Eccentric bearing in steering system

Abstract

The utility model belongs to the technical field of steering systems, and particularly relates to an eccentric bearing in a steering system. The inner side of the eccentric bearing outer ring is provided with a first roller path; the rollers are assembled in the first roller path of the eccentric bearing outer ring, and the multiple rollers are evenly distributed in the circumferential direction of the first roller path at intervals; the sealing ring is arranged in the middle of the eccentric bearing outer ring, and the axis where the first roller path and the sealing ring are located does not coincide with the axis of the eccentric bearing outer ring; the locking block is mounted in the first roller path and is positioned between two of the rollers; and the through groove is formed in the locking block. The utility model provides an eccentric bearing in a steering system, which can effectively adjust the transmission clearance of a sector gear in the steering system.

Description

Technical Field

[0001] This utility model belongs to the technical field of steering systems, and in particular relates to an eccentric bearing in a steering system. Background Technology

[0002] In the modern automotive industry, the steering system, as a core component of vehicle control, directly affects driving safety and the driving experience. Recirculating ball sector gear transmissions are widely used in automotive steering systems due to their unique performance advantages. Their core function is to efficiently convert the rotational motion of the steering wheel into linear steering force for the wheels, and through hydraulic or electric power assist, significantly reduce the driver's workload. For example, in terms of transmission performance, recirculating ball sector gears can achieve high torque transmission between intersecting shafts, with a transmission ratio reaching 16000 Nm, which greatly improves steering precision; in terms of space utilization, their compact structural design meets the requirements of complex interior space layouts in automobiles.

[0003] However, this transmission system has significant technical drawbacks. Insufficient installation contact can lead to two main failure modes. The first is localized point or line contact, where only a portion of the tooth surface engages, resulting in excessive stress concentration, significantly increasing the risk of thermal adhesion, and severely impacting the stability and lifespan of the transmission system. The second is abnormal backlash. In autonomous driving applications, installation misalignment can cause uneven normal backlash. Insufficient backlash leads to a sharp increase in rotational torque, increasing system operating resistance; excessive backlash results in a significant increase in backlash error, severely reducing steering accuracy and potentially failing to meet the stringent steering precision requirements of autonomous driving.

[0004] Currently, existing technologies for controlling contact quality in the industry have significant limitations. Taking rigid positioning assembly as an example, this method heavily relies on high-precision machining of the housing holes, requiring zero transmission backlash. This not only makes installation extremely difficult, but the high-precision machining requirements are often difficult to achieve in actual production. Furthermore, the thermal deformation of the housing during operation can cause the installation reference to drift, and it also cannot compensate for the elastic deformation of the steering shaft during operation, making it difficult to guarantee the long-term stable performance of the steering system. Utility Model Content

[0005] The purpose of this invention is to address the aforementioned technical problems by providing an eccentric bearing in a steering system that can effectively adjust the clearance of the sector gear transmission in the steering system.

[0006] In view of this, the present invention provides an eccentric bearing for a steering system, comprising:

[0007] The outer ring of the eccentric bearing has a first raceway on its inner side;

[0008] Rollers are assembled in the first raceway of the outer ring of the eccentric bearing. There are multiple rollers, which are evenly spaced along the circumferential direction of the first raceway.

[0009] The sealing ring is located in the middle of the outer ring of the eccentric bearing, and the axis where the first raceway and the sealing ring are located does not coincide with the axis of the outer ring of the eccentric bearing.

[0010] A locking block is installed in the first raceway and located between two of the rollers;

[0011] A through groove is formed on the locking block.

[0012] In the above technical solution, further, the surface of the locking block that contacts the roller is provided with a groove, and the groove is adapted to the surface of the roller.

[0013] In any of the above technical solutions, further, a barb is provided at the end face of the outer ring of the eccentric bearing, and an annular groove 1 is provided between the barb and the outer ring of the eccentric bearing, and the diameter of the barb and the annular groove 1 is smaller than the outer diameter of the outer ring of the eccentric bearing; an annular groove 2 is provided at the end face of the outer ring of the eccentric bearing, and the end face of the annular groove 2 is parallel to the axis of the outer ring of the eccentric bearing.

[0014] In any of the above technical solutions, further, a U-shaped groove and a countersunk hole are provided on the end face of the outer ring of the eccentric bearing, and the U-shaped groove and the countersunk hole penetrate the barb and the annular groove.

[0015] In any of the above technical solutions, furthermore, the outer ring of the eccentric bearing has an installation groove adapted to the sealing ring.

[0016] In any of the above technical solutions, a second raceway is provided on the end face of the outer ring of the eccentric bearing away from the barb, and a number of balls are provided inside the second raceway.

[0017] In any of the above technical solutions, a rotating sleeve is further provided in the raceway, and the rotating sleeve is in contact with the outer surface of the roller; a rotating plate is provided on the end face of the outer ring of the eccentric bearing, the rotating plate covers the balls on the second raceway, the balls are in contact with the surface of the rotating plate, and the axis of the rotating sleeve and the rotating plate coincides with the axis of the outer ring of the eccentric bearing, and the rotating sleeve and the rotating plate are integral.

[0018] In any of the above technical solutions, further, the outer ring of the eccentric bearing is provided with a plurality of heat dissipation holes in the circumferential direction, and the heat dissipation holes penetrate from the outer surface of the outer ring of the eccentric bearing into the first raceway.

[0019] In any of the above technical solutions, further, a rotating shaft is provided inside the heat dissipation hole, and multiple fins are provided on the rotating shaft, with the fins extending out of the heat dissipation hole.

[0020] The beneficial effects of this utility model are:

[0021] 1. By using an eccentric structure design where "the first raceway, the sealing ring, and the outer ring of the bearing are not concentric", the problem of poor contact and abnormal backlash caused by installation and operation deformation of the sector gear transmission in the steering system is solved. The height of the roller axis can be dynamically adjusted to adapt to the elastic deformation of the steering shaft and compensate for the thermal deformation of the housing, ensuring the transmission meshing accuracy and stability.

[0022] 2. By using locking blocks with through grooves, the stability of the roller circumferential distribution is optimized, the tendency of the rollers to slide or move during high-speed operation or sudden load changes is suppressed, and the rollers are ensured to be evenly distributed along the raceway to maintain the transmission accuracy of the steering system.

[0023] 3. Through the combined design of the barb, annular groove one and annular groove two, a triple sealing barrier is formed to prevent external mud, water and dust from entering the bearing, while preventing the leakage of steering system lubricating grease and extending the bearing life.

[0024] 4. During assembly, the U-shaped groove and countersunk hole are used as force points. Torque and load are applied using special tools to precisely rotate the outer ring of the bearing to adjust the height of the roller axis and compensate for the backlash error of the steering system.

[0025] 5. The tangential force of the roller rotation is transmitted to the rotating plate through the inner wall of the rotating bushing. The rolling of the balls supports the smooth rotation of the rotating plate. The combined torque of the two is output to the steering shaft through the center hole of the rotating plate. The double raceway design significantly increases the fatigue life of the bearing. The concentrated transmission of rotational force reduces the system backlash error and improves the autonomous driving path tracking capability.

[0026] 6. By setting through heat dissipation holes and rotatable fins on the outer ring of the eccentric bearing, the heat conduction efficiency inside the bearing is actively enhanced, the bearing operating temperature is reduced, and the failure of lubricating grease and thermal expansion deformation of materials due to high temperature are avoided, thus extending the service life of the bearing. The kinetic energy of the roller rotation drives the fins to rotate and generate forced convection, converting part of the kinetic energy of the bearing operation into heat dissipation power, without the need for additional energy consumption, thus achieving energy saving and efficiency improvement. Attached Figure Description

[0027] Figure 1 This is a first three-dimensional structural schematic diagram of this utility model;

[0028] Figure 2 This is a schematic diagram of the second three-dimensional structure of this utility model;

[0029] Figure 3 This is a schematic diagram of the third three-dimensional structure of this utility model;

[0030] Figure 4 This is an exploded view of the present invention;

[0031] Figure 5 This is a partial three-dimensional structural schematic diagram of the present invention;

[0032] Figure 6 This is the first sectional view of this utility model;

[0033] Figure 7 This is a second sectional view of the present invention;

[0034] The attached figures are labeled as follows: 1. Eccentric bearing outer ring; 2. First raceway; 3. Roller; 4. Sealing ring; 41. Mounting groove; 5. Locking block; 51. Groove; 6. Through groove; 7. Barb; 8. Annular groove one; 9. Annular groove two; 10. U-groove; 11. Countersunk hole; 12. Second raceway; 13. Ball; 14. Rotating bushing; 15. Rotating plate; 16. Heat dissipation hole; 17. Shaft; 18. Fin. Detailed Implementation

[0035] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application are within the scope of protection of this application.

[0036] In the description of this application, it should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. For ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items, and therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0037] Example 1:

[0038] like Figures 1-7 As shown, this embodiment provides an eccentric bearing in a steering system, comprising:

[0039] The outer ring 1 of the eccentric bearing has a first raceway 2 on its inner side;

[0040] Rollers 3 are assembled in the first raceway 2 of the outer ring 1 of the eccentric bearing. There are multiple rollers 3, which are evenly spaced along the circumferential direction of the first raceway 2.

[0041] The sealing ring 4 is located in the middle of the outer ring 1 of the eccentric bearing, and the axis where the first raceway 2 and the sealing ring 4 are located does not coincide with the axis of the outer ring 1 of the eccentric bearing.

[0042] Locking block 5 is installed in the first raceway 2 and located between two rollers 3;

[0043] The through groove 6 is formed on the locking block 5.

[0044] In this technical solution, the eccentric structure design of "the first raceway 2, the sealing ring 4 and the outer ring of the bearing are not concentric" solves the problems of poor contact and abnormal backlash caused by installation and operation deformation of the sector gear transmission in the steering system. The height of the roller 3 axis can be dynamically adjusted to adapt to the elastic deformation of the steering shaft and compensate for the thermal deformation of the housing, ensuring the transmission meshing accuracy and stability. With the help of the locking block 5 with through groove 6, the circumferential distribution stability of the roller 3 is optimized, the axial movement of the roller 3 during operation is suppressed, the reliability of the steering system in autonomous driving and other scenarios is improved, and the high-precision steering requirements are met (such as suppressing backlash error and stabilizing rotational torque).

[0045] Working Principle: When the automotive steering system is working, the rotation of the steering wheel is converted into wheel steering action through the transmission of the recirculating ball sector gear. Due to installation errors, thermal deformation (such as thermal expansion and contraction of the housing), and elastic deformation of the steering shaft, poor gear meshing (local contact, uneven backlash) is prone to occur. In this eccentric bearing, the axis of the first raceway 2 and the sealing ring 4 does not coincide with the axis of the bearing outer ring, forming an "eccentric adjustment mechanism." When meshing problems occur in the steering system due to the above factors, the height of the axis of the roller 3 can be changed by adjusting the installation angle of the outer ring 1 of the eccentric bearing (equivalent to fine-tuning the gear meshing position). For example, if the gear backlash is too small due to installation misalignment, the outer ring of the bearing can be rotated to allow the axis of the roller 3 to "avoid" the misalignment, increasing the actual meshing backlash. If the local contact stress is too high, the outer ring angle can be adjusted to make the contact between the roller 3 and the gear tooth surface more uniform, dispersing the stress and avoiding thermal adhesion and accelerated wear. Rollers 3 are distributed circumferentially along the first raceway 2. During operation, they are susceptible to slight axial movement due to vibrations and load changes in the steering system, which can disrupt circumferential uniformity and lead to transmission fluctuations (such as sudden torque changes and increased backlash error). Locking blocks 5 are installed between the rollers 3. By contacting the first raceway 2, they form a circumferential "limiting constraint" on the rollers 3, suppressing their tendency to move. The through groove 6 provides elasticity to the locking blocks 5. When rollers 3 experience slight displacement due to load changes, the locking blocks 5 can adaptively adjust through elastic deformation, maintaining constraint on the rollers 3 while avoiding stress concentration caused by rigid limiting. This results in smoother roller operation and ensures the transmission accuracy of the steering system (such as the steering return accuracy required for stable automatic driving and suppressing backlash error). A sealing ring 4 is located in the middle of the bearing, assisting in maintaining the assembly stability of the eccentric structure, preventing impurities from entering and affecting the eccentric adjustment accuracy, forming a sealed protection to prevent oil leakage and impurity intrusion into the steering system, ensuring the long-term reliable operation of the bearing and the entire steering transmission. During vehicle steering, whether in conventional driving or autonomous driving scenarios, this eccentric bearing can dynamically adapt to system deformation, stabilize transmission accuracy, reduce failure risks (such as excessive stress or abnormal backlash), and improve the safety and comfort of steering control.

[0046] like Figure 4 and Figure 5 As shown, in this embodiment, the surface of the locking block 5 that contacts the roller 3 is provided with a groove 51, and the groove 51 is adapted to the surface of the roller 3.

[0047] In this technical solution, by adapting the groove 51 to the surface of the roller 3, such as the arc-shaped groove 51 fitting the cylindrical surface of the roller 3, the contact area between the locking block 5 and the roller 3 is significantly increased (compared to planar contact), thereby improving the circumferential constraint stiffness, suppressing the tendency of the roller 3 to slide or move under high-speed operation or sudden load changes, ensuring that the roller 3 is evenly distributed along the raceway, and maintaining the transmission accuracy of the steering system. The groove 51 design disperses the contact stress between the roller 3 and the locking block 5 over a larger area, avoiding stress concentration caused by point or line contact, reducing the risk of local wear, and extending the service life of the locking block 5 and the roller 3, which is especially suitable for high-load steering systems. When the steering system frequently starts and stops or the steering angle changes rapidly, the "embedded constraint" provided by the groove 51 can transmit torque to each roller 3 more quickly, reduce hysteresis effects, make the steering action more sensitive, and meet the stringent requirements of autonomous driving for the dynamic response of the steering system.

[0048] Working Principle: When roller 3 undergoes slight displacement due to steering system load, the inner wall of groove 51 provides radial and tangential constraint forces through multi-point, surface contact. The depth direction of groove 51 restricts the tendency of roller 3 to detach from the raceway; the friction between the arc surface of groove 51 and the surface of roller 3 prevents circumferential sliding of roller 3, ensuring synchronous movement of locking block 5 and roller 3. The radius of curvature of groove 51 is typically slightly larger than the radius of roller 3, ensuring both fit and a small gap, allowing roller 3 to have very slight adaptive rolling within groove 51, avoiding additional wear caused by rigid jamming. Groove 51 and through groove 6 form an elastic synergy. When roller 3 deforms under load or temperature changes cause dimensional fluctuations, through groove 6 allows locking block 5 to elastically expand and contract, while groove 51 adaptively adjusts the contact state through deformation to maintain stable constraint. For example, in high-temperature environments, the thermal expansion of roller 3 causes slight elastic tension in the inner wall of groove 51, preventing excessive compressive stress; under heavy-load conditions, groove 51 disperses contact stress through elastic deformation, preventing localized crushing. The groove 51 can be designed as a partially closed structure (such as a U-shaped groove 10U) to form a "micro-oil cavity" in the contact area, store grease, reduce dry friction between the roller 3 and the locking block 5, and prevent external impurities from entering, thereby improving sealing performance.

[0049] Example 2:

[0050] This embodiment provides an eccentric bearing in a steering system, which, in addition to the technical solutions of the above embodiments, also has the following technical features.

[0051] like Figure 3 , Figure 6 and Figure 7As shown, in this embodiment, the optimized design includes a barb 7 at the end face of the outer ring 1 of the eccentric bearing, an annular groove 8 between the barb 7 and the outer ring 1 of the eccentric bearing, and the diameters of the barb 7 and the annular groove 8 are smaller than the outer diameter of the outer ring 1 of the eccentric bearing; an annular groove 9 is provided at the end face of the outer ring 1 of the eccentric bearing, and the end face of the annular groove 9 is parallel to the axis of the outer ring 1 of the eccentric bearing.

[0052] In this technical solution, a triple sealing barrier is formed by the combined design of barb 7, annular groove 8, and annular groove 9 to prevent external mud, water, and dust from entering the bearing, while also preventing leakage of steering system lubricating grease and extending bearing life. The elastic structure of barb 7 can automatically adjust the sealing gap when there is vibration or temperature change. Annular groove 8 stores lubricating grease to form a "dynamic oil seal." Annular groove 9 works in conjunction with external seals (such as O-rings and dust covers) to compensate for assembly errors and ensure sealing reliability. The diameters of barb 7 and annular groove 8 are smaller than the outer diameter of the bearing outer ring, avoiding an increase in radial dimensions and making it suitable for the compact space of the steering system. The axially parallel design of annular groove 9 makes full use of the end face space to achieve axial sealing enhancement.

[0053] like Figure 3 , Figure 6 and Figure 7 As shown, in this embodiment, the optimized eccentric bearing outer ring 1 has a U-shaped groove 10U and a countersunk hole 11 on its end face, and the U-shaped groove 10U and the countersunk hole 11 pass through the barb 7 and the annular groove 8.

[0054] In this technical solution, when machining the eccentric first raceway 2 and the sealing ring 4 mounting groove 41 on the outer ring of the bearing, the machining accuracy of the eccentric structure is ensured by using the U-shaped groove 10U and the countersunk hole 11 in conjunction with the machine tool fixture. During assembly, the U-shaped groove 10U and the countersunk hole 11 are used as force application points. Torque and load are applied using a special tool to precisely rotate the outer ring of the bearing to adjust the height of the roller 3 axis, compensating for the backlash error of the steering system (such as adjusting the backlash from 0.3mm to the design value of 0.15mm). The U-shaped groove 10U and the countersunk hole 11 penetrate the barb 7 and the annular groove 8, achieving positioning and adjustment functions without increasing the radial dimension of the bearing, thus adapting to the compact space of the steering system.

[0055] Working principle: The U-shaped groove 10U (opening width 8-10mm, depth 3-5mm) engages with the locating pin of the machine tool fixture to restrict the circumferential rotational freedom of the bearing outer ring; the countersunk hole 11 (diameter 6-8mm, depth 2-3mm) is fastened to the fixture with bolts to constrain axial displacement and ensure the positional accuracy during the machining of the eccentric first raceway 2. By inserting a special wrench into the U-shaped groove 10U, a torque of 10-20Nm is applied to rotate the bearing outer ring, and the height of the roller 3 axis is changed by utilizing the eccentricity; the countersunk hole 11 is used to install a puller or press-fitting machine, and the axial position of the bearing is finely adjusted by axial loading to optimize the gear meshing backlash. The U-shaped groove 10U and the countersunk hole 11 penetrate the barb 7 and the annular groove 8, but do not compromise their sealing integrity.

[0056] like Figure 6 As shown, in this embodiment, the optimized eccentric bearing outer ring 1 has an internal mounting groove 41 adapted to the sealing ring 4.

[0057] In this technical solution, the sealing ring 4 is precisely fixed by the mounting groove 41, preventing external mud, water, and dust from entering the bearing and simultaneously preventing leakage of steering system lubricating grease, thus extending bearing life. The mounting groove 41 ensures the concentricity of the sealing ring 4 and the outer ring of the bearing, avoiding sealing failure caused by misalignment of the sealing ring 4 and improving the reliability of the steering system. The positioning function of the mounting groove 41 makes the assembly of the sealing ring 4 more convenient and reduces manual adjustment time.

[0058] Example 3:

[0059] This embodiment provides an eccentric bearing in a steering system, which, in addition to the technical solutions of the above embodiments, also has the following technical features.

[0060] like Figures 4-6 As shown, in this embodiment, the optimized eccentric bearing outer ring 1 has a second raceway 12 on the end face away from the barb 7, and the second raceway 12 has a plurality of balls 13 inside.

[0061] like Figures 1-4 As shown, in this embodiment, the optimized design includes a rotating sleeve 14 inside the raceway, which contacts the outer surface of the roller 3; a rotating plate 15 is provided on the end face of the outer ring 1 of the eccentric bearing, which covers the balls 13 on the second raceway 12, with the balls 13 in contact with the surface of the rotating plate 15, and the axes of the rotating sleeve 14 and the rotating plate 15 coincide with the axis of the outer ring 1 of the eccentric bearing, making the rotating sleeve 14 and the rotating plate 15 an integral unit.

[0062] In this technical solution, the combination of the first raceway 2 (including rollers 3) and the second raceway 12 (including balls 13) simultaneously bears radial and axial loads, improving the stability of the bearing under complex working conditions and enabling it to withstand large radial and axial forces at the same time. Utilizing the integrated structure of the rotating bushing 14 and the rotating plate 15, the rotational force of the rollers 3 and balls 13 is converted into concentrated torque output, reducing energy loss and optimizing the steering system response speed. The axes of the rotating bushing 14 and the rotating plate 15 are concentric with the outer ring of the bearing, while the first raceway 2 containing the rollers 3 is eccentric. This maintains the eccentricity adjustment function while ensuring that the output torque is coaxial, preventing additional vibrations in the steering system due to lever arm offset.

[0063] Working principle: The rotational tangential force of roller 3 is transmitted to the rotating plate 15 through the inner wall of the rotating bushing 14. The rolling bearings 13 support the smooth rotation of the rotating plate 15. The resultant torque of both is output to the steering shaft through the center hole of the rotating plate 15. The concentric design of the rotating bushing 14 and the rotating plate 15 ensures that the line of action of the resultant torque always coincides with the steering shaft, eliminating the additional bending moment caused by eccentricity and reducing steering torque fluctuation. The inner wall of the bushing is in line contact with the outer surface of roller 3, allowing roller 3 to make slight self-adjustments when transmitting torque, avoiding jamming. The double raceway design significantly increases the bearing fatigue life, and the concentrated transmission of rotational force reduces system backlash error and improves the autonomous driving path tracking capability. The axial dimension is shorter than that of traditional combined bearings, making it suitable for compact steering system designs.

[0064] Example 3:

[0065] This embodiment provides an eccentric bearing in a steering system, which, in addition to the technical solutions of the above embodiments, also has the following technical features.

[0066] like Figures 1-6 As shown, in this embodiment, the eccentric bearing outer ring 1 is provided with a plurality of heat dissipation holes 16 in the circumferential direction, and the heat dissipation holes 16 penetrate from the outer surface of the eccentric bearing outer ring 1 into the first raceway 2.

[0067] like Figure 1 and Figure 5 As shown, in this embodiment, the optimized heat dissipation hole 16 is provided with a rotating shaft 17 inside, and the rotating shaft 17 is provided with multiple fins 18, which extend out of the heat dissipation hole 16.

[0068] In this technical solution, by providing through-hole heat dissipation holes 16 and rotatable fins 18 on the outer ring 1 of the eccentric bearing, the heat conduction efficiency inside the bearing is actively enhanced, reducing the bearing's operating temperature and preventing grease failure and material thermal expansion deformation due to high temperatures, thus extending the bearing's service life. The kinetic energy of the rollers 3 drives the fins 18 to rotate, generating forced convection and converting part of the bearing's kinetic energy into heat dissipation power, eliminating the need for additional energy consumption and achieving energy saving and efficiency improvement. The heat dissipation structure is integrated into the outer ring of the bearing, without increasing the radial dimension, adapting to the compact space requirements of the steering system, and avoiding the complex piping design of traditional air-cooled or liquid-cooled systems.

[0069] Working principle: When the bearing is running, the roller 3 rubs against the raceway, generating heat. This heat is conducted through the metal material of the outer ring 1 of the eccentric bearing to the inner wall of the heat dissipation hole 16. In a static state, the heat is slowly dissipated through the heat dissipation hole 16 and natural convection with the air. When the vehicle is moving, the external airflow sweeps over the heat dissipation hole 16, further enhancing heat dissipation. When the roller 3 rotates, its outer surface contacts the fins 18, driving the shaft 17 and fins 18 to rotate through friction. The rotating fins 18 agitate the air, forming a directional airflow inside and outside the heat dissipation hole 16, forcibly carrying away the heat from the hole wall. The rotating fins 18 have no complex transmission structure, relying solely on the kinetic energy of the roller 3 for drive, resulting in high reliability and a service life synchronized with the bearing, requiring no additional maintenance. The heat dissipation effect automatically adjusts with the steering system load; the greater the load, the faster the roller 3 rotates, and the stronger the heat dissipation capacity of the fins 18, forming a dynamic adaptive heat dissipation mechanism.

[0070] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. An eccentric bearing in a steering system, characterized in that, include: The outer ring of the eccentric bearing (1) has a first raceway (2) on its inner side; Rollers (3) are assembled in the first raceway (2) of the outer ring (1) of the eccentric bearing. There are multiple rollers (3) and they are evenly spaced along the circumferential direction of the first raceway (2). The sealing ring (4) is located in the middle of the outer ring (1) of the eccentric bearing, and the axis where the first raceway (2) and the sealing ring (4) are located does not coincide with the axis of the outer ring (1) of the eccentric bearing; A locking block (5) is installed in the first raceway (2) and located between two of the rollers (3); A through groove (6) is provided on the locking block (5).

2. An eccentric bearing in a steering system according to claim 1, characterized in that, The locking block (5) has a groove (51) on the surface that contacts the roller (3), and the groove (51) is adapted to the surface of the roller (3).

3. An eccentric bearing in a steering system according to claim 1, characterized in that, The outer ring (1) of the eccentric bearing is provided with a barb (7) at its end face, and there is an annular groove (8) between the barb (7) and the outer ring (1) of the eccentric bearing, and the diameter of the barb (7) and the annular groove (8) is smaller than the outer diameter of the outer ring (1) of the eccentric bearing; the outer ring (1) of the eccentric bearing is provided with an annular groove (9) at its end face, and the end face of the annular groove (9) is parallel to the axis of the outer ring (1) of the eccentric bearing.

4. An eccentric bearing in a steering system according to claim 3, characterized in that, The outer ring (1) of the eccentric bearing is provided with a U-shaped groove (10U) and a countersunk hole (11) on its end face, and the U-shaped groove (10U) and the countersunk hole (11) penetrate the barb (7) and the annular groove (8).

5. An eccentric bearing in a steering system according to claim 1, characterized in that, The outer ring (1) of the eccentric bearing has an installation groove (41) adapted to the sealing ring (4).

6. An eccentric bearing in a steering system according to claim 1, characterized in that, The outer ring (1) of the eccentric bearing has a second raceway (12) on the end face away from the barb (7), and the second raceway (12) has a number of balls (13) inside.

7. An eccentric bearing in a steering system according to claim 6, characterized in that, The raceway is provided with a rotating bushing (14), which is in contact with the outer surface of the roller (3); the end face of the outer ring (1) of the eccentric bearing is provided with a rotating plate (15), which covers the ball (13) on the second raceway (12), the ball (13) is in contact with the surface of the rotating plate (15), and the axis of the rotating bushing (14) and the rotating plate (15) coincides with the axis of the outer ring (1) of the eccentric bearing, and the rotating bushing (14) and the rotating plate (15) are integrated.

8. An eccentric bearing in a steering system according to claim 1, characterized in that, The outer ring (1) of the eccentric bearing has a plurality of heat dissipation holes (16) in the circumferential direction. The heat dissipation holes (16) penetrate from the outer surface of the outer ring (1) of the eccentric bearing into the first raceway (2).

9. An eccentric bearing in a steering system according to claim 8, characterized in that, The heat dissipation hole (16) is provided with a rotating shaft (17) inside, and multiple fins (18) are provided on the rotating shaft (17), with the fins (18) extending out of the heat dissipation hole (16).

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