Angular contact ball bearing and design method thereof

Abstract

The invention relates to the technical field of bearings, in particular to an angular contact ball bearing and a design method thereof.The end face of one side of an outer ring is provided with a plurality of containing grooves, springs are contained in the containing grooves, one ends of the springs abut against the groove bottoms of the containing grooves, and ejector blocks are arranged on the sides, away from the groove bottoms, of the springs; the top block is sequentially provided with an embedded part, a maximum diameter part and a protruding part in the axial direction, the embedded part is arranged on the inner side of the spring, the maximum diameter part abuts against the other end of the spring, a check ring is fixed to the containing groove, the protruding part extends out of the inner side of the check ring, and a limiting face is arranged on the side, facing the groove bottom, of the check ring and limits the axial position of the maximum diameter part. The bearing and the spring form an integrated structure, and operation errors caused by manual adjustment of a traditional external pre-tightening device are avoided; the outer contour size of the bearing is not increased, the bearing is good for small-sized and light-weight equipment, the spring automatically compensates for part expansion and the like caused by temperature rise, the pretightening force is kept constant, and vibration, noise or precision reduction caused by pretightening failure is avoided.

Description

Technical Field

[0001] This invention relates to the field of bearing technology, specifically to angular contact ball bearings and their design methods. Background Technology

[0002] Angular contact ball bearings are typically used in pairs, face-to-face, back-to-back, or tandem. Angular contact ball bearings require a constant preload during high-speed rotation, usually achieved through constant pressure preload. Constant pressure preload applies the load through spring deformation; even if the bearing position changes during rotation due to thermal and load effects, a stable preload is maintained. Current constant pressure preload methods involve placing a spring outside the bearing, occupying shaft space. Summary of the Invention

[0003] In view of the deficiencies of the prior art, the present invention provides an angular contact ball bearing and its design method. Since the preload required when the bearing rotates at high speed is small, the load for constant pressure preload is combined with the bearing, and a spring is set on the outer diameter end face of the angular contact ball bearing, which no longer occupies the shaft position.

[0004] To achieve the above objectives, the present invention provides an angular contact ball bearing, comprising an inner ring, an outer ring, a cage, and rollers. The cage is disposed between the inner and outer rings, and the rollers are installed in the cage. A plurality of receiving grooves are formed on one end face of the outer ring, each receiving groove accommodating a spring. One end of the spring abuts against the bottom of the receiving groove. A top block is provided on the side of the spring away from the bottom of the groove. The top block has, along the axial direction, a recessed portion, a maximum diameter portion, and a protrusion. The recessed portion is located inside the spring, and the maximum diameter portion abuts against the other end of the spring. A retaining ring is fixed to the inner wall of the receiving groove. The protrusion extends from the inside of the retaining ring. A limiting surface is provided on the side of the retaining ring facing the bottom of the groove, and the limiting surface limits the axial position of the maximum diameter portion.

[0005] Furthermore, the inner wall of the receiving groove is bonded to the outer diameter of the retaining ring by a cylindrical retaining adhesive.

[0006] Furthermore, the outer diameter of the largest diameter portion contacts and seals with the inner wall of the receiving groove.

[0007] Furthermore, when the maximum diameter portion of the top block is in contact with the limiting surface of the retaining ring, the end face of the protrusion is higher than the end face of the outer ring.

[0008] Furthermore, the diameter of the receiving groove is e, where e = D1 + 0.1; D1 is the diameter of the spring.

[0009] Furthermore, the thickness of the maximum diameter portion of the top block is S2, the diameter of the protrusion is f, the height of the protrusion is k1, the depth of the receiving groove is h, and the thickness of the retaining ring is S1. Then S1 = 2d1, S2 = 2d1, where d1 is the diameter of the spring wire.

[0010] f = 0.7e;

[0011] h = H - Δl + S1 + S2 + 0.5, where H is the free height of the spring and Δl is the spring compression.

[0012] k1 = h - S2 - k2, k2 = H - Δl.

[0013] On the other hand, the present invention provides a design method for an angular contact ball bearing, the specific steps of which include step S1: determining the bearing dimensions, including inner diameter d, outer diameter D, width B, and contact angle α;

[0014] Step S2: Determine the bearing rotation center diameter D wp ,

[0015]

[0016] Step S3: Determine the roller diameter D w ,

[0017] K w min(Dd)≤Dw≤K w max(Dd), where K w min and K w max and max are the maximum and minimum values ​​of the section modulus, respectively; K w min = 0.24, K w max = 0.32; according to D w The range of values ​​determines the possible values ​​for D. w ;

[0018] Step S4: Determine the number of rollers Z.

[0019] Among them, K z =1.01 + 1.9 / D w ;

[0020] Step S5: Optimize D with the maximum rated static load as the target. w Z,

[0021] Cor = f0 × I × Z × D w 2 ×cosα, where I is the column number, and f0 is based on... Obtained through interpolation calculation;

[0022] Step S6: Determine the outer groove curvature coefficient as f eThe value range is 0.505 ≤ f e ≤0.515,

[0023] The curvature coefficient of the inner groove is determined to be f. i The value range is 0.515 ≤ f i ≤0.525;

[0024] f e =0.51, f i =0.52;

[0025] Step S7: The distance x from the outer raceway diameter position to the outer diameter should be greater than or equal to 0.6 times the cross-sectional area a of the outer raceway's large end face, i.e., x ≥ 0.6a; and Step S8: Determine the required preload F1 of the bearing based on the actual operating conditions of the bearing, and calculate the spring dimensions;

[0026] Where C is the stiffness of the spring, G is the shear modulus of the spring material, d1 is the diameter of the spring wire, D1 is the diameter of the spring, n is the effective number of spring coils, F1 = F2, F2 = CNΔl, where F2 is the total force of the spring, N is the number of springs, and Δl is the spring compression.

[0027] Step S9: Design the groove size according to the spring size; confirm the retaining ring size; confirm the top block size.

[0028] Furthermore, the dimensions of the receiving groove include the diameter e of the receiving groove, the depth h of the receiving groove, and the distance c between the receiving groove and the outer ring; the dimensions of the retaining ring include the thickness S1 of the retaining ring, the outer diameter S3 of the retaining ring, and the inner diameter S4 of the retaining ring; the dimensions of the top block include the thickness S2 of the maximum diameter portion, the diameter f of the protrusion, and the height k1 of the protrusion.

[0029] e = D1 + 0.1;

[0030] S1 = 2d1;

[0031] S2 = 2d1;

[0032] h = H - Δl + S1 + S2 + 0.5;

[0033] c = 0.5e;

[0034] f = 0.7e;

[0035] S3 = e;

[0036] S4 = 1.2f;

[0037] k1 = h - S2 - k2, where k2 is the maximum length of the spring inside the receiving groove, and k2 = H - Δl.

[0038] The beneficial effects of this invention are: the bearing and spring form an integrated structure, avoiding the operational errors of manual adjustment of traditional external preload devices; it does not increase the external profile size of the bearing, which is better for miniaturized and lightweight equipment; the built-in spring automatically compensates for the expansion of parts caused by temperature rise, maintains constant preload force, and avoids vibration, noise or decrease in precision caused by preload failure. Attached Figure Description

[0039] Figure 1 This is a schematic diagram of the structure of an angular contact ball bearing according to one embodiment of the present invention;

[0040] Figure 2 This is a schematic diagram of the location of the receiving groove in an embodiment of the present invention;

[0041] Figure 3 This is a schematic diagram of the top block of an angular contact ball bearing according to one embodiment of the present invention;

[0042] Figure 4 This is a schematic diagram showing the dimensions of an angular contact ball bearing according to one embodiment of the present invention;

[0043] Figure 5 This is a schematic diagram showing the dimensions of the receiving groove position of an angular contact ball bearing according to an embodiment of the present invention;

[0044] Figure 6 This is a schematic diagram showing the dimensions of an angular contact ball bearing according to another embodiment of the present invention;

[0045] In the picture:

[0046] 100. Inner circle

[0047] 200. Outer ring; 210. Receiving groove; 211. Spring; 212. Top block; 2121. Embedded part; 2122. Maximum diameter part; 2123. Protrusion; 213. Retaining ring; 2131. Limiting surface.

[0048] 300. Cage

[0049] 400, Roller. Detailed Implementation

[0050] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0051] See Figures 1-3In one embodiment of the present invention, an angular contact ball bearing is provided, including an inner ring 100, an outer ring 200, a cage 300, and rollers 400. The cage 300 is disposed between the inner ring 100 and the outer ring 200. The rollers 400 are installed in the cage 300. A plurality of receiving grooves 210 are provided on one end face of the outer ring 200. The receiving grooves 210 accommodate springs 211. A top block 212 is provided on the side of the spring 211 away from the bottom of the receiving groove 210. A retaining ring 213 is fixed on the inner side wall of the receiving groove 210. The retaining ring 213 provides a limiting surface 2131 for limiting the axial position of the top block 212.

[0052] In one embodiment, the inner wall of the receiving groove 210 is bonded to the outer diameter of the retaining ring 213 using a cylindrical retaining adhesive. It should be noted that there are two designs for fixing the axial position of the retaining ring 213: one is to machine the groove circumferential direction into an internal thread and the retaining ring 213 circumferential direction into an external thread, fixing the axial displacement of the top block 212 by thread engagement; the other is to carve a radial groove around the groove circumference, fixing the axial displacement of the top block 212 by interference fit of the retaining ring 213. High-speed angular contact balls are used in precision applications, and their lifespan depends on rotational accuracy rather than fatigue life. Therefore, the bearing replacement cycle is generally one quarter or half a year. The elasticity of the spring 211 can be maintained for one year or more. The lifespan of the spring 211 is much longer than the rotational accuracy lifespan of the bearing. Therefore, using a cylindrical retaining adhesive to bond the groove and the retaining ring 213 is a more economical method that does not increase the machining difficulty of the bearing's outer ring 200.

[0053] In one embodiment, the top block 212 is provided with an embedded portion 2121, a maximum diameter portion 2122, and a protrusion 2123 sequentially along the axial direction. The embedded portion 2121 is located inside the spring 211, and the maximum diameter portion 2122 is located on the side of the limiting surface 2131 near the bottom of the receiving groove 210. The maximum diameter portion 2122 abuts against one end of the spring 211, and the other end of the spring 211 abuts against the bottom of the receiving groove 210. The protrusion 2123 extends from the inside of the retaining ring 213, and the end face of the protrusion 2123 is higher than the end face of the outer ring 200. Further, the outer diameter of the maximum diameter portion 2122 contacts and seals with the inner wall of the receiving groove 210. Specifically, a sealing ring can be embedded in the outer diameter of the maximum diameter portion 2122, and the sealing ring contacts and seals with the inner wall of the receiving groove 210. The spring 211 is a sealed area, unaffected by dust or oil.

[0054] The aforementioned angular contact ball bearing integrates the bearing and spring 211 into a single structure, avoiding the operational errors of manual adjustment using traditional external preload devices. It does not increase the external dimensions of the spring 211, making it suitable for miniaturized and lightweight equipment. The built-in spring 211 automatically compensates for component expansion due to temperature rise, maintaining a constant preload and preventing vibration, noise, or precision degradation caused by preload failure. Furthermore, the angular contact ball bearing has a compact structure, simple assembly process, small installation space, and high preload stability, thereby improving the bearing's impact resistance and vibration damping performance, reducing maintenance costs, extending bearing life, and providing flexible adjustment capabilities for various operating conditions. Bearings with built-in springs 211 can be used immediately after installation without separate adjustment, and different levels of preload adjustment can be achieved according to customer needs to meet diverse operating conditions.

[0055] See Figures 4-6 Another embodiment of the present invention provides a design method for an angular contact ball bearing, taking 7018ACDBA as an example.

[0056] Step S1, see Figure 6 The bearing dimensions are determined as follows: inner diameter d = 90 mm, outer diameter D = 140 mm, width B = 24 mm, and contact angle α = 25°.

[0057] Step S2: Determine the bearing rotation center diameter D wp , Step S3: Determine the roller diameter D w K w min(Dd)≤Dw≤K w max(Dd), where K w min and K w max and max are the maximum and minimum values ​​of the section modulus, respectively; K w min = 0.24, K w max=0.32; 0.24×(140-90)≤Dw≤0.32×(140-50), 12mm≤D w ≤16mm, the roller diameter should conform to GB / T308.2, D w Available thicknesses are 12.303mm, 12.7mm, 13.494mm, 14.288mm, 15.081mm, and 15.875mm.

[0058] Step S4: Determine the number of rollers Z.

[0059] Among them, K z =1.01 + 1.9 / D w ;

[0060] D wp D wSubstitute, K z =1.01 + 1.9 / D w .

[0061] When D w When Z = 12.303 mm, Z ≤ 25.22, so Z is taken as 25;

[0062] When D w When the diameter is 12.7 mm, Z ≤ 24.53, so Z is taken as 24;

[0063] When D w When Z = 13.494 mm, Z ≤ 23.27, so Z is taken as 23.

[0064] When D w When Z = 14.288 mm, Z ≤ 22.12, so Z is taken as 22;

[0065] When D w When Z = 15.081 mm, Z ≤ 23.27, so Z is taken as 21;

[0066] When D w When Z = 15.875 mm, Z ≤ 20.15, so Z is taken as 20.

[0067] Step S5: Optimize D with the maximum rated static load as the target. w Z,

[0068] Cor = f0 × I × Z × D w 2 ×cosα, where I is the column number, and f0 is based on... Obtained through interpolation calculation;

[0069] When D w When the diameter is 12.303 mm, Z ≤ 25.22, Z is taken as 25, f0 = 16.43, Cor = 56.3 kN;

[0070] When D w When the diameter is 12.7 mm, Z ≤ 24.53, Z is taken as 24, f0 = 16.40, Cor = 57.5 kN;

[0071] When D w When the diameter is 13.494 mm, Z ≤ 23.27, Z is taken as 23, f0 = 16.21, Cor = 61.5 kN;

[0072] When D w When the diameter is 14.288 mm, Z ≤ 22.12, Z is taken as 22, f0 = 16.05, Cor = 65.3 kN;

[0073] When D wWhen the diameter is 15.081 mm, Z ≤ 23.27, Z is taken as 21, f0 = 15.92, Cor = 68.9 kN;

[0074] When D w When the diameter is 15.875 mm, Z ≤ 20.15, Z is taken as 20, f0 = 15.75, Cor = 71.9 kN.

[0075] Step S6: Determine the inner groove curvature coefficient f i f i =0.52, the range of outer groove curvature is f e f e =0.51;

[0076] Step S7: To ensure the strength of the outer ring end face, the distance x from the outer ring raceway diameter position to the outer diameter should be greater than or equal to 0.6 times the cross-sectional area a of the large end face of the outer ring.

[0077] The condition x ≥ 0.6a must be met, according to calculate;

[0078] D w =12.303mm, Z≤25.22, Z is taken as 25, f0=16.43, Cor=56.3kN,

[0079] D w =12.7mm, Z≤24.53, Z is taken as 24, f0=16.40, Cor=57.5kN,

[0080] D w =13.494mm, Z≤23.27, Z is taken as 23, f0=16.21, Cor=61.5kN,

[0081] D w =14.288mm, Z≤22.12, Z is taken as 22, f0=16.05, Cor=65.3kN,

[0082] D w =15.081mm, Z≤23.27, Z is taken as 21, f0=15.92, Cor=68.9kN,

[0083] D w =15.875mm, Z≤20.15, Z is taken as 20, f0=15.75, Cor=71.9kN,

[0084] Determine the bearing design scheme. Based on the above calculations, the bearing design meets both the maximum rated static load Cor and x ≥ 0.6a. Therefore, the bearing design is determined to be D. w =15.081mm, Z≤23.27, Z is taken as 21, f0=15.92, Cor=68.9kN, f e =0.51, f i =0.52.

[0085] Step S8: Query the sample to find that the preload force F1 of a single-row angular contact tapered roller bearing under light preload should be 290kN; convert the preload force F1 to spring parameters. The spring size should comply with GB / T 2089. Calculate the spring size. Where C is the stiffness of the spring, G is the shear modulus of the spring material, d1 is the diameter of the spring wire, D1 is the diameter of the spring, n is the effective number of spring coils, F1 = F2, F2 = CNΔl, where F2 is the total force of the spring, N is the number of springs, and Δl is the spring compression.

[0086] The spring dimensions are confirmed as follows: spring wire diameter d1 = 0.8 mm, spring diameter D1 = 5.6 mm, effective number of turns n = 4.5 turns, spring free height H = 9 mm, spring compression Δl = 4.5 mm, a total of 8 springs are used, and the total spring force F2 = 296 N.

[0087] The required preload is basically the same.

[0088] Step S9: Design the groove size according to the spring size; confirm the retaining ring size; confirm the top block size;

[0089] The dimensions of the receiving groove 210 include the receiving groove diameter e, the receiving groove depth h, and the distance c between the receiving groove and the outer ring;

[0090] The dimensions of retaining ring 213 include retaining ring thickness S1, retaining ring outer diameter S3, and retaining ring inner diameter S4.

[0091] The dimensions of top block 212 include the thickness S2 of the maximum diameter portion, the diameter f of the protrusion, and the height k1 of the protrusion.

[0092] e=D1+0.1=5.6+0.1=5.7mm;

[0093] S1 = 2d1 = 2 × 0.8 = 1.6 mm;

[0094] S2 = S1 = 1.6 mm;

[0095] h=H-Δl+S1+S2+0.5=9-4.5+1.6+1.6+0.5=8.2mm;

[0096] c=0.5e=0.5×5.7=2.85≈2.9mm;

[0097] f = 0.7e = 0.7 × 5.7 ≈ 4 mm;

[0098] S3 = e = 5.7 mm;

[0099] S4 = 1.2f = 1.2 × 4 = 4.8 mm;

[0100] k1=h-S2-k2=8.2-1.6-4.5=2.1mm;

[0101] Where k2 is the maximum length of the spring inside the receiving groove, k2=H-Δl=9-4.5=4.5mm.

[0102] The design method for the aforementioned angular contact ball bearing first determines the preload F1 of the single-row angular contact tapered roller bearing. Based on the preload F1, the spring parameters are calculated. Then, based on the spring parameters and spring dimensions, the groove dimensions, retaining ring dimensions, and top block dimensions are designed to ensure that a receiving groove 210 is provided on the outer ring 200, and a spring 211 is installed within the receiving groove 210 to meet the preload F1 requirement. Different levels of preload F1 can be adjusted according to customer needs to meet diverse operating conditions.

[0103] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0104] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0105] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0106] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0107] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

Claims

1. An angular contact ball bearing, comprising an inner ring, an outer ring, a cage, and rollers, wherein the cage is disposed between the inner ring and the outer ring, and the rollers are fitted into the cage, characterized in that: The outer ring has multiple receiving grooves on one side end face, each receiving groove accommodating a spring. One end of the spring abuts against the bottom of the receiving groove. A top block is provided on the side of the spring away from the bottom of the groove. The top block has an embedded part, a maximum diameter part, and a protrusion arranged sequentially along the axial direction. The embedded part is located inside the spring, and the maximum diameter part abuts against the other end of the spring. A retaining ring is fixed to the inner side wall of the receiving groove. The protrusion extends from the inside of the retaining ring. A limiting surface is provided on the side of the retaining ring facing the bottom of the groove, and the limiting surface limits the axial position of the maximum diameter part.

2. The angular contact ball bearing according to claim 1, characterized in that: The inner wall of the receiving groove is bonded to the outer diameter of the retaining ring by a cylindrical retaining adhesive.

3. The angular contact ball bearing according to claim 1, characterized in that: The outer diameter of the largest diameter portion contacts and seals with the inner wall of the receiving groove.

4. The angular contact ball bearing according to claim 1, characterized in that: When the maximum diameter portion of the top block is in contact with the limiting surface of the retaining ring, the end face of the protrusion is higher than the end face of the outer ring.

5. The angular contact ball bearing according to claim 1, characterized in that: The diameter of the receiving groove is e, where e = D1 + 0.1; D1 is the diameter of the spring.

6. The angular contact ball bearing according to claim 5, characterized in that: The thickness of the maximum diameter portion of the top block is S2, the diameter of the protrusion is f, the height of the protrusion is k1, the depth of the receiving groove is h, and the thickness of the retaining ring is S1. Then S1 = 2d1, S2 = 2d1, where d1 is the diameter of the spring wire. f = 0.7e; h = H - Δl + S1 + S2 + 0.5, where H is the free height of the spring and Δl is the spring compression. k1 = h - S2 - k2, k2 = H - Δl.

7. A design method for angular contact ball bearings, characterized in that: The specific steps include Step S1: Determine the bearing dimensions: inner diameter d, outer diameter D, width B, and contact angle α. Step S2: Determine the bearing rotation center diameter D wp , Step S3: Determine the roller diameter D w , K w min(Dd)≤Dw≤K w max(Dd), where K w min and K w max and max are the maximum and minimum values ​​of the section modulus, respectively; K w min = 0.24, K w max = 0.32; according to D w The range of values ​​determines the possible values ​​for D. w ; Step S4: Determine the number of rollers Z. Among them, K z =1.01 + 1.9 / D w ; Step S5: Optimize D with the maximum rated static load as the target. w Z, Cor = f0 × I × Z × D w 2 ×cosα, where I is the column number, and f0 is based on... Obtained through interpolation calculation; Step S6: Determine the outer groove curvature coefficient as f e The value range is 0.505 ≤ f e ≤0.515, The curvature coefficient of the inner groove is determined to be f. i The value range is 0.515 ≤ f i ≤0.525; f e =0.51,f i =0.52; Step S7: The distance x from the outer raceway diameter position to the outer diameter should be greater than or equal to 0.6 times the cross-sectional area a of the outer raceway's large end face, i.e., x ≥ 0.6a; and Step S8: Determine the required preload F1 of the bearing based on the actual operating conditions of the bearing, and calculate the spring dimensions; Where C is the stiffness of the spring, G is the shear modulus of the spring material, d1 is the diameter of the spring wire, D1 is the diameter of the spring, n is the effective number of spring coils, F1 = F2, F2 = CNΔl, where F2 is the total force of the spring, N is the number of springs, and Δl is the spring compression. Step S9: Design the groove size according to the spring size; confirm the retaining ring size; confirm the top block size.

8. The design method for angular contact ball bearings according to claim 7, characterized in that: The dimensions of the receiving groove include the diameter e of the receiving groove, the depth h of the receiving groove, and the distance c between the receiving groove and the outer ring; The dimensions of the retaining ring include the retaining ring thickness S1, the retaining ring outer diameter S3, and the retaining ring inner diameter S4; The dimensions of the top block include the thickness S2 of the maximum diameter portion, the diameter f of the protrusion, and the height k1 of the protrusion; e = D1 + 0.1; S1 = 2d1; S2 = 2d1; h = H - Δl + S1 + S2 + 0.5; c = 0.5e; f = 0.7e; S3 = e; S4 = 1.2f; k1 = h - S2 - k2, where k2 is the maximum length of the spring inside the receiving groove, and k2 = H - Δl.

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