Double-row angular contact ball bearing for automatic inclinator
By adopting the design of stepped grooves, staggered vent holes, pressure relief grooves and oil filling holes in the double-row angular contact ball bearings of the automatic tilt mechanism, the problems of insufficient seal pull-out force and lubricating oil leakage are solved, and high reliability and long-life sealing performance are achieved, which is suitable for various application scenarios.
Patent Information
- Application Number
- CN202423267735.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-27
- Publication Date
- 2025-10-03
- Estimated Expiration
- 2034-12-27
AI Technical Summary
In the prior art, the double-row angular contact ball bearings of automatic tilt mechanisms are prone to problems such as insufficient seal pull-out force leading to lubricating oil leakage or severe seal wear during operation. In addition, the sealing performance is poor under extreme conditions, making it difficult to meet the requirements of high reliability and long life.
A double-row angular contact ball bearing was designed. A stepped groove was set circumferentially on the edge of the outer ring to cooperate with the clamping part and extension part of the sealing lip. Combined with the staggered vent structure, double interference sealing in the axial and radial directions was achieved. A pressure relief groove was set on the outer ring to balance the internal pressure. At the same time, a stepped groove and a folded edge structure were formed on the outer edge of the inner ring to enhance the dustproof effect. Oil filling holes were set between the raceways for easy maintenance.
It improves the sealing performance and reliability of the bearing, prevents grease leakage and external contaminants from invading, extends the service life, reduces maintenance frequency and cost, and adapts to stable operation in various application scenarios.
Smart Images
Figure CN223411254U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to a double-row angular contact ball bearing for an automatic tilter. Background Art
[0002] This double-row angular contact ball bearing is used in the automatic tilt mechanism of helicopters and features high sealing, strong reliability, simple structure, and low friction torque. It consists of an outer ring, an inner ring, steel balls, seals, a cage, and grease.
[0003] Since the helicopter automatic tilt device has a tilting moment with frequent changes in size and direction, the inner assembly consisting of the inner ring, roller, and cage of the bearing may be skewed relative to the outer ring during operation, that is, there is a certain coaxiality error between the inner and outer rings, and the actual self-aligning angle required by the bearing, which makes the structure require a large pull-out force for the seal. In addition, due to the installation requirements of the automatic tilt device bearing, the thickness of the inner and outer rings is relatively thin, and the skeleton of the seal is required to be shorter. According to conventional design, it is impossible for the seal and the outer ring to achieve a sealing structure with sufficient pull-out force and meeting the size requirements. In addition, the inner ring sealing bevel is a bevel. If the lubricating oil flows into the sealing bevel too much, the increase in the interference between the inner ring and the seal will lead to an increase in the friction torque of the bearing and severe wear of the inner ring and the seal. If the interference is not enough, the lubricating oil will easily leak. Utility Model Content
[0004] In view of the deficiencies in the prior art, the utility model provides a double-row angular contact ball bearing for an automatic tilter, which has a simple structure, a reasonable layout, is easy to use, and has good reliability.
[0005] To achieve the above-mentioned object, the utility model provides a double-row angular contact ball bearing for an automatic tilt device, comprising an inner ring and an outer ring, two rows of raceways formed between the inner ring and the outer ring, rolling bodies respectively fitted in the two rows of raceways, a step groove circumferentially provided on the edge of the outer ring, a sealing lip fitted in the step groove, the sealing lip comprising a connected clamping portion and an extension portion, the clamping portion being clamped on the step groove, the free end of the extension portion abutting against the outer wall of the inner ring, a first air vent being provided on the clamping portion along the radial direction of the outer ring, a second air vent being provided on the clamping portion along the axial direction of the outer ring, the first air vent and the second air vent being arranged alternately.
[0006] This arrangement offers the following benefits: the circumferentially arranged stepped groove along the outer ring and the corresponding sealing lip achieve a dual interference fit seal in both the axial and radial directions. The engaging portion and extended portion of the sealing lip engage the stepped groove and contact the outer wall of the inner ring, effectively enhancing the bearing's sealing performance. Furthermore, the staggered arrangement of the first vent holes radially along the outer ring and the second vent holes axially along the outer ring on the engaging portion not only improves sealing reliability but also offers the following technical benefits: First, the dual interference fit seal ensures excellent sealing performance even under extreme operating conditions, preventing grease leakage and the intrusion of external contaminants. Second, the staggered arrangement of the first and second vent holes helps balance air pressure within the bearing, preventing seal failure caused by pressure differentials. Third, this structure enhances bearing durability, extending its service life and reducing maintenance and replacement frequency. Finally, by achieving dual interference fit in both the axial and radial directions, this structure significantly improves the bearing's overall stability and operating efficiency, providing more reliable support for equipment in various application scenarios.
[0007] As a further configuration of the present invention, a skirt is provided at the edge of the outer ring corresponding to the step groove, and a pressure relief groove is formed by a depression on the contact surface between the clamping portion and the skirt.
[0008] The beneficial effect of this arrangement is that a pressure relief groove is formed by a depression on the contact surface between the clamping portion and the skirt. The structure of this pressure relief groove mainly acts to balance the internal and external pressures of the bearing. When the internal pressure of the bearing increases due to temperature rise or other factors during operation, the pressure relief groove can effectively alleviate this pressure difference, allowing the excess gas inside to be discharged through the pressure relief groove, thereby avoiding seal damage or bearing failure caused by excessive pressure. In addition, the presence of the pressure relief groove can also ensure that when the bearing is running at high speed or under impact load, the fluctuation of internal pressure is released in time, maintaining the stability of the internal environment of the bearing and improving the reliability and durability of the bearing. At the same time, this design also takes into account the convenience of maintenance. Through the reasonable setting of the pressure relief groove, the frequent maintenance caused by pressure imbalance is reduced, the service life of the bearing is extended, and the operating costs of users are reduced.
[0009] As a further configuration of the present invention, a stepped groove is formed on the outer edge of the inner ring, and a folded edge is formed on the free end of the extension portion, and the folded edge abuts against the side wall of the stepped groove.
[0010] This advantageous arrangement combines the stepped groove formed on the outer edge of the inner ring with the folded edge formed at the free end of the extension to enhance dust protection. The folded edge abuts against the sidewalls of the stepped groove, forming an additional physical barrier that effectively prevents external dust and particulate matter from entering the bearing through the sealing gap. This structure not only improves sealing performance, effectively preventing the intrusion of dust and other hard particles even in harsh operating environments, but also enhances protection, protecting the grease and rolling elements within the bearing and extending its service life. Furthermore, this design simplifies maintenance. The enhanced dust protection maintains bearing internal cleanliness, reducing wear and grease contamination caused by dust, thereby reducing maintenance frequency and difficulty. Furthermore, this structure improves bearing reliability, reduces failures and downtime caused by dust intrusion, and offers high adaptability, making it suitable for a variety of bearing configurations and providing effective dust protection in both low-speed, heavy-load and high-speed, light-load applications. It also extends lubrication intervals, reduces the number of grease changes, and saves costs. By reducing the frequency of maintenance and component replacement, it helps lower overall operating costs and improves economic efficiency.
[0011] As a further configuration of the present invention, a skeleton is provided in the sealing lip, and the skeleton includes a radial portion provided along the radial direction of the outer ring and an axial portion provided along the axial direction of the outer ring, the clamping portion is connected to the axial portion, the extension portion is connected to the radial portion, and the folding edge connection is provided at the end of the radial portion.
[0012] This design offers the following benefits: By providing a framework within the sealing lip, comprising a radial portion extending radially along the outer ring and an axial portion extending axially along the outer ring, a snap-fit portion connected to the axial portion, an extension portion connected to the radial portion, and a flanged edge at the end of the radial portion, the seal significantly enhances its structural strength. This not only improves sealing performance, ensuring reliable sealing under high pressure or high-speed rotation, and preventing lubricant leakage and external contaminants, but also enhances wear resistance and extends the seal's service life. Furthermore, the framework helps maintain the sealing lip's dimensional stability, improves fatigue resistance, and facilitates installation and removal. Furthermore, the framework absorbs and disperses external impact forces, optimizing load distribution and preventing excessive compression, thereby improving impact resistance and overall structural reliability. These features enable the sealing lip to adapt to equipment of varying sizes and specifications, expanding its application range. This reduces equipment downtime and repairs due to seal failure, lowering maintenance costs and providing a strong guarantee for stable equipment operation.
[0013] As a further configuration of the present invention, an oil filling hole is provided between two corresponding rows of raceways on the outer ring, and a plug is fitted on the oil filling hole.
[0014] The beneficial effects of this arrangement are: this arrangement improves maintenance efficiency: by arranging an oil filling hole between the two rows of raceways, the lubricating oil can be directly injected into the parts that need lubrication, which greatly simplifies the maintenance process and improves maintenance efficiency. At the same time, regular and convenient oiling can ensure that the equipment operates under good lubrication conditions, effectively reduce wear and extend the service life of the equipment; the design position of the oil filling hole can ensure that the lubricating oil is evenly distributed between the raceways, avoiding local wear caused by uneven lubrication; further combined with the oil filling hole design of the plug body, the oil circuit can be effectively closed during non-oiling period to prevent dust, impurities, etc. from entering, reducing the risk of oil contamination. BRIEF DESCRIPTION OF THE DRAWINGS
[0015] Figure 1 This is a schematic structural diagram of an embodiment of the present utility model;
[0016] Figure 2 This is a partial enlarged view of the sealing lip position in the embodiment of the present utility model. DETAILED DESCRIPTION
[0017] The utility model provides an embodiment of a double-row angular contact ball bearing for an automatic tilt device, such as Figures 1 to 2As shown, the inner ring 1 and outer ring 2 are formed with two rows of raceways between them, each equipped with a rolling element 3. A stepped groove 22 is circumferentially provided along the edge of the outer ring 2, and a sealing lip 4 is provided within the stepped groove 22. The sealing lip 4 comprises a connected clamping portion 41 and an extension portion 42. The clamping portion 41 is secured to the stepped groove 22, and the free end of the extension portion 42 abuts against the outer wall of the inner ring 1. The clamping portion 41 is provided with a first vent hole 411 radially along the outer ring 2, and a second vent hole 412 axially along the outer ring 2. The first vent hole 411 and the second vent hole 412 are arranged alternately. This arrangement has the beneficial effect of achieving a dual interference seal in both the axial and radial directions with the stepped groove 22 provided along the circumferential edge of the outer ring 2 and the sealing lip 4 provided therewith. The clamping portion 41 and extension portion 42 of the sealing lip 4 are respectively secured to the stepped groove 22 and abut against the outer wall of the inner ring 1, effectively enhancing the bearing's sealing performance. Furthermore, the staggered arrangement of first vent holes 411 radially disposed along the outer ring 2 and second vent holes 412 axially disposed along the outer ring 2 on the clamping portion 41 not only improves sealing reliability but also provides the following technical benefits: First, the double-interference sealing design ensures excellent sealing performance even under extreme operating conditions, preventing grease leakage and the intrusion of external contaminants. Second, the staggered arrangement of first and second vent holes 411, 412 helps balance the air pressure within the bearing, preventing seal failure due to pressure differences. Third, this structure improves the bearing's durability, extends its service life, and reduces the frequency of maintenance and replacement. Finally, by achieving dual axial and radial interference fits, this structure significantly enhances the bearing's overall stability and operating efficiency, providing more reliable support for equipment in various application scenarios.
[0018] As a further feature of this embodiment, the outer ring 2 is provided with a skirt 23 along the edge corresponding to the stepped groove 22. A pressure relief groove 413 is formed as a recessed depression on the contact surface between the clamping portion 41 and the skirt 23. This advantageous feature provides the following: The pressure relief groove 413 is formed by the recessed depression on the contact surface between the clamping portion 41 and the skirt 23. This pressure relief groove 413 primarily balances the internal and external pressures of the bearing. When the bearing's internal pressure increases during operation due to temperature rise or other factors, the pressure relief groove 413 effectively mitigates this pressure differential, allowing excess gas to escape through the groove 413, thereby preventing seal damage or bearing failure caused by excessive pressure. Furthermore, the presence of the pressure relief groove 413 ensures that internal pressure fluctuations are promptly relieved during high-speed operation or when subjected to impact loads, maintaining a stable internal environment and improving the bearing's reliability and durability. This design also takes maintenance convenience into account. The rational placement of the pressure relief groove 413 reduces the need for frequent maintenance due to pressure imbalance, extending the bearing's service life and reducing operating costs for users.
[0019] As a further feature of this embodiment, a stepped groove 11 is formed on the outer edge of the inner ring 1, and a folded edge 421 is formed at the free end of the extension 42. The folded edge 421 abuts against the sidewalls of the stepped groove 11. This advantageous arrangement enhances dust protection by combining the stepped groove 11 formed on the outer edge of the inner ring 1 with the folded edge 421 formed at the free end of the extension 42. The folded edge 421 abuts against the sidewalls of the stepped groove 11, forming an additional physical barrier that effectively prevents external dust and particulate matter from entering the bearing through the sealing gap. This structure not only improves sealing performance, effectively preventing the intrusion of dust and other hard particles even in harsh operating environments, but also enhances protection, protecting the grease and rolling elements within the bearing and extending the bearing's service life. Furthermore, this design simplifies maintenance. Due to the improved dust protection, the cleanliness of the bearing interior is maintained, reducing wear and grease contamination caused by dust, thereby reducing maintenance frequency and difficulty. Furthermore, this structure improves bearing reliability, reduces failures and downtime caused by dust intrusion, and offers strong adaptability for a variety of bearing configurations, providing effective dust protection in both low-speed, heavy-load and high-speed, light-load applications. It also extends lubrication cycles, reduces the need for grease changes, and saves costs. By reducing the frequency of maintenance and component replacement, it helps lower overall operating costs and improves economic benefits.
[0020] As a further feature of this embodiment, the sealing lip 4 is provided with a framework 5. This framework 5 comprises a radial portion 52 extending radially along the outer ring 2 and an axial portion 51 extending axially along the outer ring 2. The engaging portion 41 is connected to the axial portion 51, the extending portion 42 is connected to the radial portion 52, and the flange 421 is connected to the end of the radial portion 52. This advantageous feature is that the framework 5, comprising the radial portion 52 extending radially along the outer ring 2 and the axial portion 51 extending axially along the outer ring 2, the engaging portion 41 being connected to the axial portion 51, the extending portion 42 being connected to the radial portion 52, and the flange 421 at the end of the radial portion 52, significantly enhances the structural strength of the seal. This not only improves sealing performance, ensuring reliable sealing under high pressure or high-speed rotation, preventing lubricant leakage and external contaminants, but also enhances wear resistance and extends the service life of the seal. Furthermore, the framework 5 helps maintain the shape stability of the sealing lip 4, improves fatigue resistance, and facilitates installation and removal. Furthermore, the skeleton 5 structure absorbs and disperses external impact forces, optimizing load distribution and preventing excessive compression, thereby enhancing impact resistance and overall structural reliability. These designs allow the sealing lip 4 to adapt to equipment of varying sizes and specifications, expanding its application range. This reduces equipment downtime and repairs due to seal failure, lowering maintenance costs and providing a strong guarantee for stable equipment operation.
[0021] As a further feature of this embodiment, an oil filling hole 21 is provided between the two corresponding rows of raceways on the outer ring 2, and a plug is provided on the oil filling hole 21. This configuration has the following beneficial effects: It improves maintenance efficiency: by providing the oil filling hole 21 between the two rows of raceways, lubricating oil can be directly injected into the area requiring lubrication, greatly simplifying the maintenance process and improving maintenance efficiency. Regular and convenient oiling ensures that the equipment operates under good lubrication conditions, effectively reducing wear and extending the service life of the equipment. The design position of the oil filling hole 21 ensures that the lubricating oil is evenly distributed between the raceways, avoiding localized wear caused by uneven lubrication. Furthermore, the design of the oil filling hole 21 in conjunction with the plug effectively seals the oil circuit during non-oiling periods, preventing the ingress of dust, impurities, etc., and reducing the risk of oil contamination.
[0022] The above example is only one preferred specific example of the present invention. Common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included in the protection scope of the present invention.
Claims
1. A double-row angular contact ball bearing for an automatic tilt mechanism, comprising an inner ring and an outer ring, two rows of raceways formed between the inner and outer rings, each of the two rows of raceways being equipped with rolling elements, characterized in that: The outer ring edge is provided with a step groove along the circumferential direction, and a sealing lip is fitted in the step groove. The sealing lip includes a clamping portion and an extension portion that are connected. The clamping portion is clamped on the step groove, and the free end of the extension portion abuts against the outer wall of the inner ring. A first air vent is provided on the clamping portion along the radial direction of the outer ring, and a second air vent is provided on the clamping portion along the axial direction of the outer ring. The first air vent and the second air vent are staggered.
2. The double-row angular contact ball bearing for an automatic recliner according to claim 1, characterized in that: The outer ring is provided with a skirt at an edge corresponding to the step groove, and a pressure relief groove is formed by a depression on the contact surface between the clamping portion and the skirt.
3. The double-row angular contact ball bearing for an automatic recliner according to claim 2, characterized in that: A stepped groove is formed on the outer edge of the inner ring, and a folded edge is formed on the free end of the extension portion, and the folded edge abuts against the side wall of the stepped groove.
4. The double-row angular contact ball bearing for an automatic recliner according to claim 3, characterized in that: A skeleton is provided in the sealing lip, and the skeleton includes a radial portion provided along the radial direction of the outer ring and an axial portion provided along the axial direction of the outer ring. The clamping portion is connected to the axial portion, the extending portion is connected to the radial portion, and the folding edge is provided at the end of the radial portion.
5. The double-row angular contact ball bearing for an automatic recliner according to claim 1, characterized in that: An oil filling hole is provided between two corresponding rows of raceways on the outer ring, and a plug body is matched with the oil filling hole.