GB/T 3480-1997 Calculation method for load capacity of involute cylindrical gears
Some standard content:
1, 21 200
National Standard of the People's Republic of China
GB/T3480-1997
eqv1so6336-1-~6336-3:1996
Calculation methods of load capacityFor involute cylindrical gears1997-12-30 Issued
1998-07-01 Implementation
National Education and Technical Supervision Week Issued
GB/T3480
....rrrr
3.1 Carryability and full coefficient
Main numbers
3.3 Classification of coefficients
English 4 formula
4.1 Tooth surface calculation according to period
The nominal force of the small wheel, the coefficient of the light gear is called the use factor K, the load distribution coefficient KK between the teeth, the load distribution coefficient KHKr between the teeth, the coefficient of the positive strain stress, the coefficient of the bending force, the internal strength and repair effect of the test wheel, the life coefficient Y, the influence coefficient of the lubricant film 22..7. The surface work load bearing factor Z.
Buy system effect 2.F,
Relative tooth root angle rate induction system effect Y:mIT
According to the tooth root table current cumulative cost Y:.aT
3 Wheel ladder strength calculation
Applicable range
9.2 Price adjustment and total adjustment coefficient
9.3 Xue driving speed calculation company
Supplement A (standard supplement)
Appendix B Appendix of the prompt;
Appendix C (Appendix of the prompt)
An Xiaoan signature test value
Working under variable speed load according to the calculation of the wheel green number Ye
Gu/T3480-1997
This standard is equivalent to the area standard 1506336-1--6331956 (gradient diagram gear and new wheel thermal capacity calculation, used to The national standard GB3430-180 issued in 183 and (B318093 state ratio · ~ standard who ± to make changes in the following aspects! Can be modified: adjust the actual bending neck environment of the blood opening Appendix A gives the "large-scale small bending through-degree special full coefficient is forbidden to consider the low at the same time for the special full coefficient according to the gold book value range, the whole in the random recording B under the variable load working environment calculation method, in the appendix (taekwondo full rim gear variable bending seat small calculation reference force method! Tooth distribution system effect uKn still use the English [to reach the method, the double-bridge analysis of the ticket system was made, # for (48-- of the asymmetric arrangement and product kidney bearing bone ratio formula style part improvement, moved to the 9-level situation of the chemical formula; c) in the material connection and bending fatigue frequency installation does not MX, ME, MQ, MI four relatives receive value line warning (R 34S-3 standard is based on the domestic material test results in the past ten years, and emphasizes the inspection of the material bending limit of the production drawing; d) in the compilation, the coefficients are clearly divided into "indicative load", "positive calculated stress" and "limited allowable layer force", and the calculation of GB%-13336:1996 is also revised for its individual coefficients, numerical errors, formulas and tables. In the two confirmations and approvals of the previous standard, corresponding notes were made for some obvious inconsistencies in the 13336:1993 version. Later, in 1806 (January 1806), the 13336:1396 version was officially approved by the Ministry of Education. The results proved that the standard was not up to standard: it was first issued in 1983. After revision, this standard was implemented from January 1398: H and replaced it at the same time. B348283. This standard is the appendix of the national standard: the requirements of B and C of the international standard. This standard is proposed by the Ministry of Machinery Industry of the People's Republic of China. This standard is jointly developed by the National Gear Standardization Technical Committee of the People's Republic of China, and the Zhengzhou Kaiban Standardization Institute of the Ministry of Machinery Industry of the People's Republic of China, Harbin University, Northeastern University, Beijing University of Science and Technology, China Mining Research Institute, Lefang Steam Turbine Factory, Nanfang Two-Gear Box and the Beijing Energy-saving Institute of Qinzhou. The leaders of this standard: Dingchuan, Jie Xiaokai, Lai Xiaokuai, Liu Zhongming, Li Daoshua, Xuanheli, Pao Shuhang, Chen Gongwen, Xin Jilai, Zhang Yuanguo, Mai Liangzhi.
1 Scope
National Standard of the People's Republic of China
Calculation method of bearing capacity of involute cylindrical gears Calcalutin mrthods uf luud cupacityfor involute cylindrical gearsCR/T 3460- 1997
eqv 1s0 6336-1.~6336-3:1996
代营GE3a0-
This standard is not applicable to dry steel, iron, basic gear which meets the internal and external fee standard of GD1357, material gear and artificial gear (double-agent must> delete piece gear fast action. Basic gear health and ratio 13568? Similar to gears, but with slightly different tooth shapes, their load-bearing capacity can also be calculated according to the standard. This standard includes two methods of calculation: tooth surface strength and tooth bending strength. The core method is: This standard stipulates that the corresponding gear precision standard is GB109588: 1. When using other slow precision standards, the relevant load coefficients can be calculated using the advanced method of this standard. This standard is the basis for various departments and industries to formulate gear load-bearing capacity calculation standards and specifications based on the relevant provisions of the standard. 2. Cited standards
The following texts contained in the standard are cited in this standard and constitute the text of this standard. When the standard is in full version, the version shown is valid: All standards will be revised, and the parties using this standard should explore the possibility of using the following standards for new versions. GB1356-57 New parallel line diagram column gear basic gear GB/T33749 Western gear basic terminology
GEH5SSH? Gear material heat treatment quality inspection and inspection of the general view G108S lifting line pull step gear degree
3 Overview
3.1 Reliability and safety system
Different use scenarios have different reliability requirements for gears. The reliability requirement of the gear is the most important. The reliability requirement of the gear is the most important. The reliability requirement is determined by comprehensive consideration of factors such as working requirements and push-up. Generally, the market is divided into the following situations. The gear with low reliability requirements has a long design life. The unimportant gear with low reliability requirements has a long design life. Although the reliability requirement is not high, the reliability requirement is not high. The reliability of this type of gear can be taken as 9%. ) The most reliable requirements for general gears and most of the lower industrial gears have certain requirements for design life and reliability. The reliability of this gear is generally not high. However, for commercial gears with higher reliability requirements, such as continuous operation and longer maintenance time or period, a failure may cause a serious loss of the whole gear or a safety accident. The reliability should be as high as 3.9%. ) High reliability requirements are required for gears with very high reliability under special working conditions. The reliability requirement is more than 9.3%. At present, the reliability theory has begun to design some machine domains and it is proved that only using strong safety factors cannot fully reflect the reliability level. However, there are still insufficient cases to treat each parameter as a random variable in gear design. Therefore, the recommended design data of the standard is treated as fixed value, and the strength safety coefficient or stress is still used as the criterion. The problem is to select the appropriate safety factor to control the working reliability of the transmission equipment. The National Technical Supervision Certificate 19971230 issued
1998-07-01 implementation
CR/F3480--1997
, the calculation results and the actual situation have certain deviations. In order to ensure the required reliability, the calculation must have the necessary safety margin. Obviously, the original data taken is not accurate. The more accurate the calculation method, the smaller the deviation between the calculation results and the actual situation. The required safety margin can not be fully reduced, and the economy and configurability are more unified. When selecting the safety factor, the following points need to be noted:) The gear material fatigue limit (.1 The long head effect is obtained when the year is 1. Reliability requirements are high: the full soft potential should be large, the call can be smaller, b) Under normal circumstances, this safety factor should be larger than the contact safety factor, and the broken tooth is more serious than the pitting corrosion, and the safety expansion of the bending degree or the safety data of the noise change can also be required. The recommended minimum safety factor for the same design method is not the same. There is no design report and the appropriate data is selected. If there is no available case data, the state can be selected from Appendix A (Appendix of the standard). For the gear data with higher reliability requirements under the same system, the designer makes a detailed analysis and usually stops the design system and the user agrees.
3.2 The main codes of this standard and their meanings and single codes are shown in Table 1. 1 Main codes
u adee
dr xchi:
center here, the standard tooth energy and height change tooth grab ten wishes the new both change with the center principle of the gear
calculate the tooth
node effect
by the title combined production of cattle tooth top quantity
age year tooth change point stiffness under the average borrow (obstacle combined stiffness): - for some single low day complete recording large stiffness (single series world brush 1 point
small light, large wheel safe diameter
heart wheel, large Yan world minister self-control
small pulp, human To unite straight
small flow, big expression again sincere
(people's nuclear quantity)
law network! The force
please use the name cut
and the name text on the moon on the surface such as to the small
world blood public
cut well to reach the people without
running piece period of this direction knowledge difference
change the public
create safety according to
N/(mm:xm)
IN/(u . um)
wide spread of people's leading should
Ji's strong
F= 9. 3 N when the female powerless
F- when the internal dimension should be in
GB/T 3480-.1997
table (key)
teaching medicine for children to eat the external point of the area, refers to the high
base car tooth this can be disease and tooth root high
extension use system test
impact by the magnetic calculation step and the scattered load distribution coefficient should be considered the normal step scattered before the weak number of the melting strength calculation step light distribution system dynamic resistance unique increase medical calculation of the monitoring four teaching medicine coefficient dynamic number Lemin
fast effect: equivalent new ticket
to read pulp
continental surface model
chengli ring model
small Yan, big grab the eggplant legacy
small wheel of critical transfer note
method book
edit two The base section and the effect of the unit tooth need to be soft and worry-free, but the surface is not flat "mouth point height, divided into four levels of safety factors for the calculation of bending strength. Each mountain strength makes the whole system of problems calculated by the hospital's attention room. According to the minimum safety service, the speed torque of the small wheel and the big wheel, the tooth number ratio =
kg/anm
Am-mm/N
Line speed period, the range of this degree can be divided into two levels. The good position of the big wheel will not be divided into two levels. The main system effect of the big wheel is GA/T 3480--1997.
Get the effect on the single point outside the world area when the tooth repair system social work
, the agent on the table mesh ratio of the natural effect
Compile a new single comparison of the area outside the point when the account should be stopped for the original two forces heat positive system
: try some steps of the wheel force. Effective
Cross curve welcome the degree meter shared by the tour family negative system tour
Curve required degree meter elastic amount combined to make the system effective
Internal rate elegant combined goods
Gear can be a product
Small test. Big single to contain the system teaching
Natural zero number| |tt||node area number
flash slip agent recording effect
according to the contact strength of the beads' warehouse calculation number
Eastern grain sub-system
speed coefficient
world three chemical system effect
technical type use slide rule: zero effect
report slip welcome dance practice free effect
according to the health strength calculation overlap system effect
small, human
tooth experience when the street number
through the project surface some collection year angle
single time step area interest point method can be surface action For the strict points in the joint area, the method of top force is the same as that of the force standard. For the points outside the four areas, the force outside the area is a small amount of force. The force is usually used by the medical team. The credit period is the same as the screw activity. The old state disease year of GB/T3480-1997 (complete) is reasonable for the external points of the teeth. tt||Heart guard door turn actual quantity
Lubricating oil benefit paste
: Lake Sang ratio
However, wind passes
Dangerous room internal semi-control
Tensile strength
Calculate the back seat force
Order the constant force within the month
Test the internal bending difficulty of the tooth inspection
Let the person connect
Calculate the connection position
Produce the contact area force
3.3 System micro classification and calculation items
ut/s esh)
The effects of the system in this standard are described in two categories:
a) The coefficients of the normal load can be determined by conventional methods, such as the coefficient of the small force. When the system effects are determined by the formula,
there are many factors that affect the system. These factors have certain meanings and are difficult to calculate accurately. For example, the number of positive loads K, K, and the coefficients of the normal loads: F. For the normal load, the best way is to conduct a detailed measurement or a mechanical analysis of the transmission system. It is also confirmed by the field experience of Sichuan University. At this time, the accuracy of the method adopted can be verified and its premise should be screened. When the above method is not feasible due to technical or economic reasons, one of the general methods (i.e., the chemical method) provided in this standard may be used to determine KKK and K(K); in case of disputes over the design results and calibration of non-essential gears, the force method shall prevail. For some high-precision dryers, the coefficients should be calculated first by the most accurate method or other methods. The coefficients should be calculated according to the appropriate order of effectiveness: a) calculate
b) calculate X(Km) with F, K, K.;
) calculate KHA with F, K, H. For the detailed calculation of the system, the independent variables of each sampling point and grid are not processed in the government value of the system, such as the oil film effect system 2, 2, ), and only the "small public force or experience effect spectrum" is provided. 4 Basic calculation formula
4.1 Tooth surface contact strength shuttle
GB/T 34801997
The calculation basis of the contact stress on the tooth surface in this standard is as follows: It is used to obtain the upper index of the stress on the tooth surface according to the contact pressure, but it is not the only reason for the occurrence of stress. If the size and direction of the force, the induction coefficient and the flow state are not specified in the stress calculation, these will affect the actual contact stress of the gear. When calculating the indirect strength of the gear, take the more reasonable value of the contact stress at the point and the limit point of the single pair of gears. The minimum and maximum allowable compensatory stresses should be calculated separately. The following formula is used for the internal contact of the gear: In the internal contact, the contact stress of the large and small gears is always equal. The analysis shows that the internal contact stress of the gear is equal to the contact stress of the gear. The maximum grounding force is the inner boundary point of the single pair of gears, the node center and the inner boundary point of the single pair of gears of the gear. The three characteristic points can be seen in Figure 12. The actual use and actual danger are clear. Except for the reasons mentioned above, the actual grounding force that produces the danger of the point usually occurs at point CD or its same (large gear) at point B or back (small gear) at the node area. The coefficient of force at the node C is 2: when the force at the inner boundary point of the single pair of gears exceeds the force at the node, that is, 2 is greater than 1. When determining the stress percentage of the gear and pinion, it should be multiplied by 7: when or 2, not greater than 1. When the gear is in the longitudinal direction, the contact force is large. When the gear is in the longitudinal direction, the contact force is large. The linear value of the spur gear with the same gear teeth and the helical step gear with a gear length of 1 is determined. 4. 1.1. The larger value of the calculated contact stress of the gear and the gear at the node and the boundary point of the single-pair connection area shall not be less than the calculated safety factor 5 of the small FFbZxz.net
or the contact stress. The corresponding minimum safety factor S, that is, Suhm
In the above two formulas, m\ is the calculated contact stress of the gear, N/mm. 4.1.2 SHe———the allowable contact stress of the gear, N/m m, see 4.1.3m--Calculation safety factor of contact strength, see 4.1.4: Shan
connection neck small safety metal system, see 3.1 and Appendix 4, 4.1.2 Calculation of the contact stress of the wheel and the big wheel is determined by the following two formulas: EZsdnK.K,KK
m--u/X,K.KHK
In the formula: K
Use the multiplication factor, then 6. 1
dynamic cost coefficient + see 6-21
tensile strength calculation can provide me with distribution coefficient see 6K
report contact strength juice between teeth batch load distribution system, see 6.4: small sores and fire wheel single pair of teeth amplitude total cumulative number, see 7.1.5; node some calculation response, basic value, use the following formula: adopt reading effort:
17 this light order mutual ISUE326 may appear in the group, small life is a quick certificate, Problem 6 of uneven force
Wu Zhong:
CE/T3480—1997
y=ZHZe2.2
Add the nominal tangent NW on the 4th index; 1. Make four senses m, refer to the smaller width of the small teeth in the wheel, the number of teeth is the number of nodes of the small and large teeth, 7.1.1:
Elastic coefficient/mm. State 7. 1.2;
world gear system, see 7.1.3;
domain load coefficient, see 7.1.4.
in the formula? "-\ external meshing transmission -\ pregnant gear transmission 4.1.3 allowable contact stress He
4. 7. 3. 1
general method
in the formula: ee
allowable contact limit force of gear, N/mm; test limit of contact deformation, N/mm, see 8.1; contact coefficient, %8.2.1; slip coefficient, 8.3.
speed load, see 8.5.1
height coefficient, see 8-3. 2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient · see 8.5.4.1.3-2 The method of flower
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 The system of 1 calculation of the whole system S
(6)
In the formula, the parameters are determined by the method and the chemical method respectively, and the S of the large and small wheels are calculated separately: the safety factor is not considered in the case of application. Li Zhou 3.1 and the calculation are respectively controlled by formula (7) and formula (3), 4.2 The gear root quality is unknown, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). When the load distribution is determined for each pair of wheels, it is an ideal method to use the above method to determine the position of the maximum root stress or the corresponding maximum root stress. This standard does not use the maximum destructive stress reported by the gear as the nominal bending stress, and uses it as the calculated gear stress after correction with the corresponding system. In view of the different use conditions, requirements and sizes, this standard uses the test bending limit after adjustment as the allowable internal stress. The technical standard tooth bending neck calculation formula is applicable to the gear with an internal friction edge of not less than 3 degrees. For gears that do not meet the above conditions, make a further analysis, and determine the root stress of the gear based on experiments or empirical data. If the above method cannot be used, refer to the "Approximate" Appendix. 4-2.1 Strength of the gear
CE/T 3480..1997
The calculated tooth root stress should not be less than the allowable stress, that is: or the basic factor of the self-learning degree should be rounded to not less than the effective weak send some small safety factor Sr5.
In the above two formulas, the calculated root stress of the gear, N/mm*, see 4.2.2; the allowable root stress of the gear, N/m, see 4.2.3; the calculated safety factor of curvature, see 4.2.4: including the small safety factor of curvature strength, see 3. 1 and 4.4.2-2 The root stress of the gear is determined by the following:
a=pf.R,KKI
R:, 4.1.2 said
is the load distribution system for calculating the typical strength, see 6.3.4: K:
K——the recommended distribution system for calculating the bending strength, see 6.41-the basic value of the root stress, /m, for large and small gears should be determined separately, <5)
This standard provides the following two basic calculation methods for determining the root stress. For those with high requirements for single gear calculation, method one shall be used first: When there is disagreement on the calculation results, method one shall prevail.) This method is based on the load as the external point of the single pair of tooth meshing area for calculation. The internal root should be determined by the formula:
Wu, -
Nominal axial force on the internal indexing diagram N: YeYy
Working tooth width (at the tooth root surface), m. When the large and small gears are not selected, the tooth width of the narrow teeth is taken as the working tooth width of the gear. For the small double helical gear 62, if the gear has a single helical gear, the tooth end can be trimmed or the shape is missing, and the center should be taken as a smaller value than the actual value:
Y-tooth shadow model when the load acts on the external point of the single pair of teeth meshing area, minus 7.2.2: Y--How to use the stress list for the external point of the single pair of teeth meshing area, see 7.2.2; frequency flag system, then 7.2.4.
b) Method 2: The wood method is to calculate the tooth root stress with load acting on the tooth element and the tooth root, which is only applicable to gear transmission of E2. The basic value of tooth root stress is determined by the following formula:
Where: Ye
The tooth coefficient when the load acts on the tooth element, see 7.2.1 The stress coefficient when the load acts on the tooth element, see 2.2; .. . The vertical coefficient of the typical strength calculation is shown in 7.2.3. The meaning of F, m and Y is the same as that of formula (L2). 4.2.3 The allowable gear seat small
1 for ten 23 can also be calculated by formula (12, but in this case, the external points of the double-joint area should be used as load points, single safety,
GR/T3480-1997
people, the allowable stress of the pinion and the root stress of the tooth should be determined separately. When using the data obtained based on the strength of the test gear, the allowable gear stress can be calculated by the following formula:
FFSPEISY'H.YAnltYR.TY|| tt||Where Set
Calculate the bending limit stress of a gear, N/mm2; Test gear tooth deformation performance, N/m3; Test gear stress coefficient, such as the estimated value given by the wooden probe, and then Ys2.0
Calculate the life energy coefficient of the bending strength seat, see 8.2.2; The minimum safety factor of strength is shown in 3.1 and Appendix A1; Relative root angle inductance coefficient, 8.6;
Relative tooth surface modification coefficient: 8.; Dimensional coefficient of bending strength base calculation, see 8:5.2. 4.2.4 Calculation of overall system efficiency Sm
Se Ca CrY one
For the explanation of the formula, see 4.2.2 and 4.2.3, the safety factors of large and small gears should be calculated separately. Different users should consider the safety factors according to 3.1 and calculation respectively according to Section 5) and or (11). 5. The nominal tangential force F
The nominal tangential force or torque transmitted by the small output gear is determined by: The nominal tangential force is the nominal tangential force on the upper end surface of the gear and the tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force on the upper end surface of the gear. The nominal tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force ... 549
When the nominal work transmitted is measured in PS,
...Gear reverse rotation/min
When the gear is under variable load, the stress and strength of the gear can be calculated according to the safety system. When there is no accurate and more reliable method and data, the calculation can be made by referring to the time record B. 5 The effect of positive load and gear tooth stiffness
6. 1 Use coefficient K.
Use coefficient, considering the system affected by the external dynamic load of the pinion, the external brake belt should be used. It can also be used by actual operation or import method. 16335196.2SHe————Allowable contact stress of gear, N/mm, see 4.1.3m-——Calculation safety factor of contact strength, see 4.1.4: Small safety system of contact strength, see 3.1 and Appendix 4, 4.1.2 Calculation of contact stress of gear and big wheel is determined by the following two formulas: EZsdnK.K,KK
m--u/X,K.KHK
In the formula: K
Use the multiplication factor, then 6. 1
dynamic cost coefficient + see 6-21
tensile strength calculation can provide me with distribution coefficient see 6K
report contact strength juice between teeth batch load distribution system, see 6.4: small sores and fire wheel single pair of teeth amplitude total cumulative number, see 7.1.5; node some calculation response, basic value, use the following formula: adopt reading effort:
17 this light order mutual ISUE326 may appear in the group, small life is a quick certificate, Problem 6 of uneven force
Wu Zhong:
CE/T3480—1997
y=ZHZe2.2
Add the nominal tangent NW on the 4th index; 1. Make four senses m, refer to the smaller width of the small teeth in the wheel, the number of teeth is the number of nodes of the small and large teeth, 7.1.1:
Elastic coefficient/mm. State 7. 1.2;
world gear system, see 7.1.3;
domain load coefficient, see 7.1.4.
in the formula? "-\ external meshing transmission -\ pregnant gear transmission 4.1.3 allowable contact stress He
4. 7. 3. 1
general method
in the formula: ee
allowable contact limit force of gear, N/mm; test limit of contact deformation, N/mm, see 8.1; contact coefficient, %8.2.1; slip coefficient, 8.3.
speed load, see 8.5.1
height coefficient, see 8-3. 2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient · see 8.5.4.1.3-2 The method of loss
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 1 Calculation of the whole system of the system S
(6)
In the formula, each parameter is determined by the stock method and the chemical method, and the S virtuality of the large and small wheels is calculated separately: the consideration of the safety factor in the case of no application is Li 3.1 and 4.2 respectively control the tooth root quality without knowing the basis, in principle, it can be determined by any available method (such as finite element method, engineering method, added load variation method) or width measurement (optical elastic measurement, variable measurement). After the load distribution of each pair of wheels is determined, it is an ideal method to use the above method to determine the maximum root stress or load position and its corresponding maximum root stress. This standard does not take the maximum destructive stress of the tooth as the nominal bending force, and after correction by the corresponding system, it is used as the calculated tooth increase force. Considering the different use conditions, requirements and sizes, this standard verifies the test deformation limit after adjustment as the allowable internal stress. The technical standard formula for calculating the bending depth of gear teeth is applicable to gears with an internal friction radius of not less than 3 mm. For gears that do not meet the above conditions, make an advanced analysis and determine the tooth root stress rate through experiments or empirical data. If the above method cannot be used, refer to the attached "Approximately correct" formula. 4-2.1 Strength of the gear
CE/T 3480..1997
The calculated tooth root stress should not be less than the allowable stress, that is: or the basic factor of the self-learning degree should be rounded to not less than the effective weak send some small safety factor Sr5.
In the above two formulas, the calculated root stress of the gear, N/mm*, see 4.2.2; the allowable root stress of the gear, N/m, see 4.2.3; the calculated safety factor of curvature, see 4.2.4: including the small safety factor of curvature strength, see 3. 1 and 4.4.2-2 The root stress of the gear is determined by the following:
a=pf.R,KKI
R:, 4.1.2 said
is the load distribution system for calculating the typical strength, see 6.3.4: K:
K——the recommended distribution system for calculating the bending strength, see 6.41-the basic value of the root stress, /m, for large and small gears should be determined separately, <5)
This standard provides the following two basic calculation methods for determining the root stress. For those with high requirements for single gear calculation, method one shall be used first: When there is disagreement on the calculation results, method one shall prevail.) This method is based on the load as the external point of the single pair of tooth meshing area for calculation. The internal root should be determined by the formula:
Wu, -
Nominal axial force on the internal indexing diagram N: YeYy
Working tooth width (at the tooth root surface), m. When the large and small gears are not selected, the tooth width of the narrow teeth is taken as the working tooth width of the gear. For the small double helical gear 62, if the gear has a single helical gear, the tooth end can be trimmed or the shape is missing, and the center should be taken as a smaller value than the actual value:
Y-tooth shadow model when the load acts on the external point of the single pair of teeth meshing area, minus 7.2.2: Y--How to use the stress list for the external point of the single pair of teeth meshing area, see 7.2.2; frequency flag system, then 7.2.4.
b) Method 2: The wood method is to calculate the tooth root stress with load acting on the tooth element and the tooth root, which is only applicable to E2 gear transmission. The basic value of tooth root stress is determined by the following formula:
Where: Ye
The tooth coefficient when the load acts on the tooth element, see 7.2.1, the stress coefficient when the load acts on the tooth element, see 2.2; .. . The vertical coefficient of the typical strength calculation is shown in 7.2.3. The meaning of F, m and Y is the same as that of formula (L2). 4.2.3 The allowable gear seat small
1 for ten 23 can also be calculated by formula (12, but in this case, the external points of the double-joint area should be used as load points, single safety,
GR/T3480-1997
people, the allowable stress of the pinion and the root stress of the tooth should be determined separately. When using the data obtained based on the strength of the test gear, the allowable gear stress can be calculated by the following formula:
FFSPEISY'H.YAnltYR.TY|| tt||Where Set
Calculate the bending limit stress of a gear, N/mm2; Test gear tooth deformation performance, N/m3; Test gear stress coefficient, such as the estimated value given by the wooden probe, and then Ys2.0
Calculate the life energy coefficient of the bending strength seat, see 8.2.2; The minimum safety factor of strength is shown in 3.1 and Appendix A1; Relative root angle inductance coefficient, 8.6;
Relative tooth surface modification coefficient: 8.; Dimensional coefficient of bending strength base calculation, see 8:5.2. 4.2.4 Calculation of overall system efficiency Sm
Se Ca CrY one
For the explanation of the formula, see 4.2.2 and 4.2.3, the safety factors of large and small gears should be calculated separately. Different users should consider the safety factors according to 3.1 and calculation respectively according to Section 5) and or (11). 5. The nominal tangential force F
The nominal tangential force or torque transmitted by the small output gear is determined by: The nominal tangential force is the nominal tangential force on the upper end surface of the gear and the tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force on the upper end surface of the gear. The nominal tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force ... 549
When the nominal work transmitted is measured in PS,
...Gear reverse rotation/min
When the gear is under variable load, the stress and strength of the gear can be calculated according to the safety system. When there is no accurate and more reliable method and data, the calculation can be made by referring to the time record B. 5 The effect of positive load and gear tooth stiffness
6. 1 Use coefficient K.
Use coefficient, considering the system affected by the external dynamic load of the pinion, the external brake belt should be used. It can also be used by actual operation or import. 16335196.2SHe————Allowable contact stress of gear, N/mm, see 4.1.3m-——Calculation safety factor of contact strength, see 4.1.4: Small safety system of contact strength, see 3.1 and Appendix 4, 4.1.2 Calculation of contact stress of gear and big wheel is determined by the following two formulas: EZsdnK.K,KK
m--u/X,K.KHK
In the formula: K
Use the multiplication factor, then 6. 1
dynamic cost coefficient + see 6-21
tensile strength calculation can provide me with distribution coefficient see 6K
report contact strength juice between teeth batch load distribution system, see 6.4: small sores and fire wheel single pair of teeth amplitude total cumulative number, see 7.1.5; node some calculation response, basic value, use the following formula: adopt reading effort:
17 this light order mutual ISUE326 may appear in the group, small life is a quick certificate, Problem 6 of uneven force
Wu Zhong:
CE/T3480—1997
y=ZHZe2.2
Add the nominal tangent NW on the 4th index; 1. Make four senses m, refer to the smaller width of the small teeth in the wheel, the number of teeth is the number of nodes of the small and large teeth, 7.1.1:
Elastic coefficient/mm. State 7. 1.2;
world gear system, see 7.1.3;
domain load coefficient, see 7.1.4.
in the formula? "-\ external meshing transmission -\ pregnant gear transmission 4.1.3 allowable contact stress He
4. 7. 3. 1
general method
in the formula: ee
allowable contact limit force of gear, N/mm; test limit of contact deformation, N/mm, see 8.1; contact coefficient, %8.2.1; slip coefficient, 8.3.
speed load, see 8.5.1
height coefficient, see 8-3. 2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient · see 8.5.4.1.3-2 The method of loss
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 1 Calculation of the whole system of the system S
(6)
In the formula, each parameter is determined by the stock method and the chemical method, and the S virtuality of the large and small wheels is calculated separately: the consideration of the safety factor in the case of no application is Li 3.1 and 4.2 respectively control the tooth root quality without knowing the basis, in principle, it can be determined by any available method (such as finite element method, engineering method, added load variation method) or width measurement (optical elastic measurement, variable measurement). After the load distribution of each pair of wheels is determined, it is an ideal method to use the above method to determine the maximum root stress or load position and its corresponding maximum root stress. This standard does not take the maximum destructive stress of the tooth as the nominal bending force, and after correction by the corresponding system, it is used as the calculated tooth increase force. Considering the different use conditions, requirements and sizes, this standard verifies the test deformation limit after adjustment as the allowable internal stress. The technical standard formula for calculating the bending depth of gear teeth is applicable to gears with an internal friction radius of not less than 3 mm. For gears that do not meet the above conditions, make an advanced analysis and determine the tooth root stress rate through experiments or empirical data. If the above method cannot be used, refer to the attached "Approximately correct" formula. 4-2.1 Strength of the gear
CE/T 3480..1997
The calculated tooth root stress should not be less than the allowable stress, that is: or the basic factor of the self-learning degree should be rounded to not less than the effective weak send some small safety factor Sr5.
In the above two formulas, the calculated root stress of the gear, N/mm*, see 4.2.2; the allowable root stress of the gear, N/m, see 4.2.3; the calculated safety factor of curvature, see 4.2.4: including the small safety factor of curvature strength, see 3. 1 and 4.4.2-2 The root stress of the gear is determined by the following:
a=pf.R,KKI
R:, 4.1.2 said
is the load distribution system for calculating the typical strength, see 6.3.4: K:
K——the recommended distribution system for calculating the bending strength, see 6.41-the basic value of the root stress, /m, for large and small gears should be determined separately, <5)
This standard provides the following two basic calculation methods for determining the root stress. For those with high requirements for single gear calculation, method one shall be used first: When there is disagreement on the calculation results, method one shall prevail.) This method is based on the load as the external point of the single pair of tooth meshing area for calculation. The internal root should be determined by the formula:
Wu, -
Nominal axial force on the internal indexing diagram N: YeYy
Working tooth width (at the tooth root surface), m. When the large and small gears are not selected, the tooth width of the narrow teeth is taken as the working tooth width of the gear. For the small double helical gear 62, if the gear has a single helical gear, the tooth end can be trimmed or the shape is missing, and the center should be taken as a smaller value than the actual value:
Y-tooth shadow model when the load acts on the external point of the single pair of teeth meshing area, minus 7.2.2: Y--How to use the stress list for the external point of the single pair of teeth meshing area, see 7.2.2; frequency flag system, then 7.2.4.
b) Method 2: The wood method is to calculate the tooth root stress with load acting on the tooth element and the tooth root, which is only applicable to gear transmission of E2. The basic value of tooth root stress is determined by the following formula:
Where: Ye
The tooth coefficient when the load acts on the tooth element, see 7.2.1 The stress coefficient when the load acts on the tooth element, see 2.2; .. . The vertical coefficient of the typical strength calculation is shown in 7.2.3. The meaning of F, m and Y is the same as that of formula (L2). 4.2.3 The allowable gear seat small
1 for ten 23 can also be calculated by formula (12, but in this case, the external points of the double-joint area should be used as load points, single safety,
GR/T3480-1997
people, the allowable stress of the pinion and the root stress of the tooth should be determined separately. When using the data obtained based on the strength of the test gear, the allowable gear stress can be calculated by the following formula:
FFSPEISY'H.YAnltYR.TY|| tt||Where Set
Calculate the bending limit stress of a gear, N/mm2; Test gear tooth deformation performance, N/m3; Test gear stress coefficient, such as the estimated value given by the wooden probe, and then Ys2.0
Calculate the life energy coefficient of the bending strength seat, see 8.2.2; The minimum safety factor of strength is shown in 3.1 and Appendix A1; Relative root angle inductance coefficient, 8.6;
Relative tooth surface modification coefficient: 8.; Dimensional coefficient of bending strength base calculation, see 8:5.2. 4.2.4 Calculation of overall system efficiency Sm
Se Ca CrY one
For the explanation of the formula, see 4.2.2 and 4.2.3, the safety factors of large and small gears should be calculated separately. Different users should consider the safety factors according to 3.1 and calculation respectively according to Section 5) and or (11). 5. The nominal tangential force F
The nominal tangential force or torque transmitted by the small output gear is determined by: The nominal tangential force is the nominal tangential force on the upper end surface of the gear and the tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force on the upper end surface of the gear. The nominal tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force ... 549
When the nominal work transmitted is measured in PS,
...Gear reverse rotation/min
When the gear is under variable load, the stress and strength of the gear can be calculated according to the safety system. When there is no accurate and more reliable method and data, the calculation can be made by referring to the time record B. 5 The effect of positive load and gear tooth stiffness
6. 1 Use coefficient K.
Use coefficient, considering the system affected by the external dynamic load of the pinion, the external brake belt should be used. It can also be used by actual operation or import. 16335196.KHK
In the formula: K
Use the multiplication factor, then 6. 1
dynamic cost coefficient + see 6-21
tensile strength This certificate can be calculated to provide me with the distribution coefficient see 6K
report the contact strength juice between the teeth of the batch load distribution system, see 6.4: small sores and fire wheel single pair of teeth combined cumulative number, see 7.1.5; the node calculation response, the basic value, use the following formula: adopt the reading effort:
17 This light order mutual ISUE326 may appear in the group, the small life is a quick certificate, Problem 6 of uneven force
Wu Zhong:
CE/T3480—1997
y=ZHZe2.2
Add the nominal tangent NW on the 4th index; 1. Make four senses m, refer to the smaller width of the small teeth in the wheel, the number of teeth is the number of nodes of the small and large teeth, 7.1.1:
Elastic coefficient/mm. State 7. 1.2;
world gear system, see 7.1.3;
domain load coefficient, see 7.1.4.
in the formula? "-\ external meshing transmission -\ pregnant gear transmission 4.1.3 allowable contact stress He
4. 7. 3. 1
general method
in the formula: ee
allowable contact limit force of gear, N/mm; test limit of contact deformation, N/mm, see 8.1; contact coefficient, %8.2.1; slip coefficient, 8.3.
speed load, see 8.5.1
height coefficient, see 8-3. 2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient · see 8.5.4.1.3-2 The method of loss
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 The system of 1 calculation of the whole system S
(6)
In the formula, the parameters are determined by the stock method and the chemical method respectively, and the S virtuality of the large and small wheels is calculated separately: the safety factor is not considered in the case of application. Li Zhou 3.1 and the calculation are respectively controlled by formula (7) and formula (3), 4.2 The gear root quality of the gear is unknown, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). In the case of failure to meet the requirements of the safety factor, the gear root quality is not known, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). When the load distribution is required for each pair of wheels, it is an ideal method to use the above method to determine the position of the load action and the corresponding maximum root stress. This standard takes the maximum deflection stress of the tooth as the nominal bending stress, and uses it as the calculated gear stress after correction with the corresponding system. Taking into account the different use conditions, requirements and sizes, this standard uses the test bending limit as the allowable internal stress. The technical standard tooth bending neck calculation formula is applicable to the gear with an internal friction edge of not less than 3. For gears that do not meet the above conditions, make a further analysis, and determine the tooth root stress rate through experiments or empirical data. If the above method cannot be used, refer to the "Approximately Correct" Appendix. 4-2.1 Strength of the gear
CE/T 3480..1997
The calculated tooth root stress should not be less than the allowable stress, that is: or the basic factor of the self-learning degree should be rounded to not less than the effective weak send some small safety factor Sr5.
In the above two formulas, the calculated root stress of the gear, N/mm*, see 4.2.2; the allowable root stress of the gear, N/m, see 4.2.3; the calculated safety factor of curvature, see 4.2.4: including the small safety factor of curvature strength, see 3. 1 and 4.4.2-2 The root stress of the gear is determined by the following:
a=pf.R,KKI
R:, 4.1.2 said
is the load distribution system for calculating the typical strength, see 6.3.4: K:
K——the recommended distribution system for calculating the bending strength, see 6.41-the basic value of the root stress, /m, for large and small gears should be determined separately, <5)
This standard provides the following two basic calculation methods for determining the root stress. For those with high requirements for single gear calculation, method one shall be used first: When there is disagreement on the calculation results, method one shall prevail.) This method is based on the load as the external point of the single pair of tooth meshing area for calculation. The internal root should be determined by the formula:
Wu, -
Nominal axial force on the internal indexing diagram N: YeYy
Working tooth width (at the tooth root surface), m. When the large and small gears are not selected, the tooth width of the narrow teeth is taken as the working tooth width of the gear. For the small double helical gear 62, if the gear has a single helical gear, the tooth end can be trimmed or the shape is missing, and the center should be taken as a smaller value than the actual value:
Y-tooth shadow model when the load acts on the external point of the single pair of teeth meshing area, minus 7.2.2: Y--How to use the stress list for the external point of the single pair of teeth meshing area, see 7.2.2; frequency flag system, then 7.2.4.
b) Method 2: The wood method is to calculate the tooth root stress with load acting on the tooth element and the tooth root, which is only applicable to gear transmission of E2. The basic value of tooth root stress is determined by the following formula:
Where: Ye
The tooth coefficient when the load acts on the tooth element, see 7.2.1 The stress coefficient when the load acts on the tooth element, see 2.2; .. . The vertical coefficient of the typical strength calculation is shown in 7.2.3. The meaning of F, m and Y is the same as that of formula (L2). 4.2.3 The allowable gear seat small
1 for ten 23 can also be calculated by formula (12, but in this case, the external points of the double-joint area should be used as load points, single safety,
GR/T3480-1997
people, the allowable stress of the pinion and the root stress of the tooth should be determined separately. When using the data obtained based on the strength of the test gear, the allowable gear stress can be calculated by the following formula:
FFSPEISY'H.YAnltYR.TY|| tt||Where Set
Calculate the bending limit stress of a gear, N/mm2; Test gear tooth deformation performance, N/m3; Test gear stress coefficient, such as the estimated value given by the wooden probe, and then Ys2.0
Calculate the life energy coefficient of the bending strength seat, see 8.2.2; The minimum safety factor of strength is shown in 3.1 and Appendix A1; Relative root angle inductance coefficient, 8.6;
Relative tooth surface modification coefficient: 8.; Dimensional coefficient of bending strength base calculation, see 8:5.2. 4.2.4 Calculation of overall system efficiency Sm
Se Ca CrY one
For the explanation of the formula, see 4.2.2 and 4.2.3, the safety factors of large and small gears should be calculated separately. Different users should consider the safety factors according to 3.1 and calculation respectively according to Section 5) and or (11). 5. The nominal tangential force F
The nominal tangential force or torque transmitted by the small output gear is determined by: The nominal tangential force is the nominal tangential force on the upper end surface of the gear and the tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force on the upper end surface of the gear. The nominal tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force ... 549
When the nominal work transmitted is measured in PS,
...Gear reverse rotation/min
When the gear is under variable load, the stress and strength of the gear can be calculated according to the safety system. When there is no accurate and more reliable method and data, the calculation can be made by referring to the time record B. 5 The effect of positive load and gear tooth stiffness
6. 1 Use coefficient K.
Use coefficient, considering the system affected by the external dynamic load of the pinion, the external brake belt should be used. It can also be used by actual operation or import. 16335196.KHK
In the formula: K
Use the multiplication factor, then 6. 1
dynamic cost coefficient + see 6-21
tensile strength This certificate can be calculated to provide me with the distribution coefficient see 6K
report the contact strength juice between the teeth of the batch load distribution system, see 6.4: small sores and fire wheel single pair of teeth combined cumulative number, see 7.1.5; the node calculation response, the basic value, use the following formula: adopt the reading effort:
17 This light order mutual ISUE326 may appear in the group, the small life is a quick certificate, Problem 6 of uneven force
Wu Zhong:
CE/T3480—1997
y=ZHZe2.2
Add the nominal tangent NW on the 4th index; 1. Make four senses m, refer to the smaller width of the small teeth in the wheel, the number of teeth is the number of nodes of the small and large teeth, 7.1.1:
Elastic coefficient/mm. State 7. 1.2;
world gear system, see 7.1.3;
domain load coefficient, see 7.1.4.
in the formula? "-\ external meshing transmission -\ pregnant gear transmission 4.1.3 allowable contact stress He
4. 7. 3. 1
general method
in the formula: ee
allowable contact limit force of gear, N/mm; test limit of contact deformation, N/mm, see 8.1; contact coefficient, %8.2.1; slip coefficient, 8.3.
speed load, see 8.5.1
height coefficient, see 8-3. 2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient · see 8.5.4.1.3-2 The method of loss
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 The system of 1 calculation of the whole system S
(6)
In the formula, the parameters are determined by the stock method and the chemical method respectively, and the S virtuality of the large and small wheels is calculated separately: the safety factor is not considered in the case of application. Li Zhou 3.1 and the calculation are respectively controlled by formula (7) and formula (3), 4.2 The gear root quality of the gear is unknown, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). In the case of failure to meet the requirements of the safety factor, the gear root quality is not known, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). When the load distribution is required for each pair of wheels, it is an ideal method to use the above method to determine the position of the load action and the corresponding maximum root stress. This standard takes the maximum deflection stress of the tooth as the nominal bending stress, and uses it as the calculated gear stress after correction with the corresponding system. Taking into account the different use conditions, requirements and sizes, this standard uses the test bending limit as the allowable internal stress. The technical standard tooth bending neck calculation formula is applicable to the gear with an internal friction edge of not less than 3. For gears that do not meet the above conditions, make a further analysis, and determine the tooth root stress rate through experiments or empirical data. If the above method cannot be used, refer to the "Approximately Correct" Appendix. 4-2.1 Strength of the gear
CE/T 3480..1997
The calculated tooth root stress should not be less than the allowable stress, that is: or the basic factor of the self-learning degree should be rounded to not less than the effective weak send some small safety factor Sr5.
In the above two formulas, the calculated root stress of the gear, N/mm*, see 4.2.2; the allowable root stress of the gear, N/m, see 4.2.3; the calculated safety factor of curvature, see 4.2.4: including the small safety factor of curvature strength, see 3. 1 and 4.4.2-2 The root stress of the gear is determined by the following:
a=pf.R,KKI
R:, 4.1.2 said
is the load distribution system for calculating the typical strength, see 6.3.4: K:
K——the recommended distribution system for calculating the bending strength, see 6.41-the basic value of the root stress, /m, for large and small gears should be determined separately, <5)
This standard provides the following two basic calculation methods for determining the root stress. For those with high requirements for single gear calculation, method one shall be used first: When there is disagreement on the calculation results, method one shall prevail.) This method is based on the load as the external point of the single pair of tooth meshing area for calculation. The internal root should be determined by the formula:
Wu, -
Nominal axial force on the internal indexing diagram N: YeYy
Working tooth width (at the tooth root surface), m. When the large and small gears are not selected, the tooth width of the narrow teeth is taken as the working tooth width of the gear. For the small double helical gear 62, if the gear has a single helical gear, the tooth end can be trimmed or the shape is missing, and the center should be taken as a smaller value than the actual value:
Y-tooth shadow model when the load acts on the external point of the single pair of teeth meshing area, minus 7.2.2: Y--How to use the stress list for the external point of the single pair of teeth meshing area, see 7.2.2; frequency flag system, then 7.2.4.
b) Method 2: The wood method is to calculate the tooth root stress with load acting on the tooth element and the tooth root, which is only applicable to gear transmission of E2. The basic value of tooth root stress is determined by the following formula:
Where: Ye
The tooth coefficient when the load acts on the tooth element, see 7.2.1 The stress coefficient when the load acts on the tooth element, see 2.2; .. . The vertical coefficient of the typical strength calculation is shown in 7.2.3. The meaning of F, m and Y is the same as that of formula (L2). 4.2.3 The allowable gear seat small
1 for ten 23 can also be calculated by formula (12, but in this case, the external points of the double-joint area should be used as load points, single safety,
GR/T3480-1997
people, the allowable stress of the pinion and the root stress of the tooth should be determined separately. When using the data obtained based on the strength of the test gear, the allowable gear stress can be calculated by the following formula:
FFSPEISY'H.YAnltYR.TY|| tt||Where Set
Calculate the bending limit stress of a gear, N/mm2; Test gear tooth deformation performance, N/m3; Test gear stress coefficient, such as the estimated value given by the wooden probe, and then Ys2.0
Calculate the life energy coefficient of the bending strength seat, see 8.2.2; The minimum safety factor of strength is shown in 3.1 and Appendix A1; Relative root angle inductance coefficient, 8.6;
Relative tooth surface modification coefficient: 8.; Dimensional coefficient of bending strength base calculation, see 8:5.2. 4.2.4 Calculation of overall system efficiency Sm
Se Ca CrY one
For the explanation of the formula, see 4.2.2 and 4.2.3, the safety factors of large and small gears should be calculated separately. Different users should consider the safety factors according to 3.1 and calculation respectively according to Section 5) and or (11). 5. The nominal tangential force F
The nominal tangential force or torque transmitted by the small output gear is determined by: The nominal tangential force is the nominal tangential force on the upper end surface of the gear and the tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force on the upper end surface of the gear. The nominal tangential force is the nominal torque transmitted by the gear. The nominal tangential force is the nominal tangential force ... 549
When the nominal work transmitted is measured in PS,
...Gear reverse rotation/min
When the gear is under variable load, the stress and strength of the gear can be calculated according to the safety system. When there is no accurate and more reliable method and data, the calculation can be made by referring to the time record B. 5 The effect of positive load and gear tooth stiffness
6. 1 Use coefficient K.
Use coefficient, considering the system affected by the external dynamic load of the pinion, the external brake belt should be used. It can also be used by actual operation or import. 16335196.The workpiece is m, which refers to the smaller width of the small teeth in the gear. The gear ratio is the number of teeth of the small gear and the large gear respectively. 7.1.1: Elastic coefficient/mm. 7.1.2; For gear ratio, see 7.1.3; For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. For gear ratio, see 7.1.3. For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. For gear ratio, see 7.1.4. 1
General method
Wu Zhong: ee
Let the gear joint limit force, N/mm test limit of the joint deformation/mm, see 8.1 contact degree calculation coefficient, %8.2.1; slip coefficient, 8.3.
Speed load, see 8.5.1
H -- -- roughness coefficient, see 8-3.2 : The working coefficient, total &.41
Contact through the calculation of the size coefficient, see 8.5.4.1.3-2 The method of consumption
can be calculated by formula (7), the coefficient, 2,, Z is determined by the simplified formula. 4.1.4 The system of 1 calculation of the whole system S
(6)
In the formula, each parameter is determined by the method and the chemical method respectively, and the S of the large and small wheels are calculated separately: the safety factor is not considered in the case of use. Li Zhou 3.1 and the calculation are respectively controlled by formula (7) and formula (3), 4.2 The gear root quality of the gear is unknown, in principle, it can be determined by any available method (such as finite element method, engineering method, added load method) or wide measurement (optical elastic coverage, variable measurement). After the load distribution of each pair of wheels on the platform is determined, the above method is used to determine the maximum The ideal method is to calculate the root stress or load position and its corresponding maximum root stress. This standard does not use the maximum deflection stress of the tooth under load as the nominal bending stress, and uses it as the calculated gear stress after correction with the corresponding system. Considering the different use conditions, requirements and sizes, this standard uses the test deformation limit after adjustment as the allowable internal stress. The technical standard gear tooth bending neck calculation formula is applicable to the gear with an internal fric
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