is used to accommodate the input shaft 121, the intermediate shaft 122, and the output shaft 123.

[0051] In this embodiment, the bearing groove 140 is used to fix a bearing 150. The bearing 150 includes an outer ring 151 and an inner ring 152. The diameter of the outer ring 151 is larger than the diameter of the inner ring 152, and there is a gap between the outer ring 151 and the inner ring 152. In one embodiment, the bearing 150 includes a rolling bearing, specifically a ball bearing, a needle roller bearing, or a tapered roller bearing, etc. This embodiment takes a ball bearing as an example. In one embodiment, the bearing 150 includes a plurality of balls 154 housed within the gap between the outer ring 151 and the inner ring 152. When the powertrain 10 is running, the balls 154 roll within this gap, transmitting power from the inner ring 152 to the outer ring 151. The balls 154 convert the sliding friction between the outer ring 151 and the inner ring 152 into rolling friction, reducing frictional resistance and wear. This allows the bearing 150 to transmit mechanical power more efficiently and reduce energy loss. The balls 154 also provide support and positioning, ensuring stable operation of the bearing 150. In another embodiment, the center of the outer ring 151 coincides with the center of the inner ring 152. The balls 154 are evenly distributed and roll within the raceway between the outer ring 151 and the inner ring 152, allowing for a more even load distribution and ensuring smooth operation of the bearing 150.

[0052] In one embodiment, the bearing groove 140 is used to fix the outer ring 151 of a bearing 150. The inner diameter of the bearing groove 140 is equal to the outer diameter of the outer ring 151 of the bearing 150, to ensure that the outer ring 151 of the bearing 150 can be fixed in the bearing groove 140, and that there is a relative rotational running phenomenon between the outer ring 151 and the bearing groove 140. In another embodiment, the inner diameter of the bearing groove 140 may be larger than the outer diameter of the outer ring 151 to a certain extent, so that the outer ring 151 can be smoothly installed into the bearing groove 140. After the bearing 150 is installed into the bearing groove 140, there is a certain gap between the outer ring 151 and the bearing groove 140. This gap is small to ensure that the inner circumferential surface 141 of the bearing groove 140 can generate a certain amount of friction on the outer ring 151 to prevent the outer ring 151 from rotating relative to the inner circumferential surface 141 of the bearing groove 140. In one embodiment, the center of the bearing groove 140 coincides with the center of the outer ring 151 to ensure that after the bearing 150 is installed in the bearing groove 140, the bearing 150 is subjected to more uniform force and can operate smoothly.

[0053] In this embodiment, the inner ring 152 of the bearing 150 is used to fix the drive shaft (111, 121, 122, 123). In one embodiment, the drive shaft includes at least one of a motor shaft 111, an input shaft 121, an intermediate shaft 122, and an output shaft 123. In this embodiment, taking the input shaft 121 as an example, the central axis of the inner ring 152 coincides with the central axis of the input shaft 121 to ensure that when power is transmitted from the input shaft 121 to the inner ring 152, the power does not deflect or become interrupted during transmission, thus maintaining the continuity and stability of the transmission.

[0054] In one embodiment, the inner peripheral surface 141 of the bearing groove 140 includes a groove 142, the groove opening 1421 of the groove 142 faces the outer peripheral surface 1511 of the outer ring 151 of the bearing 150, and the depth of the groove 142 is less than the thickness of the groove wall of the bearing groove 140, to ensure the structural strength of the housing 130 that forms the groove 142.

[0055] In one embodiment, please continue reading Figure 6 The groove 142 is used to accommodate one end of a pin 170, one end of which can be inserted into the groove 142, and the other end of which protrudes from the inner circumferential surface 141 of the bearing groove 140.

[0056] In one embodiment, please refer to Figure 7 , Figure 8 and Figure 9 , Figure 7 This is a schematic diagram of a bearing provided in an embodiment of this application. Figure 8 This is a front view of the bearing provided in an embodiment of this application. Figure 9 This is a side view of the bearing provided in the embodiment of this application. The outer peripheral surface 1511 of the outer ring 151 includes another groove 153. The groove 1531 of the other groove 153 faces the inner peripheral surface 141 of the bearing groove 140. The other groove 153 is used to accommodate the other end of the pin 170.

[0057] In one embodiment, when the outer ring 151 of the bearing 150 runs relative to the bearing groove 140, the outer ring 151 rotates circumferentially along the outer peripheral surface 1511 of the bearing 150. When the groove opening 1421 of the groove 142 is aligned with the groove opening 1531 of another groove 153, the pin 170 is displaced along the bottom wall 1423 of the groove 142 towards the groove opening 1421. The other end of the pin 170 falls into the other groove 153 and abuts against the circumferential sidewall of the other groove 153, ensuring that the pin 170 can hold the outer ring 151 of the bearing 150, so that the outer ring 151 does not rotate circumferentially along the outer peripheral surface 1511 of the bearing 150. After the other end of the pin 170 falls into another groove 153, one end of the pin 170 remains in the groove 142. The pin 170 achieves circumferential positioning between the bearing groove 140 and the outer ring 151, preventing the outer ring 151 from running out of its original circle.

[0058] In one embodiment, the pin 170 includes an elastic pin. The pin 170 can be initially fixed in the groove 142. When the bearing 150 is installed, the elastic pin can be squeezed. When the outer ring 151 of the bearing 150 runs off-center, the elastic pin can fall into another groove 153 under elastic action for locking and limiting. In another embodiment, the pin 170 can be initially installed in the groove 142. The length of the pin 170 is less than the depth of the groove 142. The groove 142 is located in the positive direction of the bearing groove 140. When the bearing 150 is installed, the pin 170 is squeezed until it is completely located in the groove 142. When the outer ring 151 of the bearing 150 runs off-center, and the groove 142 and another groove 153 are opposite each other, the pin 170 can fall into the other groove 153 under gravity, realizing circumferential limiting between the bearing groove 140 and the outer ring 151, and preventing the outer ring 151 from running off-center.

[0059] In one embodiment, the radial distance between the bottom 1532 of another groove 153 and the inner circumferential surface 141 of the bearing groove 140 along the outer ring 151 is less than the length of a pin 170. The pin 170 can effectively fix the groove 142 and the other groove 153, preventing them from loosening or separating due to external forces, thereby increasing the stability and reliability of the connection.

[0060] In one embodiment, the length of the groove 1531 of another groove 153 along the circumferential direction of the outer peripheral surface 1511 is greater than or equal to the width of the other end of a pin 170, so as to ensure that the other end of the pin 170 can enter the other groove 153 and limit the outer ring 151 of the bearing 150 from running.

[0061] In one embodiment, the length of the slot 1531 of the other groove 153 along the circumferential direction of the outer peripheral surface 1511 is less than the circumference of the outer peripheral surface 1511. The other groove 153 forms two sidewalls along the circumferential direction of the outer peripheral surface 1511 to ensure that the other groove 153 and the pin 170 can form an effective engagement point. One end of the pin 170 is engaged in the groove 142, and the other end of the pin 170 is engaged in the other groove 153. The outer ring 151 of the bearing 150 is restricted in displacement by the pin 170, thus restricting the running of the outer ring 151.

[0062] In the embodiments of this application, please refer to Figure 10 , Figure 10 This is a schematic diagram of a powertrain provided in an embodiment of this application. When the powertrain 10 is running, the inner ring 152 of the bearing 150 rotates with the drive shaft, while the outer ring 151 of the bearing 150 remains stationary within the bearing groove 140. One end of the pin 170 is accommodated within the groove 142. Please continue reading. Figure 6 When the load on the powertrain 10 is too high, the outer ring 151 of the bearing 150 rotates with the inner ring 152. The outer ring 151 rotates until the groove 1531 of another groove 153 is opposite to the groove 1421 of the bearing groove 142. The pin 170 can fall into the other groove 153 and be connected and fixed to the other groove 153. One end of the pin 170 is accommodated in the groove 142. The pin 170 is simultaneously stuck in the groove 142 and the other groove 153, thereby limiting the circumferential displacement of the outer circumferential surface 1511 of the outer ring 151 where the other groove 153 is located, thus preventing the outer ring 151 from running. Furthermore, the groove 142 is provided on the inner circumferential surface 141 on the radial side of the bearing groove 140, and one end of the pin 170 is accommodated in the groove 142. The pin 170 engages the outer ring 151 and the bearing groove 140 on the radial side of the bearing 150, and will not interfere with the position of the annular gasket or other structures on the axial side of the bearing groove 140. The annular gasket does not need to be specifically modified in shape, thereby improving the stability of the support and fixation of the bearing 150 on the axial side.

[0063] Please see Figure 11 , Figure 11 This is a schematic diagram of a powertrain provided in an embodiment of this application.

[0064] In one embodiment, a groove 142 is used to accommodate an elastic member 171, the two ends of which are respectively connected to the inner wall of the groove 142 and one end of a pin 170. The length of the elastic member 171 along the radial direction of a bearing groove 140 is less than the length of the groove 142.

[0065] In this embodiment, one end of the elastic member 171 is connected to the side wall 1422 or bottom wall 1423 of the groove 142, and the other end of the elastic member 171 is connected to the pin 170. In one embodiment, the side wall 1422 or bottom wall 1423 of the groove 142 and one end of the elastic member 171 can be fixedly connected by adhesive, welding or bolts, or it can be pressed and fixed in the groove 142 by the side wall of the groove 142, or it can be accommodated in the groove 142 and abut against the bottom wall of the groove 142 in a compressed state. In one embodiment, the elastic member 171 includes a spring.

[0066] In one embodiment, the length of the elastic element 171 along the radial direction of a bearing groove 140 is less than the length of the groove 142 along the radial direction of a bearing groove 140. The elastic element 171 is completely accommodated in the groove 142 and does not protrude from the groove opening 1421 of the groove 142. This ensures that the elastic element 171 does not directly contact the outer ring 151. Instead, it is engaged with the outer ring 151 by a pin 170 fixed at one end of the elastic element 171. This prevents the elastic element 171 from being deformed by compression, which would prevent the pin 170 from being unable to spring into another groove 153. It also improves the engagement strength of the pin 170 with the outer ring 151 when it is not running.

[0067] In one embodiment, please refer to Figure 12 , Figure 12 This is a schematic diagram of a powertrain provided in an embodiment of this application. When installing the bearing 150, it is not necessary to pre-align the other groove 153 on the outer ring 151 and the groove 142 on the bearing groove 140. The outer circumferential surface 1511 of the outer ring 151 exerts a compressive force on the elastic element 171 by pressing the pin 170. The elastic element 171 undergoes compression deformation, shortening its length. This compression causes the pin 170 to move along the groove opening 1421 of the groove 142 towards the bottom wall 1423 of the groove 142, allowing the pin 170 to move into the groove 142 without interfering with the installation of the bearing 150. When the outer ring 151 runs out of circumference, it rotates relative to the bearing groove 140, gradually rotating until the other groove 153 on the outer ring 151 and the groove 142 on the bearing groove 140 are aligned. For details, please refer to [reference needed]. Figure 11 As shown, the pressure applied by the outer ring 151 to the elastic element 171 decreases or disappears. Under the action of the elastic restoring force, the elastic element 171 generates a pushing force on the pin 170. The elastic restoring force of the elastic element 171 drives the pin 170 to move along the bottom wall 1423 of the groove 142 towards the slot 1421 of the groove 142 and drives the pin 170 to extend out of the groove 142 and be inserted into another groove 153, preventing the outer ring 151 from running further.

[0068] In one embodiment, the sum of the free-state length of the elastic element 171 and the length of the pin 170 is greater than the radial distance between the bottom 144 of the groove 142 and the bottom 1532 of the other groove 153. When the elastic element 171 pushes the pin 170 to contact the bottom 1532 of the other groove 153, the elastic element 171 remains in a compressed state under the pressure of the groove 142 and the pin 170. This helps to increase the stability of the pin 170 in the groove 142 and the other groove 153, and prevents it from detaching from the other groove 153 due to gravity or other shaking, thereby improving the stability of the anti-runaway effect of the outer ring 151.

[0069] In this embodiment, the elastic element 171 is an elastic structure. When installing the bearing 150, it is not necessary to deliberately align the other groove 153 of the outer ring 151 with the groove 142 of the bearing groove 140, thereby reducing the installation difficulty of the bearing 150, improving the installation efficiency between the bearing 150 and the bearing groove 140, and improving the installation efficiency of the powertrain 10.

[0070] In the embodiments of this application, please refer to Figure 13 , Figure 14 , Figure 15 and Figure 16 , Figure 13 This is a schematic diagram of a powertrain provided in an embodiment of this application. Figure 14 This is a schematic diagram of a sleeve provided in an embodiment of this application. Figure 15 yes Figure 14 Cross-sectional view at point BB. Figure 16 This is a schematic diagram of a sleeve and bearing assembly provided in an embodiment of this application. A groove 142 is used to accommodate a sleeve 180. The width of the groove 142 along at least one direction of the bearing groove 140, both circumferential and axial, is equal to the width of the sleeve 180. The radial length of the sleeve 180 along the bearing groove 140 is less than or equal to the depth of the groove 142. The inner cavity 181 of the sleeve 180 is used to accommodate an elastic element 171. The inner wall of the sleeve 180 is used to fix one end of the elastic element 171.

[0071] In one embodiment, the groove 142 includes a cylindrical groove, and the sleeve 180 includes a cylindrical sleeve. The width of the groove 142 and the width of the sleeve 180 are equal in both the circumferential and axial directions of the bearing groove 140, and the inner diameter of the groove 142 and the outer diameter of the sleeve 180 are equal. The sleeve 180 is inserted into the groove 142, and the tight contact between the groove 142 and the sleeve 180 generates significant friction. During the assembly of the powertrain 10, if rotation or inversion occurs, the sleeve 180 is less likely to fall out of the groove 142 after insertion.

[0072] In one embodiment, the inner cavity 181 of the sleeve 180 is used to accommodate the elastic element 171, and the inner wall of the sleeve 180 is used to fix the elastic element 171. One end of the elastic element 171 is connected to the pin 170, and the other end of the elastic element 171 is connected to the inner wall of the sleeve 180, which includes an inner bottom wall 1821 and an inner side wall 1822. In one embodiment, the sleeve 180, pin 170, and elastic element 171 are pre-fixed as an assembly, making it more convenient to assemble the sleeve 180, elastic element 171, and pin 170 externally, simplifying the installation steps and reducing the workload during on-site installation. The insertion method of the sleeve 180 makes the installation process more intuitive and reduces the installation difficulty. The assembly is inserted into the groove 142 as a whole, which can ensure the accurate position of the pin 170 and the elastic element 171 and avoid deviations during installation. The interference fit between the groove 142 and the sleeve 180 provides additional positioning stability, ensuring that the assembly will not move or misalign during installation. Furthermore, the elastic element 171 and the pin 170 can be pre-installed in the sleeve 180, and the assembly of the pin 170 and the groove 142 can be achieved simply by inserting the sleeve 180 equipped with the elastic element 171 and the pin into the groove 142, thereby improving the assembly efficiency of the powertrain 10.

[0073] In one embodiment, the radial length of the sleeve 180 along the bearing groove 140 is less than or equal to the depth of the groove 142. The sleeve 180 can be completely accommodated in the groove 142, does not protrude from the groove 142, and will not contact the outer peripheral surface 1511 of the bearing 150 and generate unnecessary friction.

[0074] In the embodiments of this application, please continue to refer to Figure 13 and Figure 15 The inner cavity 181 of a sleeve 180 has a radial depth greater than the length of an elastic element 171, and a width greater than or equal to the width of one end of a pin 170 in at least one direction of the bearing groove 140, for receiving one end of a pin 170.

[0075] In one embodiment, the radial length of the inner cavity 181 of the sleeve 180 along the bearing groove 140 is greater than the radial length of the elastic member 171 along the bearing groove 140, and the elastic member 171 is completely accommodated within the inner cavity 181 of the sleeve 180. In another embodiment, the width of the inner cavity 181 of the sleeve 180 along at least one direction of the bearing groove 140, both circumferential and axial, is greater than or equal to the width of one end of the pin 170, to ensure that the inner cavity 181 of the sleeve 180 has sufficient space to accommodate at least one end of the pin 170. In another embodiment, when the sleeve 180 is inserted into the groove 142, the pin 170 is accommodated within the inner cavity 181 of the sleeve 180, and the pin 170 is not stuck outside the groove 142 of the bearing groove 140.

[0076] In the embodiments of this application, please refer to Figure 17 , Figure 17 This is a schematic diagram of a powertrain provided in an embodiment of this application. A groove 142 along the radial direction of a bearing groove 140 includes two inner sidewalls 1422, wherein the width of one inner sidewall 1424 along at least one direction of the bearing groove 140, both circumferential and axial, is greater than the width of an elastic member 171, less than the width of the other inner sidewall 1425, and less than the width of a pin 170. A slot 1421 for a groove 142 is located on both sides of the other inner sidewall 1425 along the radial direction of a bearing groove 140. The width of the other inner sidewall 1425 along at least one direction of the bearing groove 140, both circumferential and axial, is greater than or equal to the width of a pin 170, and the length along the radial direction of a bearing groove 140 is greater than or equal to the length of a pin 170.

[0077] In one embodiment, the groove 142 includes an inner sidewall 1422, which can be divided into two segments along the radial direction of the bearing groove 140. The average width of one segment of the inner sidewall 1424 along at least one direction of the bearing groove 140, both circumferential and axial, is less than the average width of the other segment of the inner sidewall 1425.

[0078] In one embodiment, the minimum width of the inner sidewall 1424 along at least one direction of the bearing groove 140 (circumferential and axial) is greater than the maximum width of the elastic member 171, and the maximum width of the inner sidewall 1424 along at least one direction of the bearing groove 140 (circumferential and axial) is less than the maximum width of the pin 170. In another embodiment, the partial groove 142 formed by the inner sidewall 1424 is capable of accommodating at least a portion of the elastic member 171 and locking the pin 170 outside the inner sidewall 1424.

[0079] In one embodiment, the other inner sidewall 1425 has a groove opening 1421 and an inner sidewall 1424 at its radial ends along the bearing groove 140, respectively. In another embodiment, the minimum width of the other inner sidewall 1425 along at least one direction of the bearing groove 140, both circumferential and axial, is greater than or equal to the maximum width of the pin 170, and the length of the other inner sidewall 1425 along the radial direction of a bearing groove 140 is greater than or equal to the length of a pin 170. In one embodiment, the groove 142 formed by the other inner sidewall 1425 can completely accommodate the pin 170. The pin 170 can be fully retracted into the groove 142 formed by the other inner sidewall 1425, preventing the pin from being stuck in a deeper position in the groove 142 and unable to extend into the other groove 153. The other inner sidewall 1425 can also limit the elastic member 171 to a certain extent, preventing the elastic member 171 from bending laterally after being compressed, and preventing the elastic member 171 from deforming and causing a large frictional force between the pin 170 and the sidewall 1422 of the groove 142, ensuring that the pin 170 can be smoothly ejected from the groove 142 into the other groove 153.

[0080] In one embodiment, the width of the inner sidewall 1422 of the groove 142 gradually decreases along at least one direction of the circumferential and axial directions of the groove opening 1421 of the bearing groove 140 toward the bottom wall 1423, forming a flared shape that is smaller inside and larger outside.

[0081] In the embodiments of this application, please refer to Figure 18 and Figure 19 , Figure 18 This is a schematic diagram of a powertrain provided in an embodiment of this application. Figure 19 yes Figure 18 A cross-section at CC. The outer peripheral surface of the bearing groove 140 includes a reinforcing rib 190, a groove 1421 of a recess 142 for the groove 142 to be located on opposite sides of the circumferential sidewall of the bearing groove 140 along the radial direction of the bearing groove 140, the radial depth of the bearing groove 140 being less than the radial distance between the inner peripheral surface 141 of the bearing groove 140 and the outer wall of the reinforcing rib 190.

[0082] In one embodiment, the circumferential sidewall of the bearing groove 140 is provided with groove openings 1421 and reinforcing ribs 190 on opposite sides of the bearing groove 140 along the radial direction. The depth of the groove 142 along the radial direction of the bearing groove 140 is less than the radial distance between the inner circumferential surface 141 of the bearing groove 140 and the outer wall 191 of the reinforcing rib 190. In one embodiment, the reinforcing rib 190 enhances the strength and rigidity of the housing in which the bearing groove 140 is located. The reinforcing rib 190 can effectively improve the structural strength and rigidity of the bearing groove 140 and the housing 130. The groove 142 is provided on the inner side of the bearing groove 140 opposite to the original reinforcing rib 190, which can prevent the setting of the groove 142 from causing a significant reduction in the structural strength of the bearing groove 140 and the housing 130.

[0083] In the embodiments of this application, please continue to refer to Figure 3 , Figure 13 , Figure 14 and Figure 16 The other end of a pin 170 includes a ball head 172, the outer diameter of which is less than or equal to the inner diameter of the slot 1421 of a groove 142, and another groove 153 includes an arcuate sidewall, the inner diameter of which is equal to the outer diameter of the ball head 172.

[0084] In one embodiment, the pin 170 includes a ball head 172, one end of which is fixedly connected to the elastic element 171. In another embodiment, the opening 1421 of a groove 142 is circular, and the outer diameter of the ball head 172 is less than or equal to the inner diameter of the opening 1421 of the groove 142, to ensure that the ball head 172 has sufficient space within the groove 142 for smooth expansion and contraction. If the diameter of the opening 1421 of the groove 142 is too small, it will restrict the range of motion of the ball head 172, and may even cause jamming, affecting the effect of fixing the outer ring 151 of the bearing 150. In another embodiment, the shape of the opening 1421 of the groove 142 is not constrained. The shape of the opening 1421 can be triangular, quadrilateral, trapezoidal, etc. When the widest part of the ball head 172 is parallel to the plane where the opening 1421 is located, there is a gap between the ball head 172 and the opening 1421, allowing the ball head 172 to have sufficient space within the groove 142 for smooth expansion and contraction.

[0085] In one embodiment, another groove 153 includes an arcuate sidewall with an inner diameter equal to the outer diameter of a ball head 172. The other end of the ball head 172 is fixedly connected to the other groove 153, defining the rotation of the outer ring 151 of the bearing 150 relative to the bearing groove 140. In one embodiment, the ball head 172 can be more easily inserted into the mating groove 153, while the spherical surface of the ball head 172 can fit tightly against the arcuate sidewall of the other groove 153, providing a stable connection. The arcuate sidewall ensures that the ball head 172 will not loosen or fall out after insertion, and the friction between the spherical surface of the ball head 172 and the arcuate sidewall also prevents the ball head 172 from disengaging from the other groove 153. In one embodiment, the ball head 172 makes the assembly process simpler and faster, requiring no complex tools or skills. The tight fit between the spherical surface of the ball head 172 and the arcuate sidewall ensures the stability of the connection, preventing the ball head 172 from loosening or falling out due to vibration or impact. In one embodiment, the ball head 172 is made of any one of carbon steel, stainless steel, aluminum alloy, and copper.

[0086] In the embodiments of this application, please continue to refer to Figure 13 , Figure 15 and Figure 16 Along the radial direction of a bearing groove 140, the length of a portion of a ball head 172 protruding from a groove 142 is greater than or equal to the radius of the ball head 172, and the depth of another groove 153 is greater than or equal to the radius of the ball head 172.

[0087] In one embodiment, at least half of a ball head 172 protrudes from the slot 1421 of a groove 142, and the arcuate sidewall of another groove 153 is an arc segment with an angle greater than or equal to 1 / 2.

[0088] In one embodiment, when the depth of the other groove 153 is greater than or equal to the radius of the ball head 172 or the radius of the arcuate sidewall, the contact area between the ball head 172 and the other groove 153 is larger, which helps to enhance the stability of the fixed connection between the ball head 172 and the other groove 153; and the inner diameter of the groove opening 1531 of the other groove 153 is less than or equal to the radius of the ball head 172 or the radius of the arcuate sidewall, which helps to more firmly lock the ball head 172 in the arcuate sidewall, and can prevent the ball head 172 from easily falling off or loosening when subjected to external force, thereby improving the reliability and durability of the connection.

[0089] In one embodiment, the tight connection between the ball head 172 and the arcuate sidewall enhances the stability of the bearing 150, making it smoother and vibration-free during operation; the larger contact area between the ball head 172 and the arcuate sidewall allows the bearing 150 to withstand greater loads, thereby improving its load-bearing capacity; the tight connection between the ball head 172 and the arcuate sidewall and the stable operation can reduce the wear and failure rate of the bearing 150, thereby extending its service life.

[0090] In the embodiments of this application, please continue to refer to Figure 8 , Figure 16 and Figure 17 The outer peripheral surface 1511 of the outer ring 151 includes a chamfer 1512 or a fillet 1513. The chamfer 1512 or the fillet 1513 is located at one axial end of the outer peripheral surface 1511 of the outer ring 151 and is used to surround one end face of the outer ring 151 along the circumference of the outer ring 151. The length of the chamfer 1512 or the fillet 1513 along the axial direction of the outer ring 151 is greater than or equal to the length of the portion of the pin 170 that protrudes from a groove 142.

[0091] In one embodiment, the chamfer 1512 and fillet 1513 make the axial edges of the outer ring 151 smoother, making it easier to contact the pin 170. This facilitates contact with the pin 170 during bearing 150 installation, pressing the pin 170 into the groove 142 and preventing the pin 170 from interfering with the installation of the bearing 150, thus reducing installation difficulty. In another embodiment, one end of the pin 170 is connected to the elastic element 171. Under the pressure of the chamfer 1512 and fillet 1513 at both axial ends of the outer ring 151, the pin 170 causes the elastic element 171 to deform, making it easier to adapt to the installation process. The design of the chamfer 1512 and fillet 1513 enhances the adaptability of the pin 170, making it less susceptible to damage during installation.

[0092] In one embodiment, the chamfer 1512 and fillet 1513 can reduce the frictional area between the axial ends of the outer ring 151 and the pin 170, reducing the heat and wear generated by friction, which helps to extend the service life of the bearing 150 and the pin 170, and reduce metal debris generated by friction. In another embodiment, the chamfer 1512 and fillet 1513 help to optimize the contact state between the axial ends of the outer ring 151 and the pin 170, ensuring that the bearing 150 can uniformly distribute stress on the contact surface when bearing a load, avoiding wear and metal debris caused by excessive local stress.

[0093] In one embodiment, the outer peripheral surface 1511 of the outer ring 151 includes two chamfers 1512, two fillets 1513, or one chamfer 1512 and one fillet 1513. The two chamfers 1512, two fillets 1513, or one chamfer 1512 and one fillet 1513 are located at both axial ends of the outer peripheral surface 1511 of the outer ring 151, and are used to surround the two end faces of the outer ring 151 circumferentially. Providing chamfers 1512 and fillets 1513 at both axial ends of the outer peripheral surface 1511 of the outer ring 151 helps to more effectively reduce stress concentration that may occur during the operation of the bearing 150, and further enhances the structural strength of the outer ring 151 of the bearing 150, making the bearing 150 more able to withstand external loads and impacts. In one embodiment, chamfered corners 1512 and fillets 1513 are provided at both ends of the outer peripheral surface 1511 of the outer ring 151, which is beneficial to the assembly of the bearing 150. When the bearing 150 is installed into the bearing groove 140, there is no need to distinguish between the front and back sides, which helps to improve the installation efficiency.

[0094] In the embodiments of this application, please continue to refer to Figure 8 and Figure 10 Along the axial direction of one bearing groove 140, another groove 153 is used to penetrate the end faces of both ends of the outer ring 151.

[0095] In one embodiment, another groove 153 penetrates the end faces of the outer ring 151 of the bearing 150 along both ends of the bearing groove 140 axially, making it easier for the pin 170 to align and insert into the other groove 153. The other groove 153 penetrating the end face increases the contact area between the engaging components, thereby improving the strength and stability of the connection. In one embodiment, when disassembling or replacing the bearing 150, the pin 170 can slide out more easily from the other groove 153 penetrating both ends of the outer ring 151 without being subjected to excessive friction or compression. The bearing 150 can engage with the pin 170 at any position in the axial direction, reducing the risk of damage to the bearing 150 or the pin 170 during disassembly and facilitating blind disassembly of the bearing 150.

[0096] In the embodiments of this application, please refer to Figure 20 , Figure 20 This is a schematic diagram of a bearing provided in an embodiment of this application. Along the axial direction of one bearing groove 140, the length of another groove 153 is less than the length of the outer ring 151. Along the axial direction of one bearing groove 140, the other groove 153 is used to penetrate one end face of the outer ring 151 and to connect the gap between the outer ring 151 and the bottom 144 of the bearing groove 140.

[0097] In one embodiment, the length of another groove 153 along the axial direction of a bearing 150 is less than the length of the outer ring 151 along the axial direction of a bearing 150. At least one end of the bearing 150 is not penetrated by the other groove 153, forming a shielding enclosure structure that helps prevent external substances from entering the bearing groove 140 and also restricts the escape of internal substances, such as debris generated by sliding friction between the outer ring 151 of the bearing 150 and the pin 170.

[0098] In one embodiment, another groove 153 penetrates one end face of the outer ring 151 of the bearing 150 and connects the gap between the outer ring 151 and the bottom 144 of the bearing groove 140, which helps the pin 170 in the other groove 153 to slide out more smoothly during disassembly without encountering jamming or obstruction.

[0099] In the embodiments of this application, please continue to refer to Figure 19 The number of grooves 142 includes a plurality of grooves 142 arranged circumferentially along a bearing groove 140, and each groove 142 is used to accommodate a pin 170.

[0100] In one embodiment, a plurality of grooves 142 arranged circumferentially along the bearing groove 140 allow the pin 170 to engage and fix with another groove 153 more quickly. When the outer ring 151 of the bearing 150 runs out of rotation, the pin 170 can be more easily inserted into another groove 153 and fixed by engaging with another groove 153, thus restricting the circumferential rotation of the outer ring 151. In another embodiment, a plurality of grooves 142 arranged circumferentially along the bearing groove 140 accommodate a plurality of pins 170. When one pin 170 fails, other valid pins 170 are fixedly connected to another groove 153.

[0101] In the embodiments of this application, please continue to refer to Figure 19 Multiple grooves 142 are arranged at non-equidistant intervals along the circumference of the bearing groove 140.

[0102] In one embodiment, the groove 142 is not equidistantly arranged on the inner circumferential surface 141 of the bearing groove 140, which is conducive to the alignment of the groove and the non-equidistant reinforcing rib 190, ensuring that the structure between the reinforcing rib 190 and the groove 142 is more stable, thereby improving the overall performance of the housing 130.

[0103] In the embodiments of this application, please refer to Figure 21 and Figure 22 , Figure 21 This is a schematic diagram of a powertrain provided in an embodiment of this application. Figure 22This is a schematic diagram of a bearing provided in an embodiment of this application. The number of additional grooves 153 includes a plurality of grooves 153, which are arranged at equal intervals along the circumference of the outer ring 151.

[0104] In one embodiment, a plurality of additional grooves 153 are arranged at equal intervals along the circumferential surface 1511 of the outer ring 151 of the bearing 150. These additional grooves 153 can form a tighter engagement with the pin 170, enhancing the stability of the fixed connection between the additional grooves 153 and the pin 170. Under stress or vibration, the multiple additional grooves 153 can disperse stress, reducing the relative movement between the pin 170 and one groove 153, thereby effectively preventing loosening or detachment and ensuring a safe and reliable connection. In another embodiment, the multiple additional grooves 153 arranged circumferentially along the outer circumferential surface 1511 of the outer ring 151 make the engagement of the pin 170 with the additional groove 153 more convenient. The pin 170 can be more easily inserted into the additional groove 153 and the bearing 150 is fixed by engaging with the additional groove 153.

[0105] In one embodiment, see Figure 3 As shown, a drive shaft includes a motor shaft 111 for a drive motor or an input shaft 121 for a reducer. An inner ring 152 of a bearing 150 is used to fix the motor shaft 111 for the drive motor or the input shaft 121 for the reducer. A pin 170 structure is provided between the outer ring 151 of the bearing 150 and the bearing groove 140 of the outer ring of the input shaft 121, which rotates at a relatively high speed, to prevent the outer ring 151 from running out of its ring when the inner ring 152 of the bearing 150 rotates at high speed due to the high speed of the input shaft 121.

[0106] The above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be included within the protection scope of this application.

Claims

1. A powertrain assembly for preventing bearing slippage, characterized in that, The powertrain housing includes at least one bearing groove for receiving an outer ring of a bearing, and an inner ring of the bearing for securing a drive shaft, wherein: The inner circumferential surface of the bearing groove includes a groove for receiving one end of a pin, and the outer circumferential surface of the outer ring includes another groove for receiving the other end of the pin. The radial distance between the bottom of the other groove and the inner circumferential surface of the bearing groove is less than the length of the pin, and the circumferential width of the other groove is less than the outer circumference of the outer ring and greater than or equal to the width of the other end of the pin.

2. The powertrain according to claim 1, characterized in that, The groove is used to accommodate an elastic element, the two ends of which are respectively connected to the inner wall of the groove and one end of the pin, and the radial length of the elastic element along the bearing groove is less than the length of the groove.

3. The powertrain according to claim 2, characterized in that, The groove is used to accommodate a sleeve, the width of the groove is equal to the width of the sleeve in at least one direction of the bearing groove (circumferential and axial), the radial length of the sleeve along the bearing groove is less than or equal to the depth of the groove, the inner cavity of the sleeve is used to accommodate the elastic element, and the inner wall of the sleeve is used to fix one end of the elastic element.

4. The powertrain according to claim 3, characterized in that, The inner cavity of the sleeve is used to accommodate one end of the pin, and the depth of the inner cavity of the sleeve along the radial direction of the bearing groove is greater than the length of the elastic element, and the width along at least one direction of the bearing groove, both circumferential and axial, is greater than or equal to the width of one end of the pin.

5. The powertrain according to any one of claims 2-4, characterized in that, The groove along the radial direction of the bearing groove includes two inner sidewalls, wherein the width of one inner sidewall along at least one direction of the bearing groove (circumferential and axial) is greater than the width of the elastic element, less than the width of the other inner sidewall, and less than the width of the pin. The inner sidewall is used to connect with the groove opening of the groove on both sides of the other inner sidewall along the radial direction of the bearing groove. The width of the other inner sidewall along at least one direction of the bearing groove (circumferential and axial) is greater than or equal to the width of the pin, and the length along the radial direction of the bearing groove is greater than or equal to the length of the pin.

6. The powertrain according to any one of claims 1-4, characterized in that, The outer peripheral surface of the bearing groove includes a reinforcing rib. The groove opening is located on opposite sides of the reinforcing rib on the circumferential sidewall of the bearing groove along the radial direction of the bearing groove. The depth of the groove along the radial direction of the bearing groove is less than the radial distance between the inner peripheral surface of the bearing groove and the outer wall of the reinforcing rib.

7. The powertrain according to any one of claims 1-4, characterized in that, The other end of one of the pins includes a ball head, the outer diameter of which is less than or equal to the inner diameter of the groove opening of one of the grooves, and the other groove includes an arcuate sidewall, the inner diameter of which is equal to the outer diameter of the ball head.

8. The powertrain according to claim 7, characterized in that, Along the radial direction of one bearing groove, the length of the portion of the ball head protruding from the groove is greater than or equal to the radius of the ball head, and the depth of the other groove is greater than or equal to the radius of the ball head.

9. The powertrain according to claim 7, characterized in that, The outer circumferential surface of the outer ring includes a chamfer or a fillet, the chamfer or the fillet is located at one axial end of the outer circumferential surface of the outer ring, the chamfer or the fillet is used to surround one end face of the outer ring along the circumferential direction of the outer ring, and the length of the chamfer or the fillet along the axial direction of the outer ring is greater than or equal to the length of the portion of the pin protruding from the groove.

10. The powertrain according to any one of claims 1-4, characterized in that, Along the axial direction of one bearing groove, the other groove is used to penetrate both end faces of the outer ring.

11. The powertrain according to any one of claims 1-4, characterized in that, The length of the other groove along the axial direction of the one bearing groove is less than the length of the outer ring. The other groove along the axial direction of the one bearing groove is used to penetrate one end face of the outer ring and to connect the gap between the bottom of the outer ring and the bearing groove.

12. The powertrain according to any one of claims 1-4, characterized in that, The number of the grooves includes a plurality of grooves, which are arranged at circumferential intervals along the bearing groove, and each groove is used to accommodate one pin.

13. The powertrain according to claim 12, characterized in that, Multiple grooves are arranged at non-equidistant intervals along the circumference of the bearing groove.

14. The powertrain according to any one of claims 1-4, characterized in that, The number of the other grooves includes a plurality of grooves, which are arranged at equal intervals along the circumference of the outer ring.

15. The powertrain according to any one of claims 1-4, characterized in that, The drive shaft includes the motor shaft of a drive motor or the input shaft of a reducer, and the inner ring of the bearing is used to fix the motor shaft of the drive motor or the input shaft of the reducer.

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

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