Large cylindrical roller bearing retainer structure parameter design method

Abstract

The invention belongs to the field of bearing manufacturing, and particularly relates to a structural parameter design method for a large cylindrical roller bearing retainer. The method comprises the following steps: firstly, determining the pitch diameter D0 of cylindrical roller distribution according to the geometric dimension of the large cylindrical roller bearing, and preliminarily selecting the nominal diameter Dw, the nominal length Lw and the roller column number i of the cylindrical rollers; the number N of the retainers, the circumferential residual arc length L, the number n of the pockets, the number a of lintels for arranging the axial anti-friction blocks, the width B of the lintels and the width Bwidth of the lintels for welding the anti-friction blocks are determined; and finally determining the nominal diameter Dw, the nominal length Lw and the roller row number i of the cylindrical roller meeting the design requirements of the large cylindrical roller, and the number N and other structural parameters of the retainer by means of checking the service life and the safety coefficient of the bearing. According to the method, a basis is mainly provided for key structure parameter design of retainers of large bearings such as large main bearings of shield tunneling machines, port machinery and tower crane turntable bearings and the like, good matching between the retainers and cylindrical rollers is realized, and stable operation of the large cylindrical roller bearings is ensured.

Description

Technical Field

[0001] This invention belongs to the field of bearing manufacturing, and specifically relates to a method for designing the structural parameters of a cage for a large cylindrical roller bearing. Background Technology

[0002] Large cylindrical roller bearings, such as the main bearings of tunnel boring machines, port machinery and tower crane slewing bearings, are large heavy-duty bearings with low operating speeds and large loads, and are widely used in heavy equipment and major equipment.

[0003] The cage plays a crucial role in large cylindrical roller bearings, limiting and guiding the movement of the rollers. It is a vital component ensuring the normal operation of large cylindrical roller bearings, and its structural parameters directly affect the operating condition and service life of the bearing. Furthermore, during the operation of large cylindrical roller bearings, the cage and cylindrical rollers are in contact, requiring a good matching relationship to ensure safe and reliable operation. Cages for large roller bearings include integral and segmented sector types. Large roller bearings (especially those with an outer diameter exceeding 3m) typically use segmented sector cages. The dimensional parameters of the cage directly affect the bearing's service life: firstly, the cage size determines the number of rollers, directly impacting the bearing's load-bearing capacity; secondly, if the dimensions of the crossbeam and transverse beam are inappropriate, the cage may be damaged due to insufficient strength. Therefore, the structural design of the cage is an extremely important step in the design process of large, heavy-duty bearings. Existing design methods for large roller bearing cages fail to adequately consider the bearing's operating conditions under complex working conditions, resulting in poor structural strength, wear resistance, and impact resistance of the cages, making them prone to wear, breakage, and other failures.

[0004] Patent CN102506075A discloses a split cage for self-aligning roller bearings and its design method. While it improves the cage structure by increasing the outer diameter and enhancing strength and reliability through splitting and connection, it primarily focuses on the design of split cages for self-aligning roller bearings. This differs significantly from the structural and design requirements of cages for large cylindrical roller bearings. It does not elaborate on the systematic design methods for key structural parameters such as crossbeams, transverse beams, and runout grooves in large cylindrical roller bearing cages, thus failing to meet the refined design needs of large cylindrical roller bearings under various complex operating conditions.

[0005] Patent CN103032470A discloses a design for a slotted bearing cage, focusing on the slotted structure and locking connection method to achieve axial, radial, and tangential fixation of the bearing cage section. However, this document does not mention the design method for the structural parameters of large cylindrical roller bearing cages, and is insufficient in terms of how to determine the various structural parameters of the cage based on the space constraints of the bearing, the parameters of the rollers, and the complex operating conditions to meet the load-bearing capacity and service life requirements of large cylindrical roller bearings.

[0006] Patent CN115952612A proposes a design method for key feature parameters of porous cages in space bearings. Based on fractal theory, it establishes a mathematical model between key feature parameters and the oil supply characteristics of the porous cage, primarily addressing the design problem of oil supply characteristics requirements for porous cages. However, it lacks comprehensive consideration for the structural parameters of cages in large cylindrical roller bearings, failing to clearly define detailed methods for determining the matching relationship between the cage and rollers, the structural parameters of the crossbeams and transverse beams, and how to ensure the overall operational stability and service life of large cylindrical roller bearings under complex working conditions. Summary of the Invention

[0007] The purpose of this invention is to provide a method for designing the structural parameters of a large cylindrical roller bearing cage. By obtaining the cage parameters through this method, the normal operation of the large cylindrical roller bearing can be guaranteed, its service life requirements can be met, and dimensional constraints can also be provided for the design of the bearing rings.

[0008] The technical solution of this invention is:

[0009] A method for designing the structural parameters of a large cylindrical roller bearing cage includes the following steps:

[0010] Step 1: Determine the pitch circle diameter D0 of the cylindrical roller distribution;

[0011] Step 2: Determine the nominal diameter D of the cylindrical roller. w Nominal length L w And the number of rollers, i;

[0012] Step 3: Determine the number of cage segments N and the remaining circumferential arc length L;

[0013] Step 4: Determine the cage lintel parameters;

[0014] Step 4 (a): Determine the number of cage pockets n and the number of crossbeams a used to set the axial wear-reducing blocks;

[0015] Step 4 (II): Determine the width B of the cage lintel;

[0016] Step 4 (3): Determine the width B of the cage welding friction reduction block overbeam.weld ;

[0017] Step 5: Check the bearing life and safety factor. If the design requirements are not met, return to Step 3; if there is no N that meets the requirements, return to Step 2.

[0018] Step Six: Determine other structural parameters of the cage;

[0019] Step 6 (a), determine the width B of the cage beam. e ;

[0020] Step 6 (II): Determine the thickness B of the radial wear-reducing block of the cage. af ;

[0021] Step 6 (3): Determine the main body thickness H of the cage and the total thickness H1 of the cage;

[0022] Step 6 (iv): Determine the cage overrun groove parameters a, b, r u ;

[0023] Step 6 (5): Determine the cage pocket clearance d s and d e .

[0024] In the design method for the cage structure parameters of the large cylindrical roller bearing, in step one, the pitch circle diameter D0 of the cylindrical rollers is determined according to the spatial size constraints of the cylindrical roller bearing.

[0025] In the design method for the structural parameters of the cage of the large cylindrical roller bearing, in step two, the nominal diameter D of the cylindrical roller is... w Nominal length L w The number of roller columns i is selected according to the standard.

[0026] In the design method for the structural parameters of the large cylindrical roller bearing cage, in step three, the number of cage segments N is determined based on the processing capability, and the remaining circumferential arc length L is determined by the following formula;

[0027] L=k1D w

[0028] Where: k1 is a coefficient, with a value of 0.5 to 1.5.

[0029] In the design method for the structural parameters of the large cylindrical roller bearing cage, step four involves determining the cage's crossbeam parameters through the following steps:

[0030] Step 4(a), the segmented cage includes n pockets and a crossbeams for setting axial wear-reducing blocks, preferably a=3. The number of cage pockets n is determined by the following formula:

[0031]

[0032] The minimum lintel width B of the cage is initially determined using the following formula. min :

[0033] B min =-7+4.3ln(D) w -0.2), D w ∈[10,150]

[0034] The minimum beam width B is checked and analyzed using multibody dynamics or the finite element method. min The maximum stress condition of the cage is determined, and the maximum stress does not exceed the fatigue limit of the cage body material. The difference between the width of the axial wear-reducing block and the width of the ordinary crossbeam is δ, and δ = 10~15mm is selected.

[0035] Step 4 (2), the width of the lintel is determined by the following formula:

[0036]

[0037] Step 4 (3), set the width of the axial wear-reducing block's crossbeam to satisfy the following constraint:

[0038] B weld =B+δ.

[0039] In the design method for the cage structure parameters of the large cylindrical roller bearing, step five involves calculating the bearing life and verifying the rated static load of the bearing. If the bearing life or safety factor does not meet the design requirements, the process returns to step three to recalculate. If there is no cage segment number N that meets the requirements, the process returns to step two to recalculate until the bearing life and safety factor meet the design requirements.

[0040] In step six of the design method for the structural parameters of the large cylindrical roller bearing cage, other structural parameters of the cage are determined by the following method:

[0041] Step 6 (a), maintain the width B of the cage beam e The formula for determining it is:

[0042] B e = (1.1~1.5)B

[0043] Step 6 (II), retainer radial wear reduction block thickness B af The formula for determining it is:

[0044] B af = (0~1.5)B

[0045] Step 6 (3), the formula for determining the thickness of the cage body is:

[0046] H = (0.35 ~ 0.55)D w

[0047] For a cage with a straight pocket, the total cage thickness H1 = D w -(2~6); For the cage of the guide roller, the total thickness of the cage H1=H;

[0048] Step six (iv), the method for determining the parameters of the cage overrun groove is as follows: select the overrun groove type according to the machining capacity, and the parameters a, b, r u The selection should avoid interference between the cylindrical roller fillet radius R and the cage runout groove; where parameter a should be as small as possible, and parameter r... u Take a larger value to reduce stress concentration;

[0049] Step 6 (5), retain the side clearance d of the bracket pocket. s No more than 2mm, end face gap d e No more than 2mm.

[0050] The design concept of this invention is:

[0051] To address the issue that the design of large cylindrical roller bearing cages often fails to adequately consider complex operating conditions, resulting in suboptimal cage strength, wear resistance, and impact resistance, and making them prone to wear and breakage, this invention provides a novel method for designing the structural parameters of large cylindrical roller bearing cages. By systematically determining various structural parameters of the cage, the normal operation and service life requirements of large cylindrical roller bearings can be guaranteed.

[0052] This invention systematically and in detail designs the key structural parameters of the cage for large cylindrical roller bearings, taking into full account factors such as the spatial size limitations of the bearing, the parameters of the rollers, and the operating conditions. By using parametric design methods, the structural parameters of the cage are closely integrated with the performance requirements of the bearing.

[0053] During the design process, we not only focus on the structural strength and performance of the cage itself, but also pay attention to the matching relationship between the cage and the rollers. By accurately determining the structural parameters such as the crossbeam, crossbeam, and pocket, we optimize the load-bearing capacity and operational stability of the cage, thereby improving the service life and reliability of the entire bearing.

[0054] The advantages and beneficial effects of this invention are as follows:

[0055] 1. This invention combines the structural parameter design of the cage and cylindrical rollers to ensure a good match between the cage and the cylindrical rollers, guaranteeing that the large cylindrical roller bearing has sufficient load-bearing capacity under various complex working conditions. Moreover, by adopting parametric design methods, the design cycle can be significantly shortened, design parameters can be efficiently determined, and dimensional constraints can be provided for the subsequent structural design of the large roller bearing rings.

[0056] 2. This invention effectively improves the structural strength and wear resistance of the cage by precisely designing parameters such as the width of the crossbeam, the width of the crossbeam, and the thickness of the wear-reducing block, thereby reducing the risk of wear and damage under complex working conditions and extending the service life of the bearing. At the same time, the reasonable structural parameter design can ensure the good distribution and movement of the rollers in the cage, reduce noise and vibration during bearing operation, and improve operational stability.

[0057] 3. This invention comprehensively considers the operating conditions of large cylindrical roller bearings under complex working conditions, including the influence of different loads, speeds and temperatures on cage performance. By checking bearing life and safety factors, it ensures that the designed cage can operate reliably under various complex working conditions and meet the application requirements of large heavy-duty bearings. Attached Figure Description

[0058] Figure 1 These are the key structural parameters of the cage. (a) is the front view, and (b) is the AA section view of (a).

[0059] Figure 2 The image shows the cage pocket overrun groove pattern. (a) is a top view of the cage, and (b) is a cross-sectional view of the cage.

[0060] Figure 3 Flowchart for cage structure parameter design.

[0061] Figure 4 A axial view of the finished main propulsion cage of the large main bearing of a tunnel boring machine.

[0062] Figure 5 A axial view of the finished radial cage of the large main bearing of a tunnel boring machine. Detailed Implementation

[0063] In its specific implementation, this invention first determines the pitch circle diameter D0 of the cylindrical rollers based on the geometric dimensions of the large cylindrical roller bearing, and then preliminarily selects the nominal diameter D of the cylindrical rollers. w Nominal length L w The number of roller rows i, the number of cages N, the remaining circumferential arc length L, the number of pockets n, the number of crossbeams a for setting the axial friction-reducing blocks a, the crossbeam width B, and the crossbeam width B for welding the friction-reducing blocks B. weldBy verifying bearing life and safety factors, the nominal diameter D of the cylindrical rollers that meets the design requirements for large cylindrical rollers was finally determined. w Nominal length L w The number of roller rows i, the number of cages N, and other structural parameters.

[0064] like Figures 1-3 As shown, the design method for the structural parameters of a large cylindrical roller bearing cage is achieved through the following steps:

[0065] Step 1: Determine the pitch circle diameter D0 of the cylindrical roller distribution based on the space size constraints.

[0066] Step 2: Referring to the standard, determine the nominal diameter D of the cylindrical roller. w Nominal length L w The number of rollers, i, is selected.

[0067] Step 3: Determine the number of cage segments N based on the processing capacity, and determine the remaining circumferential arc length L using the following formula.

[0068] L=k1D w k1 is a coefficient, ranging from 0.5 to 1.5.

[0069] Step 4: Determining the parameters of the lintel.

[0070] Step four (a): The segmented cage includes n pockets and a crossbeams for mounting axial wear-reducing blocks, preferably a = 3. The number of cage pockets n is determined by the following formula.

[0071]

[0072] The minimum lintel width B of the cage is initially determined using the following formula. min :

[0073] B min =-7+4.3ln(D) w -0.2), D w ∈[10,150]

[0074] The minimum lintel width B was verified and analyzed using methods such as multibody dynamics and the finite element method. min The maximum stress on the cage is determined, and the maximum stress does not exceed the fatigue limit of the cage body material. The difference between the width of the crossbeam with the axial wear-reducing block and the width of the ordinary crossbeam is δ, and δ is selected as 10-15mm.

[0075] Step 4 (ii), the width of the lintel is determined by the following formula.

[0076]

[0077] Step 4 (3): Set the width of the axial wear-reducing block to meet the following constraint.

[0078] B weld =B+δ

[0079] Step 5: Calculate the bearing life and verify the bearing's rated static load. If the bearing life or safety factor does not meet the design requirements, return to Step 3 to recalculate; if there is no required number of cage segments N, return to Step 2 to recalculate until the bearing life and safety factor meet the design requirements.

[0080] Step Six: Determine other structural parameters of the cage.

[0081] Step 6 (a), maintain the width B of the cage beam e The formula for determining it is:

[0082] B e = (1.1~1.5)B

[0083] Step 6 (II), retainer radial wear reduction block thickness B af The formula for determining it is:

[0084] B af = (0~1.5)B

[0085] The formula for determining the thickness of the cage body is:

[0086] H = (0.35 ~ 0.55)D w

[0087] Step 6 (3), for the cage with a straight pocket, the total cage thickness H1 = D w -(2~6); For the cage of the guide roller, the total thickness of the cage is H1=H.

[0088] Step six (iv), the method for determining the parameters of the cage overrun groove is as follows: select the overrun groove type according to the machining capacity, and the parameters a, b, r u The selection should avoid interference between the cylindrical roller fillet radius R and the cage runout groove. Specifically, parameter a should be as small as possible, and parameter r... u A larger value is chosen to reduce stress concentration.

[0089] Step 6 (5), retain the side clearance d of the bracket pocket. s No more than 2mm, end face gap d e No more than 2mm.

[0090] The technical solutions of the present invention will be clearly and completely described below with reference to the embodiments of the present invention. The following embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0091] Example 1:

[0092] Taking the large main bearing of a tunnel boring machine with an outer diameter of Φ7.6m as an example, the basic process of main thrust cage design is explained.

[0093] Step 1: Based on the space constraints, determine the pitch circle diameter D0 of the cylindrical roller distribution to be 6978mm.

[0094] Step 2: Select the nominal diameter D of the cylindrical roller according to the standard. w =120mm, nominal length L w =120mm, number of roller rows i=2.

[0095] Step 3: Based on the processing capacity, determine the number of cage segments N = 15, and the remaining circumferential arc length L = k1D w =100mm, k1 is a coefficient, ranging from 0.5 to 1.5.

[0096] Step 4: Determining the parameters of the lintel

[0097] Step 4(a): Based on the number of rollers, determine the number of pockets n=10 for a single segmented cage, preferably the number of crossbeams a=3 for setting the axial wear-reducing blocks.

[0098] Step 4 (II), based on The width of the lintel is determined to be B = 16mm.

[0099] Step 4 (3): Based on B weld =B+δ, determine the width B of the axial wear-reducing block. weld =26mm.

[0100] Step 5: Calculate and verify the bearing life and rated static load according to standard GB / T6391 "Rated Dynamic Load and Rated Life of Rolling Bearings" and standard GB / T4662 "Rated Static Load of Rolling Bearings", and ensure that they meet the requirements.

[0101] Step 6: Determine other structural parameters of the cage.

[0102] Step Six (I), based on B e = (1.1~1.5)B, determine the beam width B e =22.5mm.

[0103] Step 6 (II), based on B af = (0~1.5)B, determine the radial inner and outer grinding block thickness B af =7mm.

[0104] Step 6 (3), based on H = (0.35~0.55)D w and H1=D w -(2~6), determine the thickness of the main body of the cage as H=65mm, and the total thickness of the cage as H1=115mm.

[0105] Step 6 (iv): Select the type of overrun groove based on the processing capacity, parameters a, b, r. u The selection should avoid interference between the cylindrical roller fillet radius R and the cage runout groove. Specifically, parameter a should be as small as possible, and parameter r... u A larger value is chosen to reduce stress concentration.

[0106] The cage parameter a = 7mm.

[0107] The cage parameter b = 5.2 mm.

[0108] cage parameter r u =8mm.

[0109] Step 6 (5), the side clearance d of the pocket s =1mm, end face gap d e =2mm.

[0110] like Figure 4 As shown, after designing the above structural parameters, the finished product of the main thrust cage of the large main bearing of the tunnel boring machine with an outer diameter of Φ7.6m was obtained.

[0111] Example 2:

[0112] Taking the large main bearing of a tunnel boring machine with an outer diameter of Φ7.6m as an example, the basic process of radial cage design is explained.

[0113] Step 1: Based on the space constraints, determine the pitch circle diameter D0 of the cylindrical roller distribution to be 7137mm.

[0114] Step 2: Select the nominal diameter D of the cylindrical roller according to the standard. w =50mm, nominal length L w =85mm, number of roller rows i=1.

[0115] Step 3: Based on the processing capacity, determine the number of cage segments N = 23, and the remaining circumferential arc length L = k1D w =60mm, k1 is a coefficient, ranging from 0.5 to 1.5.

[0116] Step 4: Determining the parameters of the lintel

[0117] Step 4(a): Based on the number of rollers, determine the number of pockets n=16 for a single segmented cage, and preferably the number of crossbeams a=3 for setting the axial wear-reducing blocks.

[0118] Step 4 (II), based on The width of the lintel is determined to be B = 11.58 mm.

[0119] Step 4 (3): Based on B weld =B+δ, determine the width B of the axial wear-reducing block. weld =22mm.

[0120] Step 5: Calculate and verify the bearing life and rated static load according to standard GB / T6391 "Rated Dynamic Load and Rated Life of Rolling Bearings" and standard GB / T4662 "Rated Static Load of Rolling Bearings", and ensure that they meet the requirements.

[0121] Step 6: Determine other structural parameters of the cage.

[0122] Step Six (I), based on B e = (1.1~1.5)B, determine the beam width B e =21mm.

[0123] Step 6 (II), based on B af = (0~1.5)B, determine the radial inner and outer grinding block thickness B af =7mm.

[0124] Step 6 (3), based on H = (0.35~0.55)D w and H1=D w -(2~6), determine the thickness of the main body of the cage as H=22mm.

[0125] Step 6 (iv): Select the type of overrun groove based on the processing capacity, parameters a, b, r. u The selection should avoid interference between the cylindrical roller fillet radius R and the cage runout groove. Specifically, parameter a should be as small as possible, and parameter r... u A larger value is chosen to reduce stress concentration.

[0126] The cage parameter a = 2.4 mm.

[0127] The cage parameter b = 2 mm.

[0128] cage parameter r u =3mm.

[0129] Step 6 (5), the side clearance d of the pocket s =1mm, end face gap d e =1mm.

[0130] like Figure 5 As shown, after designing the above structural parameters, the finished radial cage of the large main bearing of the tunnel boring machine with an outer diameter of Φ7.6m was obtained.

[0131] The results show that this invention provides a basis for designing key structural parameters of cages for large bearings such as tunnel boring machine main bearings, port machinery bearings, and tower crane slewing bearings, achieving a good match between the cage and the cylindrical rollers and ensuring the stable operation of large cylindrical roller bearings. The design method of this invention effectively solves problems such as insufficient cage structural strength, poor wear resistance, and low design efficiency in existing technologies, significantly improving the service life, reliability, and operational stability of large cylindrical roller bearings, and providing a more advanced and effective technical means for bearing design and manufacturing.

Claims

1. A method for designing structural parameters of a large cylindrical roller bearing cage, characterized in that, Includes the following steps: Step 1: Determine the pitch circle diameter D0 of the cylindrical roller distribution; Step 2: Determine the nominal diameter D of the cylindrical roller. w Nominal length L w And the number of rollers, i; Step 3: Determine the number of cage segments N and the remaining circumferential arc length L; Step 4: Determine the cage lintel parameters; Step 4 (a): Determine the number of cage pockets n and the number of crossbeams a used to set the axial wear-reducing blocks; Step 4 (II): Determine the width B of the cage lintel; Step 4 (3): Determine the width B of the cage welding friction reduction block overbeam. weld ; Step 5: Check the bearing life and safety factor. If the design requirements are not met, return to Step 3; if there is no N that meets the requirements, return to Step 2. Step Six: Determine other structural parameters of the cage; Step 6 (a), determine the width B of the cage beam. e ; Step 6 (II): Determine the thickness B of the radial wear-reducing block of the cage. af ; Step 6 (3): Determine the main body thickness H of the cage and the total thickness H1 of the cage; Step 6 (iv): Determine the cage overrun groove parameters a, b, r u ; Step 6 (5): Determine the cage pocket clearance d s and d e .

2. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step one, the pitch circle diameter D0 of the cylindrical rollers is determined based on the spatial size constraints of the cylindrical roller bearing.

3. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step two, the nominal diameter D of the cylindrical roller... w Nominal length L w The number of roller columns i is selected according to the standard.

4. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step three, the number of cage segments N is determined based on the processing capacity, and the remaining circumferential arc length L is determined by the following formula; L=k1D w Where: k1 is a coefficient, with a value of 0.5 to 1.

5.

5. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step four, the cage lintel parameters are determined through the following steps: Step 4(a), the segmented cage includes n pockets and a crossbeams for setting axial wear-reducing blocks, preferably a=3. The number of cage pockets n is determined by the following formula: The minimum lintel width B of the cage is initially determined using the following formula. min : B min =-7+4.3ln(D w -0.2) D w ∈[10,150] The minimum beam width B is checked and analyzed using multibody dynamics or the finite element method. min The maximum stress condition of the cage is determined, and the maximum stress does not exceed the fatigue limit of the cage body material. The difference between the width of the axial wear-reducing block and the width of the ordinary crossbeam is δ, and δ = 10~15mm is selected. Step 4 (2), the width of the lintel is determined by the following formula: Step 4 (3), set the width of the axial wear-reducing block's crossbeam to satisfy the following constraint: B weld =B+δ.

6. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step five, the bearing life is calculated and the rated static load of the bearing is checked. If the bearing life or safety factor does not meet the design requirements, return to step three to recalculate. If there is no required number of cage segments N, return to step two to recalculate until the bearing life and safety factor meet the design requirements.

7. The method for designing structural parameters of a large cylindrical roller bearing cage according to claim 1, characterized in that: In step six, the other structural parameters of the cage are determined using the following method: Step 6 (a), maintain the width B of the cage beam e The formula for determining it is: B e =(1.1~1.5)B Step 6 (II), retainer radial wear reduction block thickness B af The formula for determining it is: B af =(0~1.5)B Step 6 (3), the formula for determining the thickness of the cage body is: H=(0.35~0.55)D w For a cage with a straight pocket, the total cage thickness H1 = D w -(2~6); For the cage of the guide roller, the total thickness of the cage H1=H; Step six (iv), the method for determining the parameters of the cage overrun groove is as follows: select the overrun groove type according to the machining capacity, and the parameters a, b, r u The selection should avoid interference between the cylindrical roller fillet radius R and the cage runout groove; where parameter a should be as small as possible, and parameter r... u Take a larger value to reduce stress concentration; Step 6 (5), retain the side clearance d of the bracket pocket. s No more than 2mm, end face gap d e No more than 2mm.

Images