High-temperature-resistant full-complement angular contact ball bearing for aero-engine

Abstract

The utility model discloses a high temperature resistant full complement angular contact ball bearing for aero-engines, which relates to the technical field of bearings and comprises an inner ring, an outer ring and a steel ball, an outer groove is concavely arranged on the inner wall of the outer ring, an inner groove is concavely arranged on the outer wall of the inner ring, the outer ring is sleeved outside the inner ring, the inner groove and the outer groove jointly form an annularly extending raceway, and the steel ball is positioned in the raceway. The multiple steel balls are arranged in the raceway in a circumferential array mode around the axis of the inner ring and are fully distributed in the raceway, a first flange and a second flange are formed in the positions, on the two sides of the outer groove, of the inner wall of the outer ring respectively, a third flange and a fourth flange are formed in the positions, on the two sides of the inner groove, of the outer wall of the inner ring respectively, and the first flange and the third flange are arranged on one side of the steel balls. The second flange and the fourth flange are arranged on the other side of the steel ball, and the distance between the first flange and the third flange is larger than that between the second flange and the fourth flange. According to the utility model, the steel balls are distributed between the outer ring and the inner ring, so that the bearing capacity is greatly improved.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and in particular to a high-temperature resistant full complement angular contact ball bearing for aero engines. Background Technology

[0002] Existing angular contact ball bearings generally include an outer ring and an inner ring, with steel balls and a cage between them. The inner wall of the outer ring and the outer wall of the inner ring have external grooves and internal grooves, respectively. The steel balls are placed within these external and internal grooves. The cage guides the movement of the steel balls, maintaining a uniform spacing between them. However, in situations where bearing installation space is limited, more steel balls cannot be placed within the limited internal space of the bearing, thus affecting the bearing's load-bearing capacity and preventing it from meeting requirements. Utility Model Content

[0003] The purpose of this invention is to provide a high-temperature resistant full complement angular contact ball bearing for aero engines, which greatly improves its load-bearing capacity by filling the space between the outer and inner rings with steel balls.

[0004] To achieve the above objectives, the solution of this utility model is as follows:

[0005] A high-temperature resistant full complement angular contact ball bearing for aero-engines includes an inner ring, an outer ring, and steel balls. The outer ring has an outer groove recessed on its inner wall, and the inner ring has an inner groove recessed on its outer wall. The outer ring is fitted over the inner ring. The inner and outer grooves together form an annular raceway. The steel balls are located within the raceway and simultaneously abut against the outer and inner grooves. Multiple steel balls are arranged in a circumferential array around the axis of the inner ring and are fully distributed within the raceway. The inner wall of the outer ring forms a first and a second retaining edge on both sides of the outer groove, and the outer wall of the inner ring forms a third and a fourth retaining edge on both sides of the inner groove. The first and third retaining edges are on one side of the steel balls, and the second and fourth retaining edges are on the other side of the steel balls. The distance between the first and third retaining edges is greater than the distance between the second and fourth retaining edges.

[0006] Furthermore, the distance between the first and third retaining edges can be increased to allow the steel balls to pass through and be pressed into the raceway when the outer ring is heated and expanded and the inner ring is cooled and contracted.

[0007] Furthermore, the diameter of the first stop is larger than the diameter of the second stop, while the diameters of the third and fourth stopes are the same.

[0008] Furthermore, the diameter of the first retaining edge is within the range of 23.9mm-24.1mm, the diameter of the second retaining edge is within the range of 23.7mm-23.9mm, the diameter of the third and fourth retaining edges is within the range of 16.80mm-17.00mm, the diameter of the steel ball is 4.763mm, the radius of curvature of the outer groove is within the range of 2.50mm-2.53mm, and the radius of curvature of the inner groove is within the range of 2.45mm-2.48mm.

[0009] Furthermore, the contact angle of the steel ball is 25°.

[0010] Furthermore, two annular dust covers are provided between the inner and outer rings. One annular dust cover is located on one side of the steel ball, and the other dust cover is located on the other side of the steel ball. The dust covers are used to prevent foreign objects from entering the bearing.

[0011] After adopting the above solution, the beneficial effects of this utility model are as follows:

[0012] (1) This utility model greatly improves its load-bearing capacity by filling the space between the outer ring and the inner ring with steel balls. The steel balls are located in the raceway and simultaneously abut against the outer groove and the inner groove. The first stop, the third stop, the second stop, and the fourth stop work together to prevent the steel balls from detaching.

[0013] (2) This utility model expands the distance between the first and third retaining edges by heating the outer ring and cooling the inner ring to allow the steel balls to pass through and be pressed into the raceway. This makes the bearing of this utility model not need to be equipped with a ball loading groove to load the steel balls into the raceway, thus avoiding the steel balls from leaking out of the ball loading groove and making the structure more reliable. Attached Figure Description

[0014] Figure 1 This is a top view of the overall structure of this utility model;

[0015] Figure 2 This is a top view of the present invention without the dust cover;

[0016] Figure 3 This is a cross-sectional view of the present invention.

[0017] Label Explanation:

[0018] 10. Outer ring; 11. Outer groove; 12. First retaining edge; 13. Second retaining edge; 20. Inner ring; 21. Inner groove; 22. Third retaining edge; 23. Fourth retaining edge; 30. Steel ball; 40. Dust cover. Detailed Implementation

[0019] The present invention will now be further described in conjunction with the accompanying drawings and specific embodiments.

[0020] like Figure 1As shown in Figure 3, this embodiment provides a high-temperature resistant full complement angular contact ball bearing for aero-engines, including an inner ring 20, an outer ring 10, and steel balls 30. An outer groove 11 is recessed on the inner wall of the outer ring 10, and an inner groove 21 is recessed on the outer wall of the inner ring 20. The outer ring 10 is fitted over the inner ring 20. The inner groove 21 and the outer groove 11 together form an annular raceway. The steel balls 30 are located within the raceway and simultaneously abut against the outer groove 11 and the inner groove 21. Multiple steel balls 30 rotate around the axis of the inner ring 20. The outer ring 10 is arranged in a circumferential array and is fully distributed in the raceway. The inner wall of the outer ring 10 forms a first stop 12 and a second stop 13 on both sides of the outer groove 11. The outer wall of the inner ring 20 forms a third stop 22 and a fourth stop 23 on both sides of the inner groove 21. The first stop 12 and the third stop 22 are on one side of the steel ball 30, and the second stop 13 and the fourth stop 23 are on the other side of the steel ball 30. The distance between the first stop 12 and the third stop 22 is greater than the distance between the second stop 13 and the fourth stop 23.

[0021] Furthermore, the distance between the first stop 12 and the third stop 22 can be increased to allow the steel ball 30 to pass through and be pressed into the raceway when the outer ring 10 is heated and expanded and the inner ring 20 is cooled and contracted.

[0022] Furthermore, the diameter of the first stop 12 is larger than the diameter of the second stop 13, while the diameters of the third stop 22 and the fourth stop 23 are the same.

[0023] Furthermore, the diameter of the first retaining edge 12 is within the range of 23.9mm-24.1mm, the diameter of the second retaining edge 13 is within the range of 23.7mm-23.9mm, the diameters of the third retaining edge 22 and the fourth retaining edge 23 are within the range of 16.80mm-17.00mm, the diameter of the steel ball 30 is 4.763mm, the radius of curvature of the outer groove 11 is within the range of 2.50mm-2.53mm, and the radius of curvature of the inner groove 21 is within the range of 2.45mm-2.48mm.

[0024] Furthermore, the contact angle of the steel ball 30 is 25°.

[0025] like Figure 3 Two annular dust covers 40 are provided between the inner ring 20 and the outer ring 10. One annular dust cover 40 is placed on one side of the steel ball 30, and the other dust cover 40 is placed on the other side of the steel ball. The dust covers 40 are used to prevent foreign objects from entering the bearing.

[0026] Specifically, the first retaining edge 12 has a first groove recessed at the end away from the outer groove 11, and the second retaining edge 13 has a second groove recessed at the end away from the outer groove 11. A dust cover 40 is located within the distance between the first retaining edge 12 and the third retaining edge 22. Its end near the first retaining edge 12 is radially flanged to form an elastic hook-shaped structure, which is then inserted into the first groove. Its other end extends toward the third retaining edge 22, thus covering one side of the steel ball 30. Another dust cover 40 is located within the distance between the second retaining edge 13 and the fourth retaining edge 23. Its end near the second retaining edge 13 is radially flanged to form an elastic hook-shaped structure, which is then inserted into the second groove. Its other end extends toward the fourth retaining edge 23, thus covering the other side of the steel ball 30. The two dust covers 40 together prevent foreign objects from entering the bearing. The two dust covers 40 achieve self-locking by the elastic deformation of the hook-shaped structure, simplifying the installation process.

[0027] This utility model greatly improves its load-bearing capacity by filling the space between the outer ring 10 and the inner ring 11 with steel balls 30. The steel balls 30 are located in the raceway and simultaneously abut against the outer groove 11 and the inner groove 21. The first stop 12, the third stop 22, the second stop 13, and the fourth stop 23 jointly prevent the steel balls 30 from detaching.

[0028] Furthermore, this invention expands the distance between the first retaining edge 12 and the third retaining edge 22 by heating the outer ring 10 and cooling the inner ring 11 to allow the steel ball 30 to pass through and be pressed into the raceway. This eliminates the need for a ball-loading groove in the bearing to load the steel ball 30 into the raceway, preventing the steel ball 30 from leaking out of the ball-loading groove and making the structure more reliable.

[0029] The directional terms used in this specification are defined relative to the structures shown in the accompanying drawings. They are relative concepts and may therefore vary depending on their location and usage. Therefore, these or other directional terms should not be interpreted as restrictive.

[0030] The above description is only a preferred embodiment of this utility model and is not intended to limit the design of this case. All equivalent changes made based on the key design of this case shall fall within the protection scope of this case.

Claims

1. A high-temperature resistant full complement angular contact ball bearing for aero engines, characterized in that: The device includes an inner ring, an outer ring, and steel balls. The inner wall of the outer ring has an outer groove, and the outer wall of the inner ring has an inner groove. The outer ring is fitted over the inner ring. The inner and outer grooves together form an annular extending raceway. The steel balls are located in the raceway and simultaneously abut against the outer and inner grooves. Multiple steel balls are arranged in a circumferential array around the axis of the inner ring and are fully distributed in the raceway. The inner wall of the outer ring forms a first and a second guard on both sides of the outer groove, and the outer wall of the inner ring forms a third and a fourth guard on both sides of the inner groove. The first and third guards are on one side of the steel balls, and the second and fourth guards are on the other side of the steel balls. The distance between the first and third guards is greater than the distance between the second and fourth guards.

2. The high-temperature resistant full complement angular contact ball bearing for aero-engines as described in claim 1, characterized in that: The distance between the first and third retaining edges can be widened to allow the steel balls to pass through and be pressed into the raceway when the outer ring is heated and expanded and the inner ring is cooled and contracted.

3. The high-temperature resistant full complement angular contact ball bearing for aero engines as described in claim 1, characterized in that: The diameter of the first retaining edge is larger than the diameter of the second retaining edge, while the diameters of the third and fourth retaining edges are the same.

4. The high-temperature resistant full complement angular contact ball bearing for aero-engines as described in claim 1, characterized in that: The diameter of the first retaining edge is within the range of 23.9mm-24.1mm, the diameter of the second retaining edge is within the range of 23.7mm-23.9mm, the diameter of the third and fourth retaining edges is within the range of 16.80mm-17.00mm, the diameter of the steel ball is 4.763mm, the radius of curvature of the outer groove is within the range of 2.50mm-2.53mm, and the radius of curvature of the inner groove is within the range of 2.45mm-2.48mm.

5. The high-temperature resistant full complement angular contact ball bearing for aero engines as described in claim 1, characterized in that: The contact angle of the steel ball is 25°.

6. The high-temperature resistant full complement angular contact ball bearing for aero-engines as described in claim 1, characterized in that: Two annular dust covers are provided between the inner and outer rings. One annular dust cover is placed on one side of the steel ball, and the other dust cover is placed on the other side of the steel ball.

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