Ring-running-preventing bearing and butt joint structure thereof

Abstract

The utility model discloses an anti-running bearing and a butt joint structure thereof, the anti-running bearing comprises a bearing inner ring and a bearing outer ring, the bearing inner ring is rotatably arranged in the bearing outer ring through a rolling assembly, and the section of the inner surface of the bearing inner ring and / or the section of the outer surface of the bearing outer ring are / is a non-rotary outline. The non-rotary body outline is adopted as the butt joint face of the bearing and the inner ring supporting piece or the outer ring supporting piece, so that the inner ring supporting piece or the outer ring supporting piece and the bearing cannot slide in the circumferential direction, and circumferential ring running of the bearing is prevented. Through rigid matching of the non-rotation contour, the possibility of circumferential sliding between the bearing and the supporting piece is physically blocked, and the running risk is eliminated from the source. And compared with the traditional anti-skidding method which only adopts interference fit and purely depends on friction force, geometric constraint is not invalid due to lubrication failure or surface abrasion, and the reliability is obviously improved.

Description

Technical Field

[0001] This utility model relates to an anti-runaway bearing and its mating structure, belonging to the field of bearing technology. Background Technology

[0002] Bearings are indispensable key components in mechanical equipment, widely used in various rotating machinery such as motors, gearboxes, pumps, and fans. Their main function is to support the inner ring of the bearing, reduce friction, and ensure smooth operation of the equipment. However, bearings may experience various failure modes during operation, among which "ring runaway" is a common and serious failure mode.

[0003] Bearing race slippage refers to the phenomenon where the inner or outer ring of a bearing slides relative to the shaft or bearing housing, leading to wear on the mating surfaces. Race slippage is usually caused by factors such as an excessively loose fit, uneven load, vibration, or impact loads. Once race slippage occurs, the mating surfaces between the inner or outer ring of the bearing and the shaft or bearing housing will gradually wear, causing the clearance to increase further, thus accelerating bearing wear and failure. Race slippage not only reduces the bearing's operating accuracy but also causes equipment vibration, increased noise, and even equipment downtime, seriously affecting the reliability and service life of the equipment.

[0004] To prevent bearing race slippage, keyed connections are traditionally used. This involves installing a key between the shaft and the inner ring of the bearing, or between the bearing housing and the outer ring, to increase friction between the mating surfaces and prevent relative sliding. However, keyed connections have several drawbacks: the presence of a keyway can create stress concentration on the shaft or bearing housing, especially under high or alternating loads. This can easily lead to material fatigue around the keyway, even cracking, and ultimately, more serious failure. Furthermore, the installation process for keyed connections is complex, requiring precise machining of the keyway and ensuring a precise fit between the key and keyway during installation; otherwise, the bearing's performance will be affected. Utility Model Content

[0005] The purpose of this utility model is to address the aforementioned problems, specifically the stress concentration and complex installation and maintenance issues associated with traditional keyed connections, by providing an anti-runaway bearing and its mating structure. This structure ensures a secure fit between the bearing and the shaft or bearing housing while preventing stress concentration, simplifying installation and maintenance, and improving the bearing's reliability and service life.

[0006] The technical solution adopted in this utility model is as follows:

[0007] An anti-running bearing includes an inner bearing ring and an outer bearing ring. The inner bearing ring is rotatably disposed within the outer bearing ring via a rolling assembly. The inner surface of the inner bearing ring and / or the outer surface of the outer bearing ring have a non-rotational profile.

[0008] Alternatively, the inner surface of the bearing inner ring and / or the outer surface of the bearing outer ring may be a rotationally symmetric shape.

[0009] Alternatively, the inner surface of the bearing inner ring and / or the outer surface of the bearing outer ring may be composed of two circular arcs and two straight lines symmetrical about 180° along the axis of rotation, with the center of the circular arcs being the axis of rotation.

[0010] Alternatively, the inner surface of the bearing inner ring and / or the outer surface of the bearing outer ring may have a regular polygonal cross-section.

[0011] Alternatively, the corners of the regular polygon may have rounded corners.

[0012] Alternatively, the inner surface of the bearing inner ring and / or the outer surface of the bearing outer ring may be covered with an anti-slip layer.

[0013] Alternatively, the anti-slip layer may be a galvanized layer.

[0014] A mating structure for an anti-runaway bearing includes the anti-runaway bearing as described above, wherein an inner ring support is provided inside the anti-runaway bearing, and the mating surfaces of the bearing inner ring and the inner ring support are both non-rotational contours; and / or, an outer ring support is sleeved on the outside of the anti-runaway bearing, and the mating surfaces of the bearing outer ring and the outer ring support are both non-rotational contours.

[0015] Alternatively, the bearing inner ring and the inner ring support are interference fits; and / or, the bearing outer ring and the outer ring support are interference fits.

[0016] Alternatively, the outer surface of the inner ring support and / or the inner surface of the outer ring support may be covered with an anti-slip layer.

[0017] In summary, due to the adoption of the above technical solution, the beneficial effects of this utility model are:

[0018] 1. The anti-slip bearing and its mating structure provided by this utility model, through the rigid matching of a non-rotational contour, physically blocks the possibility of circumferential sliding between the bearing and the support, eliminating the risk of slippage at the source. Compared with the traditional method that only uses interference fit and relies solely on friction for anti-slip, the geometric constraints do not fail due to lubrication failure or surface wear, significantly improving reliability.

[0019] 2. The anti-running bearing and its mating structure provided by this utility model feature a symmetrical, non-rotating profile that evenly distributes the load across multiple contact surfaces, avoiding stress concentration in keyways or single-point contacts and significantly reducing the risk of fatigue cracking. No keyways are required between the shaft and bearing housing, maintaining material continuity and improving bending and torsional stiffness, making it suitable for high-load or impact conditions. The manufacturing process is simple, requiring no additional mating parts during assembly, and allowing for rapid alignment of multiple installation angles, reducing assembly accuracy requirements and shortening processing time.

[0020] 3. The anti-running bearing and its mating structure provided by this utility model provide radial compressive stress through interference fit, ensuring tight fit between the bearing and the support, bearing radial load and compensating for small gaps in the profile surface, suppressing the loosening tendency caused by vibration, rather than the rigid limiting of the non-rotating profile to absorb impact energy. The combination of the two forms a damping-limiting double barrier. Attached Figure Description

[0021] Figure 1 This is an assembly diagram of the present invention.

[0022] Figure 2 yes Figure 1 Enlarged view of point I.

[0023] The markings in the diagram are: 1-anti-running bearing, 11-bearing inner ring, 12-bearing outer ring, 2-inner ring support, 3-outer ring support. Detailed Implementation

[0024] The present invention will now be described in detail with reference to the accompanying drawings.

[0025] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this utility model and are not intended to limit this utility model.

[0026] A type of anti-running bearing, such as Figure 1 , 2 As shown, the bearing includes an inner ring 11 and an outer ring 12. The inner ring 11 is rotatably disposed within the outer ring 12 via a rolling assembly. The inner surface of the inner ring 11 and / or the outer surface of the outer ring 12 have a non-rotational profile.

[0027] This solution uses a non-rotational body contour as the mating surface between the bearing and the inner ring support 2 or outer ring support 3. This contour can be a non-cylindrical shape, such as a polygon, ellipse, or incomplete cylindrical surface. Through geometric constraints, the circumferential relative movement between the bearing's inner ring 11 or outer ring and the support is forcibly restricted. Since the non-rotational body lacks rotational symmetry, when the two are mated, they can only perfectly match at a specific angle. Any attempt at circumferential sliding will be physically prevented due to shape interference, thus completely eliminating the "runaway" phenomenon. Furthermore, when the non-rotational body contour uses multiple limiting parts, the shear force during torque transmission can be evenly distributed across multiple contact surfaces, reducing the load per unit area and significantly reducing the risk of material fatigue. Compared to the concentrated load of traditional keyed connections, it significantly reduces local stress peaks and the risk of stress concentration. It also avoids machining keyways on the shaft or bearing housing, maintaining the integrity of the shaft system structure, improving overall rigidity and resistance to bending and torsion, and simplifying installation. The inner ring support 2 can be a rotating shaft or other structure, and the outer ring support 3 can be a bearing housing or other structure. Specifically, the inner ring 11 of the bearing adopts a non-rotational symmetrical contour such as a polygon, ellipse, or non-complete circle, forming a geometric interlock when mated with the inner ring support 2. The outer ring 12 of the bearing has the same or different non-rotational shape, and achieves circumferential limiting when mated with the bearing housing. Non-rotational contours can be applied to the inner ring 11 or the outer ring 12 of the bearing alone, or they can be used on both the inner and outer rings simultaneously. Due to the shape limitations, the mating surfaces of the non-rotational contour and the shaft / bearing housing cannot rotate relative to each other. Any circumferential displacement will be forcibly interfered with by the contour edge, physically eliminating the possibility of ring slippage.

[0028] In another specific implementation, the inner surface of the bearing inner ring 11 and / or the outer surface of the bearing outer ring 12 are rotationally symmetric cross-sections. A rotationally symmetric shape is one whose shape coincides after rotating about an axis by a specific angle, and is not circular. It achieves anti-runaway function through periodic geometric features, such as regular polygons, involute splines, or flower-like shapes. The rotationally symmetric profile transmits torque through symmetrically distributed contact edges, with each edge bearing equal shear force. Each contact surface alternately bears the maximum stress, mitigating local fatigue accumulation and avoiding the risk of eccentric loading caused by unilateral force on asymmetrical profiles. Furthermore, when the rotationally symmetric profile is combined with an interference fit, the radial compressive stress is uniformly distributed along the tooth side, reducing the peak contact stress compared to the local high-pressure areas of an asymmetrical profile. In addition, the rotationally symmetric structure allows for rapid alignment at multiple angles, significantly reducing adjustment time.

[0029] In another specific embodiment, the inner surface of the bearing inner ring 11 and / or the outer surface of the bearing outer ring 12 are composed of two circular arcs and two straight lines symmetrically arranged 180° along the axis of rotation, with the axis of rotation as the center of the circular arcs. The circular arcs, centered on the axis of rotation, form continuous contact with the shaft or bearing housing, and the radial load is evenly distributed along the arc surface, avoiding stress concentration at point contact. The straight lines provide axially symmetrical planar contact, dispersing shear force to both sides when transmitting circumferential torque, resulting in higher torsional efficiency. The 180° symmetry allows for quick alignment in two symmetrical positions, reducing assembly accuracy requirements. The cross-section in this design can be obtained by directly machining two opposing planes on the shaft, resulting in lower process complexity and easier machining.

[0030] In another specific implementation, the inner surface of the bearing inner ring 11 and / or the outer surface of the bearing outer ring 12 are regular polygons. Each side and angle of the regular polygon is equal, ensuring that torque and load are evenly distributed across multiple symmetrical contact surfaces. The number of sides can be selected according to different operating conditions. For example, in high-torque scenarios, a shape with more sides is used, resulting in more contact surfaces and thus a smaller unit load. In compact spaces, a shape with fewer sides is used, resulting in a compact structure and smaller radial dimensions. Furthermore, compared to shapes with concave and convex portions such as splines, the sides of a regular polygon are flat surfaces, ensuring that contact pressure is evenly distributed along the edges and that each edge bears the load equally. In contrast, splines are prone to stress concentration at the tooth root due to geometric abrupt changes, and pitch errors can easily lead to off-center loading. From an economic perspective, regular polygons can be machined using general-purpose machine tools, and the fit accuracy can be controlled by adjusting the side distances. In contrast, involute splines require specialized hobs or gear shapers to strictly guarantee tooth profile tolerances. Furthermore, considering the interference fit between the bearing and the inner ring support 2 or the outer ring support 3, when the flat surface of the regular polygon is combined with the interference fit, the radial pressure is continuously distributed along the entire edge. The pressure per unit area is lower than that of concentrated clamping at the top of the spline tooth, reducing the risk of fretting wear. Moreover, the problem of easy plastic deformation of the tooth top is avoided by multi-sided load distribution.

[0031] As another specific implementation, the corners of the regular polygon are rounded. Rounded corners replace sharp edges, avoiding sudden increases in local stress caused by abrupt changes in the contour, thus suppressing the risk of crack initiation at its source. The rounded corners form natural guide slopes, guiding the shaft and the inner ring 11 of the bearing, or the bearing housing and the outer ring, to quickly align during assembly, reducing surface scratches caused by misalignment.

[0032] In another specific embodiment, the inner surface of the bearing inner ring 11 and / or the outer surface of the bearing outer ring 12 are covered with an anti-slip layer. The anti-slip layer increases the static friction coefficient by improving the micro-roughness of the contact surface, forming triple protection with the geometric interlocking of the regular polygon and the radial clamping force of the interference fit. Simultaneously, its own wear-resistant properties protect the substrate surface and extend the service life of the bearing and shaft or bearing housing.

[0033] In another specific implementation, the anti-slip layer is a zinc-plated layer. The fine texture formed during the zinc layer's crystallization process increases the coefficient of friction on the contact surface, and works in conjunction with the geometric interlocking design to suppress circumferential slippage.

[0034] As an assembly form of the above structure, a mating structure for an anti-running bearing 1 includes the anti-running bearing 1 as described above, wherein an inner ring support 2 is provided inside the anti-running bearing 1, and the mating surfaces of the bearing inner ring 11 and the inner ring support 2 are both non-rotating contours; and / or, an outer ring support 3 is sleeved on the outside of the anti-running bearing 1, and the mating surfaces of the bearing outer ring 12 and the outer ring support 3 are both non-rotating contours. The edges of the non-rotating contours must exist simultaneously on both the bearing and the support. Only when the contour shapes are perfectly matched can the two achieve circumferential limiting through mechanical interference of the corners or tooth surfaces, and evenly distribute the torque to multiple contact areas, avoiding local stress concentration caused by unilateral non-rotation. The double non-rotating contours form a rigid connection through multi-sided contact, and under dynamic loads, each contact surface alternately shares the impact energy; while unilateral non-rotation, because the other side is a rotating surface, is prone to fretting wear during vibration, reducing stability.

[0035] In another specific implementation, the inner ring 11 of the bearing and the inner ring support 2 are interference-fitted; and / or, the outer ring 12 of the bearing and the outer ring support 3 are interference-fitted. The preload of the interference fit and the geometric locking of the non-rotating body profile jointly suppress the microscopic relative sliding between the bearing and the shaft, thereby reducing fretting wear and extending the life of the mating surfaces. Furthermore, the clamping force of the interference fit combined with the elastic deformation of the contact surface of the non-rotating body profile can absorb high-frequency vibration energy and reduce the risk of resonance. Under sudden impact loads, the geometric interlocking of the non-rotating body profile can share some of the shear force, while the clamping force of the interference fit provides instantaneous frictional resistance, forming a dual protection mechanism. In addition, the non-rotating body profile is responsible for transmitting circumferential torque, while the radial pressure of the interference fit bears the radial load. The two work together to avoid stress concentration caused by the coupling effect of circumferential shear force and radial compressive stress in traditional keyed connections. Furthermore, if the bearing uses an elastic material, even if the original interference fit fails and causes bearing displacement, the contact surfaces may spring back together, generating localized compressive stress and forming a dynamic interference. The material's elasticity allows adjacent bearing sides to press against the shaft surface again. When interference fits are used throughout, the structural rigidity of the entire bearing system is significantly enhanced, the relative positions between components are more stable, and wobbling and vibration caused by looseness or clearance are reduced. Moreover, interference fits can effectively transfer loads, allowing the load to be evenly distributed across the support components when the bearing is subjected to impact loads, rather than being concentrated on the bearing itself, thus improving the bearing's reliability and service life under high-impact conditions.

[0036] As another specific implementation, the outer surface of the inner ring support 2 and / or the inner surface of the outer ring support 3 are covered with an anti-slip layer. When the anti-slip layer covers both the bearing and the outer surfaces of the inner ring support 2 and the outer ring support 3, the relative movement of the inner and outer rings is more comprehensively constrained during operation. This multi-point anti-slip design can effectively reduce bearing position shift or wobbling caused by local slippage, thereby significantly improving the stability of the entire bearing system. Optionally, the anti-slip layers of the bearing, inner ring support 2, and outer ring support 3 are made of the same material. Under the same operating conditions, their wear and aging rates are more similar, thus ensuring a more uniform service life for the entire bearing system and reducing system failures caused by local anti-slip layer failure. Furthermore, it ensures that the anti-slip layers work synergistically throughout the system, avoiding performance inconsistencies due to material differences.

[0037] The above description is merely a preferred embodiment of the present utility model and is not intended to limit the present utility model. The present utility model extends to any new features or combinations disclosed in this specification, and any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model. It is obvious to those skilled in the art that the present utility model is not limited to the details of the above exemplary embodiments, and that detailed technical features not disclosed in this embodiment, such as specific structures, are all prior art and can be obtained by those skilled in the art from the prior art; the connection method can be a fixed connection, a detachable connection, or an integral part; it can be a fixed connection, a movable connection, or a hinged connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific manner of the above terms in the embodiments of the present utility model according to the specific circumstances, and the present disclosure does not specifically limit this aspect.

Claims

1. A raceway preventing bearing and its interfacing structure, characterized by: It includes an inner bearing ring (11) and an outer bearing ring (12). The inner bearing ring (11) is rotatably disposed inside the outer bearing ring (12) via a rolling assembly. The inner surface of the inner bearing ring (11) and / or the outer surface of the outer bearing ring (12) have a non-rotational profile.

2. The anti-runout bearing of claim 1, wherein: The inner surface of the bearing inner ring (11) and / or the outer surface of the bearing outer ring (12) are rotationally symmetric.

3. The anti-runout bearing of claim 2, wherein: The inner surface of the bearing inner ring (11) and / or the outer surface of the bearing outer ring (12) are composed of two circular arcs and two straight lines symmetrical about the axis of rotation at 180°, and the center of the circular arc is the axis of rotation.

4. The anti-runout bearing of claim 3, wherein: The inner surface of the bearing inner ring (11) and / or the outer surface of the bearing outer ring (12) have a regular polygonal cross section.

5. The anti-runout bearing of claim 4, wherein: The corners of the regular polygon are rounded.

6. The anti-runout bearing of claim 1, wherein: The inner surface of the bearing inner ring (11) and / or the outer surface of the bearing outer ring (12) are covered with an anti-slip layer.

7. The anti-runout bearing of claim 6, wherein: The anti-slip layer is a galvanized layer.

8. A butt joint structure of a raceway-escape preventing bearing, characterized by: The bearing includes an anti-runaway bearing (1) as described in any one of claims 1-7, wherein an inner ring support (2) is provided inside the bearing (1), and the mating surfaces of the bearing inner ring (11) and the inner ring support (2) are both non-rotational contours; and / or, an outer ring support (3) is sleeved on the outside of the anti-runaway bearing (1), and the mating surfaces of the bearing outer ring (12) and the outer ring support (3) are both non-rotational contours.

9. The abutment structure of the raceway preventing bearing according to claim 8, wherein: The inner ring (11) of the bearing and the inner ring support (2) are interference fits; and / or, the outer ring (12) of the bearing and the outer ring support (3) are interference fits.

10. The abutment structure of the raceway preventing bearing according to claim 8, wherein: The outer surface of the inner ring support (2) and / or the inner surface of the outer ring support (3) are covered with an anti-slip layer.

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