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GB/T4662-2003/1SO761987
This standard is equivalent to I5076:1987 rolling bearing rated static load code> (English version). Including its amendment [S076:1587/Amdl.1:19SS dynamic bearing rated static load correction 1: Yanglu A basic rated static load before the small discontinuity> (English version of this standard replaces GB/4552-1D03 dynamic bearing rated static load>. For the convenience of other use, this standard has made the following editorial changes: the term "this international standard" is changed to "this standard", the decimal point symbol ", " is used instead of the decimal point symbol \, \ avoid the international standard! | |tt||Move the "Introduction" in the main text of the international standard to the front of the main text of the standard, and incorporate the international standard version into the text as the technical mark. The modified content is marked with a vertical double line (Ⅱ) at the margin of the relevant clause! In Appendix A, "This standard" replaces the "ISO76:1987" in the standard version with "TSO75". Compared with GB/T4668-1993, the main changes of this standard are as follows: 1. The standard layout is modified in accordance with GB/T1.1-2000. 2. The content of Appendix A of the original standard is moved to the introduction of this standard (Appendix A of the 1893 version. Introduction of this version), 2.2 and 2.3 are added with annotations (see the previous pages of 2.2 and 2.3) F-1. Added the English names of terms (see Chapter 2), added the informative reference "Breakage points in basic static load calculation" (see Appendix A). Appendix A of this standard is informative.
This standard is proposed by the China Machinery Industry Federation and is under the jurisdiction of the National Technical Committee for Standardization of Tubular Bearings (CSBTS/RC98). The drafting unit of this standard is Luoyang Bearing Research Institute. The main drafter of this standard is Ma Xiqing.
The previous versions of the standards replaced by this standard are: GB/T4662-1984. GB/T4662:1993.
GB/T4662-2003/15076:1987
When a rolling bearing is subjected to a static load above medium, its rolling element will produce permanent deformation. The amount of deformation is proportional to the increase in load. .
For the bearings selected for each specific application, it is often unrealistic to confirm whether the deformation of the bearings is allowable through a large number of auxiliary bearing tests. Therefore, other methods should be used to determine whether the selected bearings are suitable. Experience shows that in most applications, the bearing can allow a total permanent deformation of 0.1 times the rolling element diameter at the center of the moving element and the raceway to ensure that it will not have a significant impact on the future operation of the shaft. Therefore, the static load that causes such a permanent deformation is specified as the rated static load of the bearing. Experiments show that under the basic static load, the bearing will produce a load equivalent to the following calculated load at the center of the moving element and the raceway contact:
4600MPa1) self-aligning ball bearing;
4KPu all other ball bearings
4000MPa all rolling bearings.
The calculation formula and coefficient of basic rated static load are based on these contact stresses. According to the requirements of running stability and efficiency and the actual surface geometry, the allowable equivalent static load can be less than, equal to or greater than the rated static load. Bearing users who lack experience in this area should consult the bearing manufacturer. 1) 1 Mlg1 N/mm.
1 Standard
Moving bearings
Rated static load
GH/T4662-—2003/1S076.1987
This standard specifies the calculation method of basic rated static load and equivalent static load for dynamic bearings. This standard applies to rolling bearings whose size specifications comply with the relevant national standards, are made of high-quality hard steel, are manufactured according to good processing methods, and the shape of the dynamic contact surface is basically the required design. This standard is not applicable to bearings with other use conditions or (and bearing internal structure) where the contact area between the moving body and the raceway is clearly limited: if calculated according to this standard, satisfactory results cannot be obtained. Similarly, this standard is not applicable to situations where the load in the bearing is abnormally distributed due to other use conditions, such as film tilting, accumulation or excessive clearance. If this situation occurs, you should consult with the bearing manufacturer on how to calculate the load. This standard is also not applicable to bearings where the moving body directly contacts the shaft. or shaft mounting surfaces, unless these surfaces are equivalent in all respects to the raceway surfaces of the same type of bearings. For double-row radial bearings and double-row thrust bearings, if this standard is used, their construction shall be compatible. 2 Definitions
The following definitions are relevant to this standard.
Static load atakkoed
Bearing sleeve micro-diameter This relative speed is the load acting on the bearing, 2.2
Basic frequency static chain recommendation basic tt||The radial load equivalent to the following contact stress is generated at the center of the contact between the rolling element and the raceway under maximum load. 400MPa Self-aligning ball bearing:
42D0MPa; other types of radial ball bearings, 4000MPa radial load. For single-row angular contact ball bearings, the radial rated load is the radial load that causes pure radial displacement of the bearing circumference relative to each other. The load is called the permanent displacement of the moving body and the liquid by the shaft bottom force system, which is about 0.0001 of the moving body diameter. 2.3
Axial basic static load The central axial load equivalent to the following contact stress is produced at the contact center of the rolling element and the raceway under heavy load. -42noMP thrust ball bearing, -4(I00MPg thrust sub-bearing.
Note: These contact stresses refer to the virtual stress when the total permanent deformation of the rolling element and the fluid channel is about 0.0001 of the moving body diameter. 2.4
Radial equivalent load
staticeguivalertradial loe
refers to the radial static contact stress produced at the contact center of the rolling element and the raceway under heavy load and the actual load. GB/T 4682--2003/S0 76.1987
Axial equivalent static load
ntatlc cqavaleBt axtal Jead
is the central axial load that produces the same contact stress as the actual load at the center of the maximum load and the roller. The
true weight is used for the calculation of the load. The
diameter is the diameter installed in the middle.
Note that for the following figure, this diameter is the average of the diameters of the large and small rollers. For non-conforming rollers, the minimum diameter at the zero-load contact point is effectively taken. The 2.7
roller length is used for the calculation of the load. The roller length is the length of the roller in contact with the roller. 2. B
nominal tnqtact angle
nominal tnqtact angle
the angle between the plane perpendicular to the bearing line and the resultant force acting on the bearing. 2.9
pitchdiameler
pitchdiameler of a hull set The diameter of a hull set containing the center of a row of balls in the bearing. 2. 9. 2
pltcacdiasteter ofa roler The most common diameter in the bearing series, the diameter of the roller shaft, 3 symbols
C---net basic load, N,
Lo--net basic load, N,
D ball diameter mm
Dm diameter, mm
Yuan--roller diameter used for load calculation, mm roller length calculated by the lower limit,
F--bearing radial load of the radial outer disk NF, bearing axial section of the actual load of the axial component of the bearing N; Pa--radial load. N;
P-equivalent static load. N,
auxiliary heat coefficient N
GB/T4662-2003/IS07619B7
Z..- number of rolling elements in a single-row bearing + number of rolling elements in each row in a multi-row bearing with the same rolling elements in each row; Formula 1 - coefficient related to the shape and application level of bearing parts
(nominal contact of shaft and disk).
4 Radial ball bearing
4. 1 Basic radial load section
The basic radial load section of a radial ball bearing is calculated as follows: C. - fZDEc
The values in the formula are given in Table 1. The formula is applicable to radial contact and angular contact ball bearings with an inner radius of curvature not exceeding 0.5 and an outer groove curvature not exceeding 53, as well as radial ball bearings with an inner radius of curvature not exceeding 0.53D. Using a groove radius smaller than the above value may not necessarily increase the bearing capacity. However, using a raceway groove radius greater than the above value will reduce its bearing capacity. For the latter, use an appropriately smaller radius. 4.1.1 Wheel assembly
4.1.1.1 For two sets of identical single-row radial contact or angular contact ball bearings, which are arranged "back to back" or "box to box", they are installed (in pairs) on the same shaft and run as a whole. The radial static load required is the static load of two single-row bearings. 4.1.1.2 For two or more sets of identical single-contact or angular contact ball bearings, which are arranged in series and installed as a unit, the rated static load of the bearing set is equal to the basic static load of the single-row auxiliary bearing multiplied by the number of bearing sets. The rated static load of the ball bearing is equal to the f value of the thrust bearing and the vertical torsion and lifting force of the bearing. 2
GB/T4662—2003/1SO76,1987
Change 1 (rotation)
Self-centered bearing
Interchangeable and angular contact groove ball bearing
f: The most
two-center ball bearing flexibility
thrust spicy flight
, this table is based on the Herz point contact formula. The elastic modulus is 2.07×10MPa. The sinking ratio is 0.3. For the center ball bearing, the maximum bearing weight in the load distribution is 5
Zsing·Series
For the thrust ball bearing, the load distribution is set to the largest bearing weight in the middle of the load distribution. The contribution of the ball is D; the middle is 1 The value can be obtained by linear internal index. 4.2 Radial equivalent static load
Radial ball bearing radial equivalent static load is the larger of the following two formulas: PX, F, +, F
where X, and Y are given in Table 2.
Radial ball bearing: and
Light contact inner bearing
Hu A bearing
. The maximum follow-up speed of F/C is faster than the bearing design (internal groove tracking speed) o, s
Double-row shaft
i,44cnta
4,2.1 Bearing matching
GB/T4662—2003/ISO7611987
4,2.1.1 For two identical single-row radial contact angular contact ball bearings, they are arranged in a "face-to-face" or "face-to-face" configuration, installed side by side (in pairs) on the same shaft as two units. When calculating their equivalent static load in the longitudinal direction, X, and. The values of F and F of the double-row shaft should be calculated according to the total load acting on the bearing set. 4.2.1.2 For two or more sets of identical single-row radial contact or angular contact groove bearings, they are arranged in a "matched" or "face-to-face" configuration, installed side by side (in pairs) and installed on the same shaft as two units. When calculating the equivalent static load of the bearing as a whole, X, and, the values of the single bearing are used, and the total load acting on the bearing assembly is calculated as follows: 5 Thrust ball bearings
5.1 Basic axial radial load
The basic axial radial load of a single or double thrust ball bearing is calculated as follows: Cf,ZDieina
Where:
f. —From Table 1;
2—The number of balls bearing the load in one direction. This formula is applicable to bearings with a coefficient radius not greater than 4D. Using a raceway curvature radius less than the above value will not necessarily increase the bearing capacity of the bearing, but using a raceway curvature radius greater than the above value will reduce its bearing capacity. For the latter, an appropriately smaller one should be used. 5.2 Equivalent axial static load For thrust ball bearings with a rated load of 90°, the axial static load is calculated as follows: Po,-2.3F,tana+F
For double-direction bearings, this formula is applicable to all F/F values. For single-direction bearings, this formula is valid when F,/F,≤0.44cota. When F,/F, increases to 0.67cota, this formula can still produce a satisfactory P value, but it is not conservative enough. Thrust ball bearings with a rated load of
=\ can only withstand the maximum axial load. The equivalent static load of this type of bearing is calculated as follows: PF
6 Radial basic static load for radial bearingsWww.bzxZ.net
6.1 Radial basic static load for radial bearings
The radial basic static load rating of radial bearings is calculated as follows: u, - 44(1- Pgco)zt. 6.1.1/Shaft assembly 6.1.1.1 For two sets of alternate single-row bearings, mounted in a "back-to-back" or "face-to-face" configuration (mounted in pairs) on the same shaft as a whole, their basic radial static load rating is twice the static load rating of a single-row bearing. 6.1.1.2 For single-row roller bearings of equal width or more, arranged in a "linked" configuration, mounted side by side (mounted in pairs or groups) on the same shaft as a whole, the selection accuracy and installation accuracy can ensure that the load is evenly distributed. The basic radial static load rating of the bearing group is equal to the basic radial static load of the single-row bearing multiplied by the bearing equivalent static load. 6.2 For roller bearings with radial equivalent static load greater than 0, the smaller radial static load is the larger of the following calculated values: Ph, = X,F, -YF,
Prr= The values of x, and, in the formula F are given in Table 3. The values of GB/E4662-2003/INO76.1987 and 3 are the equivalent values of the radial load of the radial sub-bearing. The equivalent radial load of the radial sub-bearing is calculated by the following formula: P=F
. This shows the relationship between the ability of the radial sub-bearing to bear the radial load and the bearing design method. Therefore, when the 0" contact bearing is subjected to the shaft, the user should ask the shaft for the equivalent static force. 6.2.1 Bearing assembly
6.2.1.1 For two sets of single-row angular contact roller bearings facing each other, they are arranged in a "back-to-back" manner and installed side by side (in pairs) on the same racket as a whole. When calculating their load, X, Y, and F are calculated according to the total load acting on the bearing group.
6.2.1.2 For two sets of single-row angular contact roller bearings with the same inductance, they are arranged in a "single-joint" manner and installed directly (in pairs). When the bearings are installed on the same axis and run as a unit, the radial static load is calculated. The values of the X and Y bearings are single bearings, F, and F are calculated according to the total load on the bearing assembly. 7 Thrust bearings
7.1 Basic axial static load
The basic axial static load of single and double thrust bearings is calculated according to the following formula: DoaZuDsin
G=520(1-
Where:
2--Number of bearings in the same direction. When the length of the bearing is different, the length of all bearings to be loaded in the same direction shall be calculated according to the provisions of 2.7. 2. 1.1 Auxiliary bearing assembly
For two or more sets of identical one-way thrust bearings, they are matched in "linked" and installed side by side (in pairs or in disc sets) on one shaft as a rotating body. The manufacturing and installation accuracy can be guaranteed to be fully evenly distributed. The load on the auxiliary bearing assembly is equal to the static load of the one-way bearing multiplied by the number of bearing sets. 7.2 Static load of the auxiliary bearings. For the thrust bearings of the "axle", the static load of the auxiliary bearing is calculated as follows: Pu=2.ap,tana+F
For double bearings, this formula is applicable to all F/F values. For one-way shafts, when F/F 0.44nto, please adjust the formula: some F/F increases to 0.When the coefficient of return is 67, the recovery formula can give a satisfactory P value, but it is not conservative enough.
A tensile bearing with a load of 10 can only withstand the impact of the inner wall. The load reduction of this type of bearing is calculated according to the following formula: PawF
7.2.1 Shaft bearing
For two or more parallel roller bearings with the same bearing type, in a "single" arrangement, installed side by side (or oppositely or in series) on the same bearing as a whole, when calculating their axial static load, F, and F, are calculated according to the total load acting on the bearing group. Appendix A
(Informative Appendix)
Breakage points in the calculation of basic static load A.1 Breakage points in the calculation of basic static load for radial and thrust contact ball bearings GB/T4662-2003/ISO76:1987
According to the text of this standard, the breakage points used for calculation The coefficients for calculating the basic rated static load (C%) of radial and thrust angular contact ball bearings are slightly different. Therefore, there is a break in the calculation of the axial static rated load C% when the bearing with a sleeve contact angle of α-45 is regarded as a radial bearing (CurCa./Y) and when it is regarded as a thrust bearing. The appendix explains the reason for the difference in rated load coefficients and shows the method of recalculating the rated load so that accurate comparison can be made under the same conditions.
A2 Special number
The symbols given in the text of this standard and the following symbols are used in this appendix. Cou - Corrected basic axial rated static load of radial bearings (%45), NCmu - Corrected basic axial rated static load of thrust bearings (>45). N, n Radius of curvature of internal groove, nm ||t t||—Radius of curvature of outer groove, mm.
A.3 Calculation of static loads of radial and angular contact thrust ball bearings for different systems For angular contact thrust ball bearings, in the calculation of C, the fit between ball and raceway is: +n/D,≤0.64/r,/D.0,54 For angular contact radial ball bearings, in the calculation of C, the fit between ball and raceway is: /D0.52 and /D0.53. A.4 Comparison of basic axial rated static load correction values Ca and C for radial and angular contact thrust ball bearings For some applications, it is required that angular contact ball bearings with α>4\ and α>1\ have the same fit. Sometimes it is necessary to calculate and compare the actual axial loads. The basic rated static loads C and C can be calculated according to the text of this standard or obtained from the bearing manufacturer. The results are obtained from the product samples. However, as described in A, 3, different tightnesses are used for the calculation and comparison of radial and thrust bearings. If a correct comparison and comparison is required, the corresponding tightness should be used to calculate and C+ to calculate the correct axial static load C- and C. The calculation under two different tightness conditions can be completed with the help of formula (A1)-formula (A4\)-the tightness of radial and thrust bearings is in accordance with the provisions of the standard text. Only the axial load needs to be compared, because this is the slowest. Assuming that the contact angle is independent of the axial load and is constant, then the calculation accuracy will be reduced for bearings with small contact angles and variable loads:
A4.1 Angular contact radial bearings (/D, 0.52 vs. /D_U, 53)Cuu = Cn/Y.
Cou1.43C..
A.4.2 Angular contact thrust small bearing (r:/D=0.54 and r/D0.54) Cw - 0. fCu./Y.
GB/T4662—2003/15O76.1987
A5 Example
A5.1α-45\ bearing
The three 45\ angular contact ball bearings are regarded as radial bearings and thrust bearings respectively, and their modified axial basic statics are compared. Assume that the selected bearing (,cns)/Dm=0.16, the shaft has the tightness of the radial bearing, and according to Table 1, find f. =14.9, substitute it into the formula C=Kfacosa given in 4.1, and we get: C:KX 14.9 X cos45°- 10.54 KK is a constant, and the total number of bases it contains is the same for radial and thrust bearings. According to Table 2+, we get Y,=0.22
Special Cor and Y. Substitute it into formula (A.1) and we get: C=10. E4×K/0.22 =47, DK
According to Table 1, we get f. -48.8. Substitute 5.1 into the previous formula Co, = Kfsinz, and then according to formula (A2), we get: Cu = 1. 43 × K × 48.# × ain45° = 49,8 K. After recalculating the basic static load, the center. center indicates that there is no discontinuity point A, 5. 2α = 40\ and = B0. When calculating the axial basic static load of the two angular contact ball bearings = 40\ and = 0\, it is assumed that the two bearings have the same thrust bearing fit, D/D = 0.091, light weight P, * 7.3mt, precious number 7-27 for = 4U bearing (Dcus40) / N0, 091 × c0M0\ = 07. According to Table 1, f is obtained. =16.1According to Table 2, we get Y,026, substituting it into the formula given in 4,1, we get:
C=fiZD%rna = 1G, 1 X 27 × 7. 5t ×X caa4C*According to formula (A.3>, we get:
C-0.7×13731/0.26=50430N
C=50100N
For a60 bearing, (DcDs60°>/D=0.91×c0s60°=0.046: According to Table 1, we get f.=5%.82 Substituting it into the formula given in 5.1, we get,
Co.—f,ZDaina57.82×27×7.5Xsin60°=76049According to formula (.4,1), we get,
C==76 049 N
C=-76000N53) Cuu = Cn/Y.
Cou1.43C..
A.4.2 Angular contact thrust small bearing (r:/D=0.54 and r/D0.54) Cw - 0. fCu./Y.
GB/T4662—2003/15O76.1987
A5 Example
A5.1α-45\ bearing
The three 45\ angular contact ball bearings are regarded as radial bearings and thrust bearings respectively, and their modified axial basic statics are compared. Assume that the selected bearing (,cns)/Dm=0.16, the shaft has the tightness of the radial bearing, and according to Table 1, find f. =14.9, substitute it into the formula C=Kfacosa given in 4.1, and we get: C:KX 14.9 X cos45°- 10.54 KK is a constant, and the total number of bases it contains is the same for radial and thrust bearings. According to Table 2+, we get Y,=0.22
Special Cor and Y. Substitute it into formula (A.1) and we get: C=10. E4×K/0.22 =47, DK
According to Table 1, we get f. -48.8. Substitute 5.1 into the previous formula Co, = Kfsinz, and then according to formula (A2), we get: Cu = 1. 43 × K × 48.# × ain45° = 49,8 K. After recalculating the basic static load, the center. center indicates that there is no discontinuity point A, 5. 2α = 40\ and = B0. When calculating the axial basic static load of the two angular contact ball bearings = 40\ and = 0\, it is assumed that the two bearings have the same thrust bearing fit, D/D = 0.091, light weight P, * 7.3mt, precious number 7-27 for = 4U bearing (Dcus40) / N0, 091 × c0M0\ = 07. According to Table 1, f is obtained. =16.1According to Table 2, we get Y,026, substituting it into the formula given in 4,1, we get:
C=fiZD%rna = 1G, 1 X 27 × 7. 5t ×X caa4C*According to formula (A.3>, we get:
C-0.7×13731/0.26=50430N
C=50100N
For a60 bearing, (DcDs60°>/D=0.91×c0s60°=0.046: According to Table 1, we get f.=5%.82 Substituting it into the formula given in 5.1, we get,
Co.—f,ZDaina57.82×27×7.5Xsin60°=76049According to formula (.4,1), we get,
C==76 049 N
C=-76000N53) Cuu = Cn/Y.
Cou1.43C..
A.4.2 Angular contact thrust small bearing (r:/D=0.54 and r/D0.54) Cw - 0. fCu./Y.
GB/T4662—2003/15O76.1987
A5 Example
A5.1α-45\ bearing
The three 45\ angular contact ball bearings are regarded as radial bearings and thrust bearings respectively, and their modified axial basic statics are compared. Assume that the selected bearing (,cns)/Dm=0.16, the shaft has the tightness of the radial bearing, and according to Table 1, find f. =14.9, substitute it into the formula C=Kfacosa given in 4.1, and we get: C:KX 14.9 X cos45°- 10.54 KK is a constant, and the total number of bases it contains is the same for radial and thrust bearings. According to Table 2+, we get Y,=0.22
Special Cor and Y. Substitute it into formula (A.1) and we get: C=10. E4×K/0.22 =47, DK
According to Table 1, we get f. -48.8. Substitute 5.1 into the previous formula Co, = Kfsinz, and then according to formula (A2), we get: Cu = 1. 43 × K × 48.# × ain45° = 49,8 K. After recalculating the basic static load, the center. center indicates that there is no discontinuity point A, 5. 2α = 40\ and = B0. When calculating the axial basic static load of the two angular contact ball bearings = 40\ and = 0\, it is assumed that the two bearings have the same thrust bearing fit, D/D = 0.091, light weight P, * 7.3mt, precious number 7-27 for = 4U bearing (Dcus40) / N0, 091 × c0M0\ = 07. According to Table 1, f is obtained. =16.1According to Table 2, we get Y,026, substituting it into the formula given in 4,1, we get:
C=fiZD%rna = 1G, 1 X 27 × 7. 5t ×X caa4C*According to formula (A.3>, we get:
C-0.7×13731/0.26=50430N
C=50100N
For a60 bearing, (DcDs60°>/D=0.91×c0s60°=0.046: According to Table 1, we get f.=5%.82 Substituting it into the formula given in 5.1, we get,
Co.—f,ZDaina57.82×27×7.5Xsin60°=76049According to formula (.4,1), we get,
C==76 049 N
C=-76000N
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