Self-locking anti-rotation double-row tapered roller bearing inner ring
By employing threaded connections and anti-rotation block design in the inner ring of double-row tapered roller bearings, the problem of inner ring displacement caused by snap ring connections is solved, achieving stable bearing operation and extended lifespan, and reducing maintenance costs.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SHANDONG YIJIXI PRECISION MFG CO LTD
- Filing Date
- 2025-06-04
- Publication Date
- 2026-04-14
AI Technical Summary
The existing snap ring connection method for the inner ring of double-row tapered roller bearings is prone to relative displacement of the inner ring under high-speed operation or heavy load, which leads to the disruption of the fit between internal bearing components, increased friction and wear, and affects bearing life and equipment stability.
The threaded connection method is adopted. The external threaded part of the small flange of the inner ring of the first bearing is connected with the internal threaded part of the small flange of the inner ring of the second bearing to form a self-locking connection, which prevents the inner ring from rotating relative to each other or displacing axially. The anti-rotation capability can be enhanced by anti-rotation blocks.
It improves the stability and service life of bearings, reduces maintenance difficulty and cost, ensures smooth operation of equipment, and reduces production downtime caused by failures.
Smart Images
Figure CN224120553U_ABST
Abstract
Description
Technical Field
[0001] This application belongs to the field of double-row tapered roller bearings, and particularly relates to a self-locking anti-rotation inner ring of a double-row tapered roller bearing. Background Technology
[0002] In modern mechanical industry, double-row tapered roller bearings are a key mechanical component, widely used in various mechanical equipment that need to withstand large combined radial and axial loads, such as automotive transmissions, heavy machinery transmission systems, and main shafts of large industrial equipment. Their unique double-row tapered roller structure design allows them to withstand loads from different directions simultaneously in complex working environments, ensuring the smoothness and reliability of equipment operation. A typical double-row tapered roller bearing mainly consists of an outer ring, two inner rings, a cage, and double-row tapered rollers. The two inner rings are designed as separate units, which facilitates bearing installation, disassembly, and maintenance, allowing for more efficient replacement or maintenance of inner ring components, reducing maintenance costs and time.
[0003] However, in existing technologies, the connection between the two inner rings of a double-row tapered roller bearing is commonly achieved using snap rings. While snap ring connections offer advantages such as simple structure and convenient installation, they have revealed a series of serious problems in practical use. Due to the inherent mechanical properties of the snap ring connection and the influence of various complex factors in the working environment, this connection method often suffers from insecure connections. When the bearing operates at high speed or bears a large load, relative displacement can easily occur between the inner rings. This displacement not only disrupts the normal fit between the internal components of the bearing, altering the contact state between the rollers and the inner and outer ring raceways, increasing friction and wear, and reducing the bearing's service life, but it can also cause unstable equipment operation, generating vibration and noise, seriously affecting the performance and precision of the entire mechanical equipment, and may even lead to equipment failure, resulting in production stoppages and economic losses. Therefore, existing technologies require further improvement and enhancement. Utility Model Content
[0004] This invention provides a self-locking anti-rotation double-row tapered roller bearing inner ring to solve the problem that when the two inner rings are connected by a snap ring, relative displacement easily occurs between the inner rings when the bearing is running at high speed or under heavy load, which leads to the disruption of the fit between the internal components of the bearing, changes in the contact state between the rollers and the raceway, increased friction and wear, and reduced bearing life.
[0005] To achieve the above objectives, the present invention provides the following technical solution:
[0006] A self-locking anti-rotation double-row tapered roller bearing inner ring includes a first bearing inner ring and a second bearing inner ring, which are coaxially arranged. Both the first and second bearing inner rings include a large inner ring flange, a small inner ring flange, and a roller raceway located between them. An external thread is provided on the end face of the small inner ring flange of the first bearing inner ring, and an internal thread is provided on the small inner ring flange of the second bearing inner ring. The external thread and the internal thread are engaged to achieve a self-locking connection between the first and second bearing inner rings.
[0007] The aforementioned structure features an external thread on the end face of the small flange of the first bearing inner ring and an internal thread on the small flange of the second bearing inner ring. When the external thread of the first bearing inner ring and the internal thread of the second bearing inner ring are engaged, a tight threaded connection is formed. Under lateral force, the inclined surface of the thread generates a component force opposite to the direction of the lateral force, preventing relative lateral movement between the inner rings. The threaded connection is self-locking; when the friction angle of the threaded pair is greater than the helix angle, the threaded pair can achieve self-locking, preventing relative rotation or axial displacement of the inner rings during operation. Compared to existing snap ring connections, where the snap ring may lose its restraining effect on the inner ring due to fatigue or deformation under heavy loads or high-speed operation, leading to displacement of the inner ring, the self-locking threaded connection method designed in this invention is more reliable, maintaining a stable connection of the inner rings under various operating conditions, ensuring normal bearing operation. The threaded connection method is relatively simple, and installation and disassembly are convenient. When the bearing needs maintenance or replacement, simply tighten or loosen the threaded connection. No complicated operations or professional tools are required, which reduces the difficulty and time cost of maintenance and has high practical value and promising prospects for widespread application.
[0008] In a preferred embodiment, after the external thread and the internal thread are connected, the through hole formed by the first bearing inner ring and the second bearing inner ring has the same diameter along the axial direction, and the outer wall surface of the small flange of the first bearing inner ring and the outer wall surface of the small flange of the second bearing inner ring are flush.
[0009] When the through holes have the same diameter along the axial direction, it can ensure that the fit dimensions between the shaft and the entire inner ring are consistent, which is convenient for installation. The outer wall surfaces of the two inner ring small flanges are flush, which can ensure that the roller has good contact with the inner and outer ring raceways during rolling, and will not cause uneven force on the roller or abnormal running trajectory due to the unevenness of the inner ring small flanges.
[0010] In a preferred embodiment, the roller raceways and the large flange of the inner ring of the first bearing inner ring and the inner ring of the second bearing inner ring have the same structural dimensions, and the height of the small flange of the inner ring of the first bearing inner ring is less than the height of the small flange of the inner ring of the second bearing inner ring; an external threaded portion extends outward from the end face of the small flange of the first bearing inner ring, and an internal threaded portion adapted to the external threaded portion is provided on the inner wall end of the small flange of the second bearing inner ring.
[0011] The improvement is made only at the small flange of the bearing inner ring, retaining the characteristic that the roller raceways and large flanges of the first and second bearing inner rings have the same structural dimensions. The identical dimensions of the roller raceways and large flanges mean that the bearing performance in terms of load bearing and roller guidance remains consistent with the original design. The height of the small flange of the first bearing inner ring is smaller than that of the second bearing inner ring; this height difference provides space for threaded connections. During connection, the external thread of the first bearing inner ring can smoothly screw into the internal thread of the second bearing inner ring without being limited by the height of the small flange.
[0012] In a preferred embodiment, the length of the external thread is 50%-90% of the length of the small flange of the inner ring of the first bearing, and the length of the internal thread is 50%-90% of the length of the small flange of the inner ring of the second bearing.
[0013] In a preferred embodiment, the external thread portion and the internal thread portion are self-locking thread structures, and the thread helix angle of the self-locking thread structure is less than or equal to the equivalent friction angle, so as to prevent the inner ring of the first bearing and the inner ring of the second bearing from rotating relative to each other after connection.
[0014] In a preferred implementation, after the external thread portion and the internal thread portion are connected, the end face of the small flange of the first bearing inner ring and the end face of the small flange of the second bearing inner ring come into contact.
[0015] When the end face of the small flange of the first bearing inner ring and the end face of the small flange of the second bearing inner ring come into contact, a tight connection is formed between the two inner rings, which can effectively resist the action of axial force and prevent the inner rings from undergoing relative displacement in the axial direction.
[0016] In a preferred embodiment, the external threaded portion has a first groove, and the internal threaded portion has a second groove. When the external threaded portion and the internal threaded portion are connected, the first groove and the second groove are radially aligned. Anti-rotation blocks are embedded in the radially aligned portions of the first groove and the second groove to prevent the inner rings of the first bearing and the second bearing from rotating relative to each other.
[0017] The thread self-locking mechanism itself provides a certain degree of anti-rotation capability, but adding an anti-rotation block creates a double-layered anti-rotation protection. After the anti-rotation block is embedded in the corresponding first and second grooves, it directly restricts the relative rotation of the inner rings of the first and second bearings, preventing both forward and reverse rotation; the anti-rotation block must be removed. Thus, even if the thread self-locking mechanism loosens to some extent due to long-term use, vibration, or other factors, the anti-rotation block can still function, preventing relative rotation between the inner rings, thereby greatly improving the reliability of anti-rotation.
[0018] In a preferred embodiment, the anti-rotation block has an arc-shaped surface. When the embedded anti-rotation block is embedded in the first groove and the second groove, the arc-shaped surface is flush with the inner wall surfaces of the inner rings of the first and second bearings. After the shaft is installed, the surface of the shaft contacts the arc-shaped surface of the embedded anti-rotation block, forming a radial limit on the embedded anti-rotation block to prevent it from falling off.
[0019] In a preferred embodiment, the external thread portion is integrally formed with the inner ring of the first bearing, and the internal thread portion is integrally formed with the inner ring of the second bearing. Attached Figure Description
[0020] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain this application and do not constitute an undue limitation of the present invention. In the drawings:
[0021] Figure 1 An exploded view of an embodiment of the self-locking anti-rotation double-row tapered roller bearing of this application is shown.
[0022] Figure 2 The illustration shows a schematic cross-sectional structural diagram of one embodiment of the self-locking anti-rotation double-row tapered roller bearing of this application, in which the two inner rings are assembled into the bearing.
[0023] Figure 3 An exploded view of an embodiment of the self-locking anti-rotation double-row tapered roller bearing of this application is shown.
[0024] Label Explanation:
[0025] 1. First bearing inner ring; 10. Small flange of first bearing inner ring; 100. External thread; 1000. First groove; 11. Large flange of first bearing inner ring; 2. Second bearing inner ring; 20. Small flange of second bearing inner ring; 200. Internal thread; 2000. Second groove; 21. Large flange of second bearing inner ring; 3. Through shaft hole; 4. Anti-rotation block. Detailed Implementation
[0026] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit and scope of this invention. Therefore, the drawings and description are considered exemplary in nature and not restrictive.
[0027] In the description of this utility model, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. In this utility model, unless otherwise expressly specified and limited, the first feature being "upper" or "lower" than the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium.
[0028] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral unit; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. However, specifying a direct connection indicates that the two main bodies at the connection point are not connected by an intermediate structure, but are simply connected to form a whole through a connecting structure. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.
[0029] In this utility model, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature.
[0030] The present invention will now be described with reference to the accompanying drawings.
[0031] The specific solution adopted is as follows:
[0032] like Figure 1-3As shown, this utility model provides a self-locking anti-rotation double-row tapered roller bearing inner ring, including a first bearing inner ring 1 and a second bearing inner ring 2. The first bearing inner ring 1 and the second bearing inner ring 2 are coaxially arranged. Both the first bearing inner ring 1 and the second bearing inner ring 2 include a large inner ring flange, a small inner ring flange, and a roller raceway located between the two. An external thread portion 100 is provided on the end face of the small inner ring flange 10 of the first bearing inner ring, and an internal thread portion 200 is provided on the small inner ring flange 20 of the second bearing inner ring. The external thread portion 100 and the internal thread portion 200 are engaged to achieve a self-locking connection between the first bearing inner ring 1 and the second bearing inner ring 2.
[0033] By employing the self-locking anti-rotation double-row tapered roller bearing inner ring of this application, when the external thread 100 of the first bearing inner ring 1 and the internal thread 200 of the second bearing inner ring 2 are engaged, a tight threaded engagement is formed between them. When subjected to lateral force, the inclined surface of the thread generates a component force opposite to the direction of the lateral force, preventing relative lateral movement between the inner rings. The threaded connection has self-locking properties; when the friction angle of the threaded pair is greater than the helix angle, the threaded pair can achieve self-locking. In this design, the parameters of the external thread 100 and the internal thread 200, such as pitch and thread angle, are rationally designed so that the threaded pair can automatically lock under normal operating conditions, preventing relative rotation or axial displacement of the inner rings during operation. Compared with existing snap ring connections, snap ring connections may lose their restraining effect on the inner ring due to fatigue or deformation under large loads or high-speed operation, leading to displacement of the inner ring. The self-locking threaded connection method of this design is more reliable, maintaining a stable connection of the inner rings under various operating conditions and ensuring normal bearing operation.
[0034] Because the inner ring does not shift during operation, the contact state between the roller and the inner and outer ring raceways remains stable, reducing additional friction and wear caused by changes in the contact state. Reduced friction and wear decrease heat generation within the bearing, preventing overheating damage and extending its service life. This extended bearing life reduces the probability of equipment failure, thus decreasing the frequency of repairs and maintenance costs. Simultaneously, stable bearing operation reduces production downtime due to equipment failure, improving production efficiency.
[0035] Furthermore, threaded connections are relatively simple, and installation and disassembly are convenient. When bearing maintenance or replacement is required, simply tighten or loosen the threaded connection; no complicated operations or specialized tools are needed, reducing maintenance difficulty and time costs, and demonstrating high practical value and promising prospects for widespread application.
[0036] See Figure 2In a preferred embodiment of this application, after the external thread portion 100 and the internal thread portion 200 are connected, the through hole 3 formed by the first bearing inner ring 1 and the second bearing inner ring 2 has the same diameter along the axial direction, and the outer wall surface of the small flange 10 of the first bearing inner ring and the outer wall surface of the small flange of the second bearing inner ring 2 are flush.
[0037] The fit between the shaft and the bearing inner ring typically needs to adhere to certain tolerance standards and fit characteristics to ensure stable and smooth rotation of the shaft within the inner ring while transmitting sufficient torque. When the through-holes 3 have the same diameter along the axial direction, it ensures consistent fit dimensions between the shaft and the entire inner ring. If the through-holes 3 have inconsistent diameters, the shaft requires special design, and issues such as misalignment and jamming may occur during installation and operation. Through-holes 3 of the same diameter avoid this problem, ensuring a standard fit between the shaft and the inner ring and guaranteeing normal shaft operation. Through-holes 3 of the same diameter also facilitate shaft installation. During installation, the shaft only needs to be inserted along a hole of a fixed diameter, eliminating the need to consider matching different diameter segments, thus improving installation efficiency and accuracy.
[0038] In double-row tapered roller bearings, the rollers roll between the raceways of the inner and outer rings. The flush outer wall of the inner ring's small flange ensures good contact between the roller and the raceways of both rings during rolling, preventing uneven force distribution or abnormal running trajectories caused by unevenness in the small flange. For example, if the outer wall of the inner ring's small flange is uneven, the roller may experience additional compression or impact when rolling to that position, accelerating wear and reducing bearing life. In mechanical design, the dimensional fits between various components need to form a reasonable dimensional chain to ensure the accuracy and performance of the entire mechanical system. The fit between the inner and outer rings is a crucial link in this dimensional chain; a flush outer wall of the inner ring's small flange ensures the accuracy of the dimensional chain, guaranteeing that the bearing's fit with other components conforms to standards.
[0039] See Figure 2 The roller raceways and inner ring large flanges of the first bearing inner ring 1 and the second bearing inner ring 2 have the same structural dimensions, and the height of the inner ring small flange of the first bearing inner ring 1 is smaller than the height of the inner ring small flange of the second bearing inner ring 2; an external thread portion 100 extends outward from the end face of the small flange 10 of the first bearing inner ring, and an internal thread portion 200 adapted to the external thread portion 100 is provided on the inner wall end of the small flange 20 of the second bearing inner ring.
[0040] The improvement is made only at the small flange of the inner ring of the bearing, retaining the characteristic that the roller raceways and large flanges of the first bearing inner ring 1 and the second bearing inner ring 2 have the same structural dimensions. The identical dimensions of the roller raceways and large flanges mean that the bearing's performance in terms of load bearing and guiding roller movement remains consistent with the original design. The design of the roller raceways determines the roller's movement trajectory and stress conditions. Raceways of the same size ensure that the rollers maintain a stable contact state during operation, thereby maintaining the bearing's load-bearing capacity and operational accuracy. The large flange of the inner ring restricts the axial movement of the rollers. Large flanges of the same size ensure the axial stability of the rollers, preventing them from falling off or deviating from their normal position.
[0041] The height of the inner ring flange of the first bearing inner ring 1 is less than that of the inner ring flange of the second bearing inner ring 2. This height difference provides space for the threaded connection. During connection, the external thread 100 of the first bearing inner ring 1 can smoothly screw into the internal thread 200 of the second bearing inner ring 2 without being limited by the height of the flange. Simultaneously, the flanges of different heights also provide positioning and restraint after connection, preventing excessive rotation or displacement of the inner ring during the connection process. The threaded connection is self-locking, preventing relative rotation or axial displacement of the inner ring during operation. The external thread 100 is integrally formed with the first bearing inner ring 1, and the internal thread 200 is integrally formed with the second bearing inner ring 2, ensuring the strength and stability of the threaded connection. The integrally formed design avoids loosening or breakage at the threaded connection, improving the reliability of the connection.
[0042] Furthermore, the length of the external thread portion 100 is 50%-90% of the length of the small flange 10 of the inner ring of the first bearing, and the length of the internal thread portion 200 is 50%-90% of the length of the small flange 20 of the inner ring of the second bearing.
[0043] On the one hand, this length range ensures sufficient engagement length between the internal and external threads. Under axial and radial loads, sufficient engagement length disperses stress, preventing stress concentration at the threaded connection and thus avoiding deformation or damage. On the other hand, if the external thread portion 100 and the internal thread portion 200 are too long, they will excessively occupy space on the small flange, potentially reducing its structural strength and even affecting the installation and layout of other components. Controlling the thread length within the range of 50%-90% ensures connection strength while avoiding excessive space occupation, resulting in a more compact overall structure for the bearing inner ring.
[0044] See Figure 2 After the external thread portion 100 and the internal thread portion 200 are connected, the end face of the small flange 10 of the first bearing inner ring and the end face of the small flange 20 of the second bearing inner ring come into contact.
[0045] During bearing operation, it is subjected to various forces, including axial forces. When the end faces of the first bearing inner ring small flange 10 and the second bearing inner ring small flange 20 come into contact, a tight connection is formed between the two inner rings, effectively resisting the axial force and preventing relative displacement of the inner rings in the axial direction. For example, in some mechanical equipment that needs to withstand large axial loads, such as the drum bearings of cranes, the end face contact design can ensure the stability of the bearing inner ring in the axial direction, ensuring the normal operation of the equipment. When the end faces of the two inner ring small flanges come into contact, the load can be distributed more evenly at the connection. When subjected to combined radial and axial loads, the end face contact can provide an additional support surface, distributing the load over a larger area, thereby reducing local stress concentration.
[0046] In addition, during installation, the end face contact provides a clear reference surface for the positioning of the inner ring. Installers can ensure the accurate installation position of the inner ring and reduce installation errors by ensuring that the end faces of the two inner ring small flanges are in close contact.
[0047] As a preferred embodiment of this application, see [link to application]. Figure 3 The external threaded portion 100 is provided with a first groove 1000, and the internal threaded portion 200 is provided with a second groove 2000. When the external threaded portion 100 and the internal threaded portion 200 are connected, the first groove 1000 and the second groove 2000 are radially corresponding. Anti-rotation blocks 4 are embedded in the radially corresponding positions of the first groove 1000 and the second groove 2000 to prevent the inner ring 1 of the first bearing and the inner ring 2 of the second bearing from rotating relative to each other.
[0048] The thread self-locking mechanism itself provides a certain degree of anti-rotation capability, but the addition of the anti-rotation block 4 creates a double-layered anti-rotation protection. After the anti-rotation block 4 is embedded in the corresponding first groove 1000 and second groove 2000, it directly restricts the relative rotation of the first bearing inner ring 1 and the second bearing inner ring 2. Neither forward nor reverse rotation is possible; the anti-rotation block 4 must be removed. Thus, even if the thread self-locking mechanism loosens to some extent due to long-term use, vibration, or other factors, the anti-rotation block 4 can still function, preventing relative rotation between the inner rings, thereby greatly improving the reliability of anti-rotation.
[0049] The anti-rotation block 4 has an arc-shaped surface. After being embedded in the first groove 1000 and the second groove 2000, the arc-shaped surface is flush with the inner wall surface of the first bearing inner ring 1 and the second bearing inner ring 2. This design achieves the anti-rotation function without causing protrusions or depressions to the inner wall surface of the bearing inner ring, maintaining the flatness of the inner wall surface. The flat inner wall surface is beneficial to the installation and operation of the shaft, reducing friction and wear between the shaft and the inner ring caused by unevenness of the inner wall surface.
[0050] For any parts not mentioned in this utility model, existing technologies can be used or referenced.
[0051] The above are merely specific embodiments of this utility model, but the protection scope of this utility model is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this utility model, and these should all be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the scope of the claims.
Claims
1. A self-locking, anti-rotation double-row tapered roller bearing inner ring, characterized in that, The bearing includes a first bearing inner ring and a second bearing inner ring, which are coaxially arranged. Both the first and second bearing inner rings include a large inner ring flange, a small inner ring flange, and a roller raceway located between them. An external thread is provided on the end face of the small inner ring flange of the first bearing inner ring, and an internal thread is provided on the small inner ring flange of the second bearing inner ring. The external thread and the internal thread are engaged to achieve a self-locking connection between the first and second bearing inner rings.
2. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, After the external thread and the internal thread are connected, the through hole formed by the first bearing inner ring and the second bearing inner ring has the same diameter along the axial direction, and the outer wall surface of the small flange of the first bearing inner ring and the outer wall surface of the small flange of the second bearing inner ring are flush.
3. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, The roller raceways and inner ring large flanges of the first bearing inner ring and the second bearing inner ring have the same structural dimensions, and the height of the inner ring small flange of the first bearing inner ring is less than the height of the inner ring small flange of the second bearing inner ring; an external threaded portion extends outward from the end face of the small flange of the first bearing inner ring, and an internal threaded portion adapted to the external threaded portion is provided on the inner wall end of the small flange of the second bearing inner ring.
4. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 3, characterized in that, The length of the external thread is 50%-90% of the length of the small flange of the inner ring of the first bearing, and the length of the internal thread is 50%-90% of the length of the small flange of the inner ring of the second bearing.
5. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, The external thread and the internal thread are self-locking thread structures. The thread helix angle of the self-locking thread structure is less than or equal to the equivalent friction angle to prevent relative rotation between the inner rings of the first bearing and the second bearing after connection.
6. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, After the external threaded portion and the internal threaded portion are connected, the end face of the small flange of the inner ring of the first bearing and the end face of the small flange of the inner ring of the second bearing come into contact.
7. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, The external threaded portion has a first groove, and the internal threaded portion has a second groove. When the external threaded portion and the internal threaded portion are connected, the first groove and the second groove are radially aligned. Anti-rotation blocks are embedded in the radially aligned portions of the first groove and the second groove to prevent the inner rings of the first bearing and the second bearing from rotating relative to each other.
8. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 7, characterized in that, The anti-rotation block has an arc-shaped surface. When the embedded anti-rotation block is embedded in the first groove and the second groove, the arc-shaped surface is flush with the inner wall surface of the inner ring of the first bearing and the inner ring of the second bearing. After the shaft is installed, the surface of the shaft contacts the arc-shaped surface of the embedded anti-rotation block, forming a radial limit on the embedded anti-rotation block to prevent it from falling off.
9. The inner ring of the self-locking anti-rotation double-row tapered roller bearing according to claim 1, characterized in that, The external thread portion is integrally formed with the inner ring of the first bearing, and the internal thread portion is integrally formed with the inner ring of the second bearing.