A dual ring redundant bearing

Abstract

The utility model belongs to bearing technical field discloses a double ring redundancy bearing, including the inside to the outside in proper order of inner ring, inner retainer, middle ring, outer retainer and outer ring, be equipped with a plurality of inner rolling body between inner ring and middle ring, inner retainer is connected with each inner rolling body, be equipped with a plurality of outer rolling body between middle ring and outer ring, outer retainer is connected with each outer rolling body, the front side of inner ring is equipped with a plurality of inner pawl, its back side is equipped with a plurality of outer pawl, each inner pawl and each outer pawl are connected with inner ring through elastic part, the front side of inner retainer is equipped with inner ratchet wheel, inner ratchet wheel is matched with each inner pawl, the back side of outer retainer is equipped with outer ratchet wheel, outer ratchet wheel is matched with each outer ratchet wheel and is opposite with inner ratchet wheel direction.

Description

Technical Field

[0001] This utility model belongs to the field of bearing technology, and in particular relates to a double-ring redundant bearing. Background Technology

[0002] The helicopter swashplate is a critical transmission control component in rotorcraft, and its spherical bearings typically need to perform high-frequency reciprocating oscillations within a small angle range of approximately ±90°. Under these special operating conditions, traditional angular contact ball bearings face serious durability issues. Because the rolling elements always act on the same arc segment of the raceway during reciprocating motion, this localized area repeatedly bears the load, making it prone to localized wear, pitting, and contact fatigue after long-term operation, resulting in a significant reduction in bearing life. This problem has become a major bottleneck restricting the long-term reliability and safety of helicopter swashplates.

[0003] To address the aforementioned problems, existing technologies have proposed some improvement solutions, but many shortcomings remain. For example, traditional methods mainly delay failure by increasing lubrication, changing materials, or increasing clearance. However, these methods can only alleviate the problem of rolling element contact fatigue to a certain extent and cannot fundamentally eliminate the localized damage caused by fixed contact areas and repeated stress. Therefore, in aerospace applications with high-frequency oscillation and high reliability requirements, traditional bearing structures are difficult to meet the needs.

[0004] Several patents have attempted innovation at the structural design level. Chinese patent application CN110864045A discloses a ball bearing with replaceable wear-resistant contact areas, which extends service life by setting detachable contact units. However, wear in this solution is still concentrated in a fixed position, making it unsuitable for the problem of cyclic loading of the rolling element contact area under small-angle reciprocating conditions. Chinese patent application CN210371629U discloses an angular contact ball bearing with an oil groove cage, proposing to create oil grooves on the cage that communicate with the ball pockets to achieve oil storage and slow-release lubrication, thereby improving lubrication durability. Although the lubrication method is improved, under small-angle, high-frequency oscillation conditions, the rolling elements are still repeatedly loaded only in the same area, without achieving dynamic migration of the contact position. Furthermore, Chinese patent application CN1549903A discloses an angular contact ball bearing and a rolling bearing, which improves resistance to fretting wear by carbonitriding the raceway and using urea-based grease. Although its wear resistance has been improved, it still has not achieved "contact point migration" from a structural mechanism perspective, and there is still a problem of local fatigue failure during small-angle oscillation.

[0005] In summary, existing spherical plain bearings generally suffer from concentrated contact areas and repeated localized stress loading, making it difficult to meet the high lifespan and high reliability requirements of helicopter automatic swashplates under high-frequency, small-angle oscillation conditions. Therefore, there is an urgent need for a novel bearing structure with structural innovation, capable of periodically migrating the rolling contact point in the circumferential direction and possessing redundant operation, to effectively extend service life and improve the overall reliability and safety of the system. Summary of the Invention

[0006] This invention provides a double-ring redundant bearing to solve existing technical problems.

[0007] To solve the above-mentioned technical problems, the technical solution proposed by this utility model is as follows:

[0008] A dual-ring redundant bearing includes an inner ring, an inner cage, a middle ring, an outer cage, and an outer ring, which are sequentially assembled from the inside to the outside. Multiple inner rolling elements are provided between the inner and middle rings, and the inner cage engages with each inner rolling element. Multiple outer rolling elements are provided between the middle and outer rings, and the outer cage engages with each outer rolling element. Multiple inner pawls are provided on the front side of the inner ring, and multiple outer pawls are provided on its rear side. Each inner and outer pawl is connected to the inner ring via an elastic element. An inner ratchet is provided on the front side of the inner cage, and the inner ratchet engages with each inner pawl. An outer ratchet is provided on the rear side of the outer cage, and the outer ratchet engages with each outer pawl and is in the opposite direction to the inner ratchet.

[0009] As a further improvement to the above technical solution:

[0010] The inner ring is provided with multiple hydraulic chambers, each hydraulic chamber is provided with a damper, the damper includes a mounting block, the mounting block is located on the side of the hydraulic chamber close to the elastic element and closes the hydraulic chamber, and each elastic element is connected to the mounting block.

[0011] The damper also includes a piston block, and a connecting rod is fixedly connected between the piston block and the mounting block. The piston block is located in the hydraulic chamber.

[0012] The piston block is provided with multiple oil guide holes, each of which extends along the extension and contraction direction of the elastic element, and the multiple oil guide holes are distributed along the circumference of the inner ring.

[0013] The elastic element includes a plurality of springs, which are distributed circumferentially along the inner ring.

[0014] The middle ring is floatingly installed between the inner ring and the outer ring.

[0015] Washers are provided on the front and outer sides of both the inner and outer rings.

[0016] The inner ring and the outer ring are provided with grooves on the front and outer sides. The inner side of the washer is fitted into the groove of the inner ring, and the outer side of the washer is fitted into the groove of the outer ring.

[0017] The number of teeth on the outer ratchet is not an integer multiple of the number of teeth on the outer pawl, the number of teeth on the inner ratchet is not an integer multiple of the number of teeth on the inner pawl, the contact state between the outer ratchet and each outer pawl is different, and the contact state between the inner ratchet and each inner pawl is different.

[0018] The inner and outer rolling elements are evenly distributed in a staggered manner on both sides of the middle ring.

[0019] Compared with the prior art, the beneficial effects of this utility model are as follows:

[0020] The structure introduces a redundant path: when one side of the roller fails and jams due to wear or fatigue, the other side of the roller can still continue to operate, thus ensuring that the bearing has basic functions under failure conditions, significantly improving the system reliability and safety of the helicopter automatic swashplate, and meeting the stringent requirements for long-term high-reliability operation of aircraft.

[0021] Multiple inner and outer pawls are provided on the front and rear sides of the inner ring, respectively, and are elastically connected to the inner ring via elastic elements. An inner ratchet is located on the front side of the inner cage, and an outer ratchet is located on the rear side of the outer cage. The inner and outer ratchets are in opposite directions to the corresponding pawls. This structure forms two unidirectional locking mechanisms in opposite directions: when the inner ring swings clockwise, the inner pawl engages with the inner ratchet, causing the inner cage to drive the inner rolling elements to rotate in one direction; while during reverse swinging, the outer pawl engages with the outer ratchet, driving the outer cage to drive the outer rolling elements to rotate in the opposite direction. Through this mechanism, only one side of the rolling elements participates in the movement each time the swing direction changes, thereby achieving periodic migration of the rolling contact point in the circumferential direction. Compared to traditional angular contact ball bearings, where the contact point remains concentrated under small-angle, high-frequency swinging, leading to increased local fatigue, this structure effectively disperses the contact load, reduces the risk of localized wear and pitting, and extends the overall bearing life.

[0022] In summary, this invention not only achieves redundant design and improves fault tolerance through inner and outer double raceways, but also realizes dynamic migration of rolling contact points through inner and outer ratchet-pawl unidirectional meshing mechanism, effectively solving the life bottleneck problem of traditional bearings under oscillating conditions. It is particularly suitable for high reliability applications such as helicopter automatic swashplates. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a schematic diagram of the cross-sectional structure of a double-ring redundant bearing;

[0025] Figure 2 This is a schematic diagram of the front structure of a double-ring redundant bearing;

[0026] Figure 3 This is a schematic diagram of the rear structure of a double-ring redundant bearing;

[0027] Figure 4 This is a perspective diagram of the internal pawl structure;

[0028] Figure 5 This is a perspective diagram of the external pawl structure;

[0029] Figure 6 This is a schematic diagram of the assembly structure of the inner pawl and the inner ratchet;

[0030] Figure 7 This is a partial structural diagram of the inner ring;

[0031] Figure 8 This is a three-dimensional structural diagram of the external cage.

[0032] Legend:

[0033] 1. Inner ring; 11. Inner pawl; 12. Outer pawl; 13. Hydraulic chamber; 2. Inner cage; 21. Inner ratchet; 3. Middle ring; 31. Inner roller; 32. Outer roller; 4. Outer cage; 41. Outer ratchet; 5. Outer ring; 6. Elastic element; 61. Spring; 7. Damper; 71. Mounting block; 72. Piston block; 721. Oil guide hole; 73. Connecting rod; 8. Washer; 81. Ring groove. Detailed Implementation

[0034] To facilitate understanding of this utility model, the following description will be provided in more comprehensive and detailed manner with reference to the accompanying drawings and preferred embodiments. However, the scope of protection of this utility model is not limited to the following specific embodiments.

[0035] Unless otherwise defined, all technical terms used herein have the same meaning as commonly understood by those skilled in the art. "Front side" refers to the side or side closer to the operator, the exterior of the equipment, or the assembly entrance; "rear side" refers to the side or side further away from the operator, closer to the machine interior, or deeper into the assembly. The technical terms used herein are for the purpose of describing particular embodiments only and are not intended to limit the scope of protection of this invention.

[0036] Unless otherwise specified, all raw materials, reagents, instruments and equipment used in this invention can be purchased from the market or prepared by existing methods.

[0037] Example: Figures 1-8 As shown, the double-ring redundant bearing of this embodiment includes an inner ring 1, an inner cage 2, a middle ring 3, an outer cage 4, and an outer ring 5, which are sequentially assembled from the inside to the outside. A plurality of inner rolling elements 31 are provided between the inner ring 1 and the middle ring 3. The inner cage 2 is engaged with each of the inner rolling elements 31. A plurality of outer rolling elements 32 are provided between the middle ring 3 and the outer ring 5. The outer cage 4 is engaged with each of the outer rolling elements 32. A plurality of inner pawls 11 are provided on the front side of the inner ring 1, and a plurality of outer pawls 12 are provided on its rear side. Each inner pawl 11 and each outer pawl 12 is connected to the inner ring 1 through an elastic element 6. An inner ratchet 21 is provided on the front side of the inner cage 2, and the inner ratchet 21 cooperates with each of the inner pawls 11. An outer ratchet 41 is provided on the rear side of the outer cage 4, and the outer ratchet 41 cooperates with each of the outer pawls 12 and is in the opposite direction to the inner ratchet 21.

[0038] This embodiment introduces a redundant path in its structure: when one side of the roller (such as the inner roller 31) fails and jams due to wear or fatigue, the other side of the roller (such as the outer roller 32) can still continue to operate, thereby ensuring that the bearing has basic functions under failure conditions, significantly improving the system reliability and safety of the helicopter automatic swashplate, and meeting the stringent requirements for long-term high-reliability operation of aircraft.

[0039] Furthermore, in this embodiment, multiple inner pawls 11 and outer pawls 12 are respectively provided on the front and rear sides of the inner ring 1, and are elastically connected to the inner ring 1 through elastic elements 6; an inner ratchet 21 is provided on the front side of the inner cage 2, and an outer ratchet 41 is provided on the rear side of the outer cage 4, with the inner and outer ratchets and the corresponding pawls in opposite directions. This structure forms two unidirectional locking mechanisms in opposite directions: when the inner ring 1 swings clockwise, the inner pawl 11 engages with the inner ratchet 21, causing the inner cage 2 to drive the inner rolling element 31 to rotate unidirectionally; while when swinging in the opposite direction, the outer pawl 12 engages with the outer ratchet 41, driving the outer cage 4 to drive the outer rolling element 32 to rotate in the opposite direction. Through this mechanism, when the bearing swings in different directions, only one side of the rolling element participates in the movement, thereby realizing the periodic migration of the rolling contact point in the circumferential direction. Compared with the problem of the contact point always being concentrated under small-angle high-frequency swing of traditional angular contact ball bearings, which leads to the aggravation of local fatigue, this structure can effectively disperse the contact load, reduce the risk of local wear and pitting, and extend the overall life of the bearing.

[0040] In summary, this embodiment not only achieves redundant design and improves fault tolerance through internal and external double raceways, but also realizes dynamic migration of rolling contact points through internal and external ratchet-pawl unidirectional meshing mechanism, effectively solving the life bottleneck problem of traditional bearings under oscillating conditions. It is particularly suitable for high reliability applications such as helicopter automatic swashplates.

[0041] The phenomenon of "periodic migration" refers to the alternating movement of the rolling elements in the circumferential direction as the number of oscillations changes: during forward oscillation, the outer rolling element migrates while the inner rolling element remains stationary; during reverse oscillation, the inner rolling element migrates while the outer rolling element remains stationary. The fundamental reason lies in the meshing relationship between the pawl and the corresponding cage ratchet: the pawl drives the cage to move, and the cage then drives the corresponding rolling element to move. Therefore, each migration of a rolling element actually corresponds to one meshing action between the cage and the pawl. It is worth noting that this migration phenomenon does not depend on a specific angle value, but is determined by the actual direction and number of oscillations. For example, when oscillating 90° forward, the outer rolling element will undergo one circumferential migration; immediately following, if oscillating 45° in the reverse direction, the outer rolling element will no longer migrate, while the inner rolling element will migrate once, thus demonstrating that the migration behavior is closely related to the direction of oscillation.

[0042] "Locking" is achieved through the interlocking shape of the pawl and the ratchet of the corresponding cage, combined with the frictional force of their contact surfaces. When the inner ring 1 rotates relative to the cage to the minimum locking stroke of the pawl, the pawl engages with the ratchet of the cage, forming a geometric interlock. Simultaneously, the frictional force causes the cage to rotate accordingly. If the rotation direction is reversed, because the teeth of the pawl are opposite, the other cage meets the engagement condition and is locked, while the previously locked cage becomes free-sliding. This design ensures that the inner and outer cages lock alternately in both forward and reverse operation, thereby achieving circumferential relocation of the contact points and guaranteeing the reliability and stability of the system.

[0043] In this embodiment, the inner ring 1 is provided with multiple hydraulic chambers 13, and each hydraulic chamber 13 is provided with a damper 7. The damper 7 includes a mounting block 71, which is located on the side of the hydraulic chamber 13 near the elastic element 6 and closes the hydraulic chamber 13. Each elastic element 6 is connected to the mounting block 71. The mounting block 71 also serves to close the hydraulic chamber. Each elastic element 6 is connected to the corresponding mounting block 71, so that the energy generated by the elastic element 6 during operation can be transferred to the hydraulic medium in the hydraulic chamber 13 through the mounting block, achieving an effective damping effect. This structure uses the slow flow of hydraulic oil in the hydraulic chamber 13 to absorb the instantaneous impact force during the engagement or release of the pawl, playing a role in vibration reduction and buffering, avoiding violent collisions between the pawl and ratchet due to frequent swinging, thereby reducing the wear of the cage, pawl, and engaging parts. Compared with the design that relies solely on the elastic element for buffering, the introduction of a damper can significantly improve the stability and durability of the locking mechanism under high-frequency reciprocating conditions. Meanwhile, the damper 7 has a compact structure and is integrated with the elastic element, making it easy to arrange in space-constrained bearing systems. It is particularly suitable for applications with high requirements for reliability and shock resistance, such as helicopter automatic swashplates.

[0044] In this embodiment, the damper 7 also includes a piston block 72, with a connecting rod 73 fixedly connected between the piston block 72 and the mounting block 71. The piston block 72 is located within the hydraulic chamber 13. When the elastic element 6 drives the pawl to move, the connecting rod 73 drives the piston block 72 to reciprocate within the hydraulic chamber 13, thereby compressing or pulling the hydraulic oil, generating flow resistance, and achieving effective damping. Through the movement of the piston block 72, the hydraulic oil must flow through a specific channel (such as a throttling orifice), thereby dissipating energy, suppressing the impact force at the moment of engagement between the pawl and the ratchet, and improving the smoothness and controllability of the locking process. Simultaneously, since the piston block 72 and the hydraulic chamber 13 form a sealed structure, the damping effect can be ensured to remain stable over a long period, unaffected by external environmental interference. This design, combining the buffering effect of the elastic element 6 with the energy dissipation advantage of hydraulic damping, can significantly reduce wear and impact loads caused by high-frequency oscillations, improve the reliability and service life of the bearing system, and is particularly suitable for scenarios with extremely high requirements for vibration and impact control, such as helicopters.

[0045] In this embodiment, the piston block 72 is provided with multiple oil guide holes 721, each extending along the extension and retraction direction of the elastic element 6, and the multiple oil guide holes 721 are distributed circumferentially along the inner ring 1. This allows the hydraulic oil in the hydraulic chamber 13 to flow axially through the oil guide holes 721 when the piston block 72 moves with the elastic element 6, thereby forming fluid damping. The circumferential distribution of multiple oil guide holes 721 along the inner ring 1 helps to achieve uniform flow of hydraulic oil in the hydraulic chamber 13, avoiding problems such as excessively high local pressure or uneven resistance. This structural design improves the response consistency of the damper 7 when engaged at different angles, and can more smoothly absorb the impact energy during the pawl engagement process. By controlling the size and number of the oil guide holes 721, the damping effect can also be flexibly adjusted to meet the usage requirements under different frequency and amplitude oscillation conditions, thereby further improving the working stability and service life of the double ring bearing in a high-frequency, small-amplitude oscillation environment.

[0046] This embodiment effectively improves lubrication reliability under high-frequency, small-angle oscillation conditions by combining single-stage grease sealing with surface engineering. Specifically, aerospace-grade synthetic grease is used to fill the contact area between the raceway and the rolling element, and solid lubricant additives are incorporated to enhance lubrication performance. Simultaneously, a wear-resistant, low-friction film is applied to the contact surface between the raceway and the rolling element to reduce friction and wear. The raceway also undergoes carbonitriding and ultra-precision grinding treatment to improve surface pitting resistance and reduce roughness, further ensuring lubrication effectiveness. Furthermore, the hydraulic oil in the hydraulic chamber 13 is in a closed environment, preventing oil leakage and frequent oil replenishment, ensuring stable operation of the damping system.

[0047] In this embodiment, the elastic element 6 includes multiple springs 61 distributed circumferentially along the inner ring 1. This allows the elastic element 6 to provide balanced elastic support around the inner ring 1, effectively buffering the relative movement of the inner pawl 11 and the outer pawl 12, thereby improving the stability and service life of the bearing.

[0048] In this embodiment, the middle ring 3 is floatingly mounted between the inner ring 1 and the outer ring 5. The middle ring 3 does not form a rigid fixed connection with the inner ring 1 and the outer ring 5; it is only indirectly supported and guided by the inner rolling elements 31 and 32. This arrangement allows the middle ring 3 to undergo slight displacement relative to the inner ring 1 and the outer ring 5 when bearing loads, avoiding the obstruction that a rigid connection might cause to the movement of the rolling elements. This effectively alleviates the relative displacement and stress concentration between the inner ring 1 and the outer ring 5, improves the bearing's adaptability and overall durability, and effectively ensures the smooth operation of the rolling elements. Simultaneously, the middle ring 3 does not directly transmit the main torque, nor does it interfere with the rotation or revolution of the rolling elements. Instead, it plays a crucial role in load distribution, motion isolation, and structural stability, thus improving the overall performance and lifespan of the bearing.

[0049] In this embodiment, washers 8 are provided on the front and outer sides of both the inner ring 1 and the outer ring 5. The washers 8 can effectively reduce friction and wear during bearing operation, protect the bearing structure, and extend service life.

[0050] In this embodiment, grooves 81 are provided on the front and outer sides of both the inner ring 1 and the outer ring 5. The inner side of the washer 8 is fitted into the groove 81 of the inner ring 1, and the outer side of the washer 8 is fitted into the groove 81 of the outer ring 5. This achieves a stable fixation of the washer 8, prevents displacement of the washer 8 during operation, and improves the sealing performance and overall stability of the bearing.

[0051] In this embodiment, the number of teeth on the outer ratchet 41 is not an integer multiple of the number of teeth on the outer pawl 12, and the number of teeth on the inner ratchet 21 is not an integer multiple of the number of teeth on the inner pawl 11. The contact states between the outer ratchet 41 and each outer pawl 12 are different, and the contact states between the inner ratchet 21 and each inner pawl 11 are also different. This enables multi-point non-uniform contact, improving the meshing reliability and torque balance of the double-ring redundant bearing, and further enhancing the bearing's vibration resistance and wear resistance. By using multiple asynchronous pawls with inconsistent contact states with the ratchet on the corresponding cage, large idle strokes are avoided, improving the unidirectional rotation efficiency of the cage and rollers. The inconsistent contact states between multiple pawls and ratchets result in differences in the stroke and time required for each pawl to lock. When the pawl with the shortest stroke reaches the locking condition first, the entire mechanism locks, avoiding the delay caused by waiting for all pawls to reach the locking state simultaneously. If the contact states between all pawls and ratchets are completely consistent, the stroke required for locking is larger, and the locking process is prone to delay. To achieve the "asynchronous ratchet" design, the number of circumferential ratchet wheels and the number of ratchet wheels must be coprime (i.e., no common factor other than 1) to ensure that the contact positions of each ratchet wheel and ratchet wheel are not repeated, thereby preventing full synchronization and improving the timeliness and reliability of locking response.

[0052] In this embodiment, the inner rolling elements 31 and outer rolling elements 32 are staggered and evenly distributed on both sides of the middle ring 3. This avoids interference between the rolling elements and achieves optimized load distribution. Simultaneously, the geometry of the inner raceway of the outer ring 5 is consistent with that of the middle ring 3, further ensuring the matching of rolling contact and manufacturing consistency. The geometric design of each structural component of the bearing is coordinated to ensure stable motion and reasonable load distribution. Both the inner cage 2 and the outer cage 4 have evenly distributed spherical pockets along the circumferential direction to limit the inner and outer rolling elements 32. Furthermore, their axial side walls are respectively provided with grooves geometrically consistent with the protruding parts of the inner pawl 11 and the outer pawl 12, ensuring reliable engagement during locking. The middle ring 3 has geometrically consistent raceways on both radial sides to ensure that the contact conditions of the inner rolling elements 31 and the outer rolling elements 32 are the same during operation, improving overall load balance. This coordinated and unified geometric design effectively improves the bearing's operational stability and lifespan under complex operating conditions.

Claims

1. A double-ring redundant bearing, characterized in that, The device comprises, from the inside out, an inner ring (1), an inner cage (2), a middle ring (3), an outer cage (4), and an outer ring (5). Multiple inner rollers (31) are provided between the inner ring (1) and the middle ring (3). The inner cage (2) engages with each inner roller (31). Multiple outer rollers (32) are provided between the middle ring (3) and the outer ring (5). The outer cage (4) engages with each outer roller (32). Multiple inner rollers are provided on the front side of the inner ring (1). Pawl (11) with multiple outer pawls (12) on its rear side. Each inner pawl (11) and each outer pawl (12) is connected to the inner ring (1) through an elastic element (6). An inner ratchet (21) is provided on the front side of the inner cage (2). The inner ratchet (21) cooperates with each inner pawl (11). An outer ratchet (41) is provided on the rear side of the outer cage (4). The outer ratchet (41) cooperates with each outer pawl (12) and is in the opposite direction to the inner ratchet (21).

2. The double-ring redundant bearing according to claim 1, characterized in that, The inner ring (1) is provided with a plurality of hydraulic chambers (13), each hydraulic chamber (13) is provided with a damper (7), the damper (7) includes a mounting block (71), the mounting block (71) is located on the side of the hydraulic chamber (13) close to the elastic element (6) and closes the hydraulic chamber (13), and each elastic element (6) is connected to the mounting block (71).

3. The double-ring redundant bearing according to claim 2, characterized in that, The damper (7) also includes a piston block (72), and a connecting rod (73) is fixedly connected between the piston block (72) and the mounting block (71). The piston block (72) is located in the hydraulic chamber (13).

4. The double-ring redundant bearing according to claim 3, characterized in that, The piston block (72) is provided with a plurality of oil guide holes (721), each of the oil guide holes (721) extending along the extension and retraction direction of the elastic member (6), and the plurality of oil guide holes (721) are distributed along the circumference of the inner ring (1).

5. The double-ring redundant bearing according to claim 4, characterized in that, The elastic element (6) includes a plurality of springs (61) distributed circumferentially along the inner ring (1).

6. The double-ring redundant bearing according to claim 1, characterized in that, The middle ring (3) is floating between the inner ring (1) and the outer ring (5).

7. The double-ring redundant bearing according to claim 1, characterized in that, Washers (8) are provided on the front and outer sides of the inner ring (1) and the outer ring (5).

8. The double-ring redundant bearing according to claim 7, characterized in that, The inner ring (1) and the outer ring (5) are provided with grooves (81) on the front and outer sides. The inner side of the washer (8) is fitted into the groove (81) of the inner ring (1), and the outer side of the washer (8) is fitted into the groove (81) of the outer ring (5).

9. The double-ring redundant bearing according to any one of claims 1-8, characterized in that, The number of teeth of the outer ratchet (41) is not an integer multiple of the number of teeth of the outer pawl (12), the number of teeth of the inner ratchet (21) is not an integer multiple of the number of teeth of the inner pawl (11), the contact state between the outer ratchet (41) and each outer pawl (12) is different, and the contact state between the inner ratchet (21) and each inner pawl (11) is different.

10. The double-ring redundant bearing according to claim 9, characterized in that, The inner rolling element (31) and the outer rolling element (32) are evenly distributed in a staggered manner on both sides of the middle ring (3).

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