Bearing with seal

Abstract

The utility model discloses a bearing with sealing element, including inner race and outer ring, be provided with the sealing element on the outer ring and be connected, be provided with the cooperation groove on the inner race, the inner race is provided with the cooperation step on one side of cooperation groove, the sealing element is provided with first baffle lip, second baffle lip and third baffle lip, the first baffle lip is in contact with the inner race edge, second baffle lip position setting corresponds cooperation groove, the third baffle lip and second baffle lip between form height difference, the third baffle lip is in contact with cooperation step, second baffle lip is by first wall, bottom wall and second wall combination constitutes, first wall sets up in one side close to first baffle lip, first wall is inclined to first baffle lip and sets up, second wall sets up in one side close to third baffle lip, second wall is inclined to third baffle lip and sets up. Its simple structure, effectively reduce temperature rise at the same time, seal stable and reliable, not prone to the problem of falling off, has good use effect.

Description

Technical Field

[0001] This utility model relates to a bearing with a sealing element. Background Technology

[0002] Bearings, as critical supporting components in mechanical equipment, are widely used in many fields such as industrial production, transportation, and aerospace. Their operational stability and service life directly affect the working performance and reliability of the entire equipment. The bearing seal structure is a core component of the bearing, its main function being to prevent internal lubricating oil leakage and to block external dust, moisture, impurities, etc., from entering the bearing, thus avoiding wear, corrosion, and jamming of critical components such as rolling elements and raceways. This is crucial for ensuring the long-term stable operation of the bearing. Existing bearing seal structures mostly adopt traditional uniform contact sealing designs, with an approximately rectangular pressure distribution on the sealing lip. The overall structure is simple, mainly relying on the large-area rigid contact between the sealing lip and the inner ring of the bearing to achieve a seal. This type of sealing lip has a wide contact bandwidth and a gentle pressure distribution. Its large contact area and high frictional torque during operation can easily lead to excessively high bearing operating temperatures, accelerating seal aging and wear, and shortening the service life of both the seal and the bearing. However, the sealing structure lacks an effective oil return design. Oil film generated by the rotation of the bearing inner ring can easily enter the sealing lip contact area, causing lubricant leakage. This not only wastes resources but also pollutes the surrounding environment. Furthermore, the existing sealing lip has uniform stiffness variation and poor dynamic tracking, making it difficult to adapt to the eccentricity and runout of the shaft during bearing operation. This can easily lead to fluctuations in the sealing gap, allowing external dust and moisture to be easily drawn in, resulting in insufficient sealing reliability. Moreover, traditional sealing structures have weak axial positioning capabilities. Under conditions of high-speed operation and vibration impact, the seal is prone to axial detachment, further damaging the sealing effect and even causing bearing failure, affecting the safe operation of the equipment. Utility Model Content

[0003] To address the shortcomings of existing technologies, this utility model provides a bearing with a sealing element. It has a simple structure, effectively reduces temperature rise, and provides a stable and reliable seal that is not prone to falling off, thus exhibiting good performance.

[0004] To achieve the above objectives, this utility model provides a bearing with a seal, including an inner ring and an outer ring. A rolling element is disposed between the inner ring and the outer ring. A seal is connected to the inner peripheral wall of the outer ring. A mating groove is disposed on the outer peripheral wall of the inner ring corresponding to the position of the seal. A mating step is disposed on the side of the mating groove near the rolling element of the inner ring. A first lip, a second lip, and a third lip are disposed sequentially from the outside to the inside of the seal near the inner ring. The first lip abuts against the edge of the inner ring. The second lip is disposed corresponding to the position of the mating groove. A height difference is formed between the third lip and the second lip. The third lip abuts against the mating step. The second lip is composed of a first wall, a bottom wall, and a second wall. The first wall is disposed on the side near the first lip and is inclined toward the first lip. The second wall is disposed on the side near the third lip and is inclined toward the third lip.

[0005] The beneficial effects of this design are as follows: By sequentially setting the first, second, and third retaining lips from the outside to the inside at one end of the seal near the inner ring, with the first retaining lip abutting against the edge of the inner ring, the second retaining lip corresponding to the mating groove, and the third retaining lip abutting against the mating step, a three-section sealing structure is formed, which realizes the zoned and controllable distribution of sealing pressure and significantly improves sealing reliability and operational stability. The first retaining lip serves as an external dust and water barrier, effectively preventing external dust, moisture, and impurities from intruding into the sealing interface and avoiding the siphoning of external contaminants into the bearing, thus reducing the risk of bearing corrosion and wear from the source. The second retaining lip, corresponding to the inner ring groove, is the core sealing lip section. Through the inclined combination structure of the first wall, bottom wall, and second wall, it forms a three-section pressure distribution of the inlet, middle, and outlet areas. The inclined surface of the inlet area can scrape off and pump excess lubricating oil back to the sealing cavity, preventing oil leakage. The middle area utilizes the inclined wall surface to form a non-linear stiffness distribution, so that the contact pressure is highly concentrated on the narrow lip, forming a stable oil film and significantly reducing frictional torque and temperature rise. The outlet area rapidly reduces pressure to form a micron-level stable lubricating film, reducing lip wear and extending the life of the seal. The third retaining lip abuts against the mating step, forming axial positioning and secondary sealing, improving the resistance to axial detachment and preventing the seal from loosening under high-speed and vibration conditions. The integrated three-section lip structure enables the seal to have multiple effects such as dust prevention, oil return, friction reduction, and positioning, solving the defects of traditional seals such as large-area contact, high friction, high temperature, easy leakage, and easy detachment. It significantly improves the bearing sealing performance, operational stability and service life, and is suitable for a wide range of operating conditions from low speed to high speed and from stationary to rotating.

[0006] As a further feature of this invention, the bottom wall is flush with the end of the first retaining lip.

[0007] The beneficial effects of this design are: with the bottom wall flush with the end of the first lip, the sealing lip end face forms a smooth transition structure, further optimizing the pressure distribution continuity and contact stability of the three-section sealing interface, and significantly improving the sealing effect and operational reliability. The bottom wall is flush with the end of the first retaining lip, ensuring no step difference between the first and second retaining lips. This makes the transition of the inclined surface in the inlet area smoother, allowing the oil film carried by the inner ring rotation to smoothly enter the inlet area of ​​the second retaining lip after passing the first retaining lip. This avoids oil film rupture, backflow obstruction, or pressure sudden changes caused by local steps, ensuring stable performance of the oil scraping and pumping return functions and effectively reducing lubricant leakage. At the same time, the flush structure makes the overall contact end face of the sealing lip more uniformly stressed, avoiding local stress concentration that could lead to early wear, deformation, or cracking of the lip, thus improving the structural strength and fatigue resistance of the seal. In addition, the smooth transition structure reduces local eddies when the sealing lip contacts the inner ring, reducing oil film disturbance and facilitating the formation of a stable and uniform fluid lubrication film in the middle area of ​​the second retaining lip. This reduces frictional resistance and operating temperature rise, and decreases the aging rate of the seal. This structure also optimizes the external dust prevention path, preventing dust and moisture from accumulating at the steps, reducing the risk of contaminant intrusion, and improving the dustproof and waterproof capabilities of the seal.

[0008] As a further feature of this invention, the first wall and the bottom wall, as well as the second wall and the bottom wall, are connected by smooth curved surfaces.

[0009] The beneficial effects of this design are as follows: The smooth curved surface connection ensures a continuous and abrupt transition between the inlet, middle, and outlet regions of the second retaining lip. The oil film formed by the inner ring's rotation flows through the lip without localized eddies or film tearing, guaranteeing smooth and efficient oil scraping and pumping return in the inlet region, and preventing oil accumulation and leakage at the turning points. The curved surface transition also results in a non-linear, gradual change in lip stiffness: slightly higher stiffness near the inlet, a sharp decrease in stiffness in the middle region, and a smooth transition in stiffness at the outlet region. This creates high flexibility in the middle region, facilitating micro-deformation of the lip under hydrodynamic pressure. This design concentrates contact pressure on an extremely narrow lip band, forming a stable micron-level lubricating film. This significantly reduces the frictional torque and operating temperature rise between the lip and the inner ring, minimizing aging and wear of the seal. Simultaneously, the smooth curved surface eliminates stress concentration points, preventing cracks, chipping, or deformation at sharp corners due to repeated compression and friction, thus improving the seal's structural strength, fatigue resistance, and service life. Furthermore, the curved surface optimizes the external dustproof path, preventing dust and moisture from accumulating at corners, reducing the risk of contaminants intruding into the sealing interface, and enhancing the seal's dustproof and waterproof capabilities.

[0010] As a further feature of this utility model, the outer ring is provided with a snap-fit ​​groove corresponding to the position of the sealing element, the sealing element is snapped in the snap-fit ​​groove, and the sealing element is also provided with a tensioning protrusion corresponding to the position of the snap-fit ​​groove.

[0011] The beneficial effects of this design are as follows: The snap-fit ​​groove provides a precise installation positioning reference for the seal, ensuring consistent installation position and preventing uneven lip contact and seal failure due to installation misalignment or tilting; the seal snaps into the snap-fit ​​groove, forming an initial axial limit and restricting axial movement; the tensioning protrusion tightly presses against the inner wall of the snap-fit ​​groove, generating radial tension force to firmly lock the seal within the groove, significantly improving its resistance to axial detachment. This effectively prevents the seal from loosening or shifting under conditions such as high-speed operation, vibration, impact, and temperature changes, avoiding seal failure, bearing oil leakage, or intrusion of external impurities.

[0012] As a further feature of this invention, a deformation groove is formed by bending the inner peripheral wall of the sealing element.

[0013] The beneficial effects of this design are as follows: With this design, the deformation groove forms an inwardly recessed cavity structure on the inner circumferential wall of the seal. Compared with traditional seals with flat inner circumferential walls, this design can effectively expand the grease storage space inside the bearing without changing the overall dimensions of the bearing or increasing the radial installation space. This allows the bearing to hold more grease, significantly increasing the initial grease injection volume, extending the grease replenishment cycle, and reducing the frequency of maintenance. Attached Figure Description

[0014] Figure 1 This is a cross-sectional structural diagram of an embodiment of the present utility model; Figure 2 This is a partial cross-sectional structural diagram of the sealing element location in an embodiment of this utility model. Detailed Implementation

[0015] Examples of embodiments of the bearing with a seal according to this invention Figures 1 to 2As shown: The ring includes an inner ring 2 and an outer ring 1. A rolling element 3 is disposed between the inner ring 2 and the outer ring 1. A sealing element 4 is disposed on the inner peripheral wall of the outer ring 1. A mating groove 21 is disposed on the outer peripheral wall of the inner ring 2 corresponding to the position of the sealing element 4. A mating step 22 is disposed on the side of the mating groove 21 near the rolling element 3 of the inner ring 2. From the outside to the inside, the sealing element 4 near the inner ring 2 has a first retaining lip 41, a second retaining lip 42, and a third retaining lip 43. The first retaining lip 41 abuts against the edge of the inner ring 2, and the second retaining lip 42... The third retaining lip 43 and the second retaining lip 42 are positioned corresponding to the mating groove 21. A height difference exists between them. The third retaining lip 43 abuts against the mating step 22. The second retaining lip 42 is composed of a first wall 421, a bottom wall 422, and a second wall 423. The first wall 421 is positioned near the first retaining lip 41 and is inclined towards it. The second wall 423 is positioned near the third retaining lip 43 and is inclined towards it. The beneficial effect of this arrangement is that by sequentially arranging the first retaining lip 41, the second retaining lip 42, and the third retaining lip 43 from the outside to the inside at the end of the seal 4 near the inner ring 2, with the first retaining lip 41 abutting against the edge of the inner ring 2, the second retaining lip 42 corresponding to the mating groove 21, and the third retaining lip 43 abutting against the mating step 22, a three-section sealing structure is formed. This achieves a zoned and controllable distribution of sealing pressure, significantly improving sealing reliability and operational stability. The first retaining lip 41 serves as an external dust and water barrier, effectively preventing external dust, moisture, and impurities from intruding into the sealing interface and avoiding the siphoning of external contaminants into the bearing, thus reducing the risk of bearing corrosion and wear from the source. The second retaining lip 42 corresponds to the inner ring 2 and fits into the groove 21, serving as the core sealing lip section. Through the inclined combination structure of the first wall 421, the bottom wall 422, and the second wall 423, it forms a three-section pressure distribution of the inlet area, the middle area, and the outlet area. The inclined surface of the inlet area can scrape off and pump excess lubricating oil back to the sealing cavity, preventing oil leakage. The middle area utilizes the inclined wall surface to form a nonlinear stiffness distribution, so that the contact pressure is highly concentrated on the narrow lip, forming a stable oil film and significantly reducing frictional torque and temperature rise. The outlet area rapidly reduces pressure to form a micron-level stable lubricating film, reducing lip wear and extending the life of the seal 4. The third retaining lip 43 abuts against the mating step 22, forming axial positioning and secondary sealing, improving the resistance to axial detachment and preventing the seal 4 from loosening under high-speed and vibration conditions. The integrated three-section lip structure enables the seal 4 to have multiple effects such as dust prevention, oil return, friction reduction, and positioning, solving the defects of traditional seals such as large-area contact, high friction, high temperature, easy leakage, and easy detachment. It significantly improves the bearing sealing performance, operational stability and service life, and is suitable for a wide range of working conditions from low speed to high speed and from stationary to rotating.

[0016] As a further feature of this embodiment, the bottom wall 422 is flush with the end of the first lip 41. The beneficial effect of this configuration is that, with the bottom wall 422 and the end of the first lip 41 flush, a smooth transition structure is formed at the lip end face of the seal 4, further optimizing the pressure distribution continuity and contact stability of the three-section sealing interface, and significantly improving the sealing effect and operational reliability. The bottom wall 422 is flush with the end of the first retaining lip 41, ensuring that there is no step difference between the first retaining lip 41 and the second retaining lip 42. This makes the transition of the inclined surface in the inlet area smoother, and the oil film carried by the rotation of the inner ring 2 can smoothly enter the inlet area of ​​the second retaining lip 42 after passing the first retaining lip 41. This avoids oil film rupture, backflow obstruction, or pressure change caused by local steps, ensuring stable performance of the oil scraping and pumping return functions and effectively reducing lubricating oil leakage. At the same time, the flush structure makes the overall contact end face of the sealing lip more uniformly stressed, avoiding local stress concentration that could lead to early wear, deformation, or cracking of the lip, and improving the structural strength and fatigue resistance of the seal 4. In addition, the flat transition structure can reduce local eddies when the sealing lip contacts the inner ring 2, reduce oil film disturbance, and facilitate the formation of a stable and uniform fluid lubrication film in the middle area of ​​the second retaining lip 42, reducing frictional resistance and operating temperature rise, and reducing the aging rate of the seal 4. This structure can also optimize the external dust prevention path, prevent dust and moisture from accumulating at the step, reduce the risk of contaminant intrusion, and improve the dustproof and waterproof capabilities of the seal 4.

[0017] As a further feature of this embodiment, the first wall 421 and the bottom wall 422, as well as the second wall 423 and the bottom wall 422, are connected by smooth curved surfaces. The advantages of this design are: the smooth curved surface connection ensures a continuous transition without abrupt changes in the inlet, middle, and outlet regions of the second lip 42; the oil film formed by the rotation of the inner ring 2 flows through the lip without localized eddies or tearing, ensuring smooth and efficient oil scraping and pumping return in the inlet region, and preventing oil accumulation and leakage at the turning points; the curved surface transition causes a non-linear gradual change in lip stiffness, with slightly higher stiffness near the inlet region, a sharp decrease in stiffness in the middle region, and a smooth transition in stiffness at the outlet region, forming a highly flexible middle region that facilitates micro-deformation of the lip under hydrodynamic pressure. This design concentrates contact pressure on an extremely narrow lip band, forming a stable micron-level lubricating film. This significantly reduces the frictional torque and operating temperature rise between the lip and the inner ring 2, minimizing aging and wear of the seal 4. Simultaneously, the smooth curved surface eliminates stress concentration points, preventing cracks, chipping, or deformation at sharp corners due to repeated compression and friction, thus improving the structural strength, fatigue resistance, and service life of the seal 4. Furthermore, the curved surface transition optimizes the external dustproof path, preventing dust and moisture from accumulating at corners, reducing the risk of contaminants intruding into the sealing interface, and enhancing the seal's dustproof and waterproof capabilities.

[0018] As a further feature of this embodiment, the outer ring 1 is provided with a snap-fit ​​groove corresponding to the position of the seal 4, and the seal 4 is snapped into the snap-fit ​​groove. A tensioning protrusion 44 is also provided on the seal 4 corresponding to the position of the snap-fit ​​groove. The beneficial effects of this design are: the snap-fit ​​groove provides a precise installation positioning reference for the seal 4, ensuring consistent installation position and preventing uneven lip contact and seal failure due to installation offset or misalignment; the seal 4 snapping into the snap-fit ​​groove forms a preliminary axial limit, restricting axial movement of the seal 4; the tensioning protrusion 44 tightly presses against the inner wall of the snap-fit ​​groove, generating radial tension force, firmly locking the seal 4 within the snap-fit ​​groove, significantly improving its resistance to axial detachment, effectively preventing the seal 4 from loosening or shifting under conditions such as high-speed operation, vibration, impact, and temperature changes, and avoiding seal failure, bearing oil leakage, or intrusion of external impurities.

[0019] As a further feature of this embodiment, a deformation groove is formed by bending the inner peripheral wall of the seal 4. The beneficial effect of this design is that the deformation groove forms an inwardly recessed cavity structure on the inner peripheral wall of the seal 4. Compared to a traditional seal 4 with a flat inner peripheral wall, this effectively expands the grease storage space inside the bearing without changing the overall dimensions of the bearing or increasing the radial installation space. This allows the bearing to hold more grease, significantly increasing the initial grease injection volume, extending the grease replenishment cycle, and reducing maintenance frequency.

[0020] The above examples are merely one preferred embodiment of this utility model. Ordinary variations and substitutions made by those skilled in the art within the scope of this utility model's technical solution are all included within the protection scope of this utility model.

Claims

1. A bearing with a seal, comprising an inner ring and an outer ring, wherein a rolling element is disposed between the inner ring and the outer ring, a seal is disposed on the inner peripheral wall of the outer ring, a mating groove is disposed on the outer peripheral wall of the inner ring corresponding to the position of the seal, and a mating step is disposed on the side of the inner ring near the rolling element of the mating groove, characterized in that: The sealing element has a first lip, a second lip, and a third lip arranged sequentially from the outside to the inside at one end near the inner ring. The first lip abuts against the edge of the inner ring, the second lip is positioned corresponding to the mating groove, and there is a height difference between the third lip and the second lip. The third lip abuts against the mating step. The second lip is composed of a first wall, a bottom wall, and a second wall. The first wall is located on the side near the first lip and is inclined toward the first lip. The second wall is located on the side near the third lip and is inclined toward the third lip.

2. The bearing with seal of claim 1, wherein: The bottom wall is flush with the end of the first retaining lip.

3. The bearing with seal of claim 1, wherein: The first wall and the bottom wall, as well as the second wall and the bottom wall, are connected by smooth curved surfaces.

4. The bearing with a seal according to claim 1, characterized in that: The outer ring is provided with a snap-fit ​​groove corresponding to the position of the seal, and the seal is snapped in the snap-fit ​​groove. The seal is also provided with a tensioning protrusion corresponding to the position of the snap-fit ​​groove.

5. The bearing with seal of claim 1, wherein: The inner peripheral wall of the seal is bent to form a deformation groove.

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