Bevel gear bending strength correction calculation method

Abstract

The invention discloses a helical gear bending strength correction calculation method, which belongs to the technical field of gear strength, and takes a helical gear as a research object, an advanced precise helical gear three-dimensional bending finite element calculation model is introduced, and a helical gear end face correction coefficient and a helical gear longitudinal correction coefficient are added in the calculation process. Compared with a standard calculation method, the accurate bending strength safety coefficient of the helical gear can be quickly, simply and conveniently obtained. The method is particularly suitable for calculation of bending strength and fatigue life of high-speed and heavy-duty helical gears of wind power, rail transit, engineering machinery and the like, and provides powerful support for gear transmission design and manufacturing in related fields.

Description

Technical Field

[0001] The invention relates to the technical field of gear strength, and in particular to a method for calculating the bending strength correction of a helical gear. Background Art

[0002] Gears are the most widely used transmission parts in mechanical transmission, and are often used to transmit power, change speed and direction of rotation. As a special type of gear, the tooth surface of the helical gear is at a certain angle to the axis. This design makes the helical gear have better stability and load-bearing capacity during the transmission process, so it has been widely used in various mechanical equipment.

[0003] However, the design, calculation and manufacturing of helical gears also face many challenges. Among them, the calculation of the bending strength and life of helical gears is a key issue. Traditional calculation methods, such as ISO6336.3 or GB3480.3 standards, usually treat the helical gear as an equivalent hypothetical spur gear for calculation. Although this calculation method simplifies the calculation process, it cannot fully adapt to the changes in the meshing line caused by the helix angle of the helical gear, so it is difficult to accurately reflect the stress distribution under actual working conditions. Especially under high-speed and heavy-load conditions, traditional calculation methods often cannot accurately predict the bending strength and fatigue life of helical gears. This results in the designed gears being either too large in size and weight, losing market competitiveness; or prone to failure and damage, and unable to meet actual application needs. Therefore, a more accurate, simple and fast calculation method is needed for the calculation of the bending strength of helical gears.

[0004] The existing patent CN105138734B discloses an improved helical gear noise optimization design method, which belongs to the field of transmission gear optimization design. The method specifically includes: step one, establishing a calculation model of the meshing dynamic stiffness and dynamic transmission error during the meshing process of the helical gear, which is used to calculate the fluctuation value of the dynamic transmission error of the helical gear meshing; step two, based on the calculation model of step one and the requirements of gear design regulations, establishing an optimization design model of the main parameters of the helical gear of the transmission with the goal of reducing noise and volume while ensuring strength and reliability during use, and optimizing the design of the helical gear of the transmission; step three, testing the optimal parameters obtained by the optimization design to ensure the correctness of the optimization results. This method focuses on reducing the transmission error of gear meshing, thereby reducing vibration and noise during meshing, improving service life and driving comfort, and does not solve the problem that traditional calculation methods in the prior art often cannot accurately predict the bending strength and fatigue life of helical gears.

[0005] The existing patent CN 107327559 B discloses a helical gear with arc parabola multi-point contact. The basic tooth profile of the helical gear adopts a stepped tooth shape, including a working tooth profile and a non-working tooth profile. The working tooth profile includes a convex arc tooth profile curve segment and a concave parabola tooth profile curve segment. The non-working tooth profile includes a stepped arc tooth profile curve segment and a tooth root arc tooth profile curve segment. The convex arc tooth profile curve segment is smoothly connected to the stepped arc tooth profile curve segment, the stepped arc tooth profile curve segment is connected to the concave parabola tooth profile curve segment, and the concave parabola tooth profile curve segment is connected to the tooth root arc tooth profile curve segment. The helical gear is in concave and convex point contact when meshing. When the longitudinal overlap is greater than 1, it has four or more contact points at the same time. This method focuses on reducing the average load of the contact point, so that the gear has high contact strength, large load-bearing capacity, high transmission efficiency, and good lubrication effect. It does not solve the problem that the traditional calculation method in the prior art often cannot accurately predict the bending strength and fatigue life of the helical gear.

[0006] In summary, the above two existing patents do not solve the problem that the traditional calculation methods in the prior art are often unable to accurately predict the bending strength and fatigue life of the helical gears. Summary of the invention

[0007] Based on the above technical problems, the present invention proposes a corrected calculation method for the bending strength of helical gears to solve the problem that traditional calculation methods in the prior art often cannot accurately predict the bending strength and fatigue life of helical gears.

[0008] In order to achieve the above purpose, the present invention proposes a helical gear bending strength correction calculation method, which introduces an accurate helical gear three-dimensional bending finite element calculation model, adds the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient in the calculation process, and more accurately predicts the bending strength and fatigue life of the helical gear under actual working conditions. The specific technical solution is as follows:

[0009] A method for calculating the bending strength correction of a helical gear, the method comprising:

[0010] Calculation of the required tooth root bending stress σ of the helical gear FG ;

[0011] Introduce the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient to calculate the helical gear bending stress σ F ;

[0012] According to the required tooth root bending stress σ of the helical gear FG and the bending stress σ of the helical gear F Calculation of the safety factor S of the bending strength of helical gears F .

[0013] Furthermore, the calculation method of the tooth root bending stress required for the helical gear is:

[0014] σFG =σ Flim Y ST Y NT Y δrelT Y RrelT Y X

[0015] Among them, σ Flim is the bending fatigue limit of the test gear, Y ST is the stress correction factor, Y NT is the tooth root stress life factor, Y δrelT is the relative tooth root fillet sensitivity coefficient, Y RrelT is the relative tooth root surface condition coefficient, Y X is the size factor.

[0016] Furthermore, the helical gear end face correction coefficient is

[0017]

[0018] Among them, ε α is the gear end face overlap, A, B, C are correction coefficients.

[0019] Furthermore, the longitudinal correction coefficient of the helical gear is

[0020]

[0021] Among them, ε β is the longitudinal overlap of the gears, and D, E, and F are correction coefficients.

[0022] Furthermore, when the ISO6336-2006 standard is used for calculation, the helical gear end face correction coefficient P α The values ​​of correction coefficients A, B, and C in are as follows:

[0023] When 1.2≤ε α When <2, A=-0.024±0.005, B=0.06±0.005, C=0.974±0.005;

[0024] The helical gear longitudinal correction factor P β The values ​​of correction coefficients D, E, and F in are as follows:

[0025] When 0<ε β When ≤1, D = 0.263 ± 0.005, E = -0.398 ± 0.005, C = 1 ± 0.005;

[0026] When 1<ε β When ≤2, D = -0.103 ± 0.005, E = 0.387 ± 0.005, C = 0.579 ± 0.005;

[0027] When 2<ε β When ≤3, D=0.189±0.005, E=-0.74±0.005, C=1.656±0.005.

[0028] Furthermore, when the ISO 6336.3-2019 standard or the GB3480.3-2021 standard is used for calculation, the helical gear end face correction coefficient P α The values ​​of correction coefficients A, B, and C in are as follows:

[0029] When 1.2≤ε α When <2, A=-0.161±0.005, B=0.721±0.005, C=0.3±0.005;

[0030] The helical gear longitudinal correction factor P β The values ​​of correction coefficients D, E, and F in are as follows:

[0031] When 0<ε β When ≤1, D = 0.312 ± 0.005, E = -0.234 ± 0.005, C = 1 ± 0.005;

[0032] When 1<ε β When ≤2, D = -0.133 ± 0.005, E = 0.421 ± 0.005, C = 0.801 ± 0.005;

[0033] When 2<ε β When ≤3, D=-0.032±0.005, E=0.253±0.005, C=0.699±0.005.

[0034] Furthermore, the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient are introduced into the basic value for calculating the gear bending stress. The basic value for calculating the gear bending stress is calculated as follows:

[0035]

[0036] Among them, F t is the nominal end face tangential load on the pitch circle, b is the tooth width, m n is the normal module of the gear, Y F is the tooth profile coefficient, Y S is the stress correction factor, Y β is the helix angle coefficient, Y B is the rim thickness coefficient, Y DT is the tooth height coefficient, P α is the helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

[0037] Further, the basic value σ is calculated based on the gear bending stress introduced by the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient. F0 Calculation of bending stress σ of helical gear F , the bending stress of the helical gear is calculated as follows:

[0038] σ F =σ F0 K A K γ K V K Fβ K Fα

[0039] Among them, σ F0 is the basic value for calculating the gear bending stress, K A is the service factor, K γ is the load-balancing factor, K V is the dynamic load coefficient, K Fβ is the helix load distribution factor for bending strength calculation, K Fα Load distribution factor between teeth calculated for bending strength.

[0040] Furthermore, the calculation method of the bending strength safety factor of the helical gear is:

[0041]

[0042] Among them, σ F is the bending stress of the helical gear, σ FG It is the required root bending stress of helical gears.

[0043] The present invention also provides a computer-readable storage medium, characterized in that the computer-readable storage medium includes a stored computer program, wherein when the computer program is executed by a processor, the device where the storage medium is located is controlled to execute the steps of the above-mentioned helical gear bending strength correction calculation method.

[0044] The present invention also provides another method for calculating the bending strength correction of helical gears. The method introduces the above-mentioned helical gear end face correction coefficient and helical gear longitudinal correction coefficient. The calculation method of the helical gear bending strength safety factor in the method is as follows:

[0045] S F =P α P β S' F

[0046] Among them, S' F is the safety factor calculated using international or national standards, P α is the helical gear end face correction factor, P βis the longitudinal correction factor of the helical gear.

[0047] Furthermore, the method uses software Kisssoft or Romax compiled based on international or national standards to calculate the safety factor S' F .

[0048] Based on the above technical solution, the present invention proposes a method for calculating the bending strength correction of helical gears, which has at least the following beneficial effects:

[0049] 1. The present invention proposes a method for calculating the bending strength correction of helical gears. Compared with the standard calculation method, the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient are added during the calculation of the gear bending strength. This method can quickly and easily obtain an accurate bending strength safety factor of the helical gear.

[0050] 2. The present invention provides a method for calculating the bending strength correction of helical gears, which can reduce design redundancy based on the accurate gear bending safety factor obtained by calculation, thereby reducing the gear size and achieving the purpose of reducing manufacturing costs.

[0051] 3. The present invention provides a method for calculating the bending strength correction of helical gears. By accurately calculating the gear bending safety factor, the gear module can be appropriately reduced and the number of teeth can be increased under the condition of meeting similar speed ratios, thereby increasing the gear overlap, improving the gear contact strength safety factor and reducing the vibration and noise of the system.

[0052] 4. The present invention provides a method for calculating the bending strength correction of helical gears, which can be used to calculate the bending safety factor of helical gears and also can be used to calculate the bending safety life of helical gears. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] The accompanying drawings constituting a part of the present invention are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the accompanying drawings:

[0054] Figure 1 A schematic diagram of a flow chart of a method for calculating the bending strength correction of a helical gear provided by the present invention;

[0055] Figure 2 is the basic value of bending stress calculated by ISO6336-2006, ISO6336-2019, finite element method and the method of the present invention under different longitudinal overlaps of a certain modulus gear in an embodiment of the present invention;

[0056] Figure 3 It is the basic value of bending stress calculated by ISO6336-2006, ISO6336-2019, finite element method and the method of the present invention under different end face overlap of a certain module gear in an embodiment of the present invention. DETAILED DESCRIPTION

[0057] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0058] The present invention is further described in detail below in conjunction with specific embodiments. These embodiments should not be construed as limiting the scope of protection claimed by the present invention.

[0059] Example 1

[0060] In order to meet the high requirements for the performance of helical gears in high-speed and heavy-load fields such as wind power, rail transit and engineering machinery, this embodiment proposes a corrected calculation method for the bending strength of helical gears. This method aims to provide a more scientific and practical means of calculating the bending strength of helical gears. By introducing an advanced and precise three-dimensional bending finite element calculation model for helical gears, the bending strength and fatigue life of helical gears under actual working conditions can be more accurately predicted, providing strong support for the gear transmission design and manufacturing in related fields.

[0061] To achieve the above purpose, see Figure 1 As shown, the present invention proposes a method for calculating the bending strength correction of helical gears, which specifically includes:

[0062] Calculation of the required root bending stress σ for helical gears FG ;

[0063] Specifically, the tooth root bending stress refers to the bending stress of the tooth root when the lateral force of the gear acts on the gear. Because they are bent by external forces, they are also called external force bending stress. The axial and tangential forces between the transmission gears cause the bending of the tooth root. The tooth root bending stress is affected by such axial and tangential forces, mainly involving the bending stress level of the tooth root, the strength of commonly used rubber materials, the static and dynamic properties of the relay shaft, the precision requirements of gear installation, etc. Therefore, the calculation method of the tooth root bending stress is as follows:

[0064] σ FG =σ Flim Y ST Y NT Y δrelT Y RrelT Y X

[0065] Among them, σ Flim is the bending fatigue limit of the test gear, Y ST is the stress correction factor, Y NT is the tooth root stress life factor, Y δrelT is the relative tooth root fillet sensitivity coefficient, Y RrelTis the relative tooth root surface condition coefficient, Y X is the size factor.

[0066] The helical gear end face correction coefficient and the helical gear longitudinal correction coefficient are introduced to calculate the helical gear bending stress;

[0067] Specifically, the gear will be subjected to bending stress during operation, so it is necessary to calculate the bending stress. Bending stress refers to the stress caused by the bending deformation on the gear tooth surface when the gear is subjected to external load. The calculation method of the gear bending stress is as follows:

[0068] σ F =σ F0 K A K γ K V K Fβ K Fα

[0069] Among them, σ F0 is the basic value for calculating the gear bending stress, K A is the service factor, K γ is the load-balancing factor, K V is the dynamic load coefficient, K Fβ is the helix load distribution factor for bending strength calculation, K Fα inter-tooth load distribution factor calculated for bending strength;

[0070] Basic value σ in the calculation of bending stress in gears F0 The helical gear end face correction factor P is introduced α and the helical gear longitudinal correction factor P β , then the basic value of gear bending stress calculation σ F0 for

[0071]

[0072] Among them, F t is the nominal end face tangential load on the pitch circle, b is the tooth width, m n is the normal module of the gear, Y F is the tooth profile coefficient, Y S is the stress correction factor, Y β is the helix angle coefficient, Y B is the rim thickness coefficient, Y DT is the tooth height coefficient, Pα 为 Helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

[0073] Helical gear end face correction factor P α and the helical gear longitudinal correction factor P β They are

[0074]

[0075] Among them, ε α is the gear end face overlap, ε β is the longitudinal overlap of the gears.

[0076] When calculated using ISO6336-2006 standard,

[0077] 1.2≤ε α When <2, A=-0.024, B=0.06, C=0.974;

[0078] 0<ε β When ≤1, D=0.263, E=-0.398, C=1;

[0079] 1<ε β When ≤2, D = -0.103, E = 0.387, C = 0.579;

[0080] 2<ε β When ≤3, D = 0.189, E = -0.74, C = 1.656;

[0081] When calculated using ISO 6336.3-2019 or GB3480.3-2021 standards,

[0082] 1.2≤ε α When <2, A=-0.161, B=0.721, C=0.3;

[0083] 0<ε β When ≤1, D=0.312, E=-0.234, C=1;

[0084] 1<ε β When ≤2, D = -0.133, E = 0.421, C = 0.801;

[0085] 2<ε β When ≤3, D=-0.032, E=0.253, C=0.699.

[0086] See also Figure 2 As shown, the basic values ​​of bending stress calculated by ISO6336-2006, ISO6336-2019, finite element method and the method of this embodiment under different longitudinal overlap of a certain module gear are shown; see Figure 3As shown, the basic values ​​of bending stress calculated by ISO6336-2006, ISO6336-2019, finite element method and the method of this embodiment under different end face overlaps of a certain module gear; it can be seen from the two figures that the basic values ​​of bending stress calculated by the method of this embodiment are very close to the basic values ​​of bending force by the finite element method, while the basic values ​​of bending stress calculated using the ISO6336-2006 standard or the ISO6336-2019 standard are quite different.

[0087] Calculate the bending strength safety factor of the helical gear based on the bending stress of the helical gear and the required tooth root bending stress;

[0088] Specifically, the bending strength safety factor of the helical gear is calculated based on the bending stress of the helical gear and the required tooth root bending stress. The bending strength safety factor of the helical gear is

[0089]

[0090] Among them, σ F is the calculated value of the bending stress of the helical gear, σ FG It is the value required for calculating the tooth root bending stress.

[0091] In this embodiment, in the above calculation formula: the bending fatigue limit coefficient σ of the test gear Flim , stress correction factor Y ST , tooth root stress life factor Y NT , relative tooth root fillet sensitivity coefficient Y δrelT , relative tooth root surface condition coefficient Y RrelT , size factor Y X , use factor K A , load-averaging factor K γ , dynamic load coefficient K V , helix load distribution coefficient K for bending strength calculation Fβ , inter-tooth load distribution coefficient K for bending strength calculation Fα , nominal end face tangential load F on the pitch circle t , tooth width b, normal module m of the gear n , tooth profile coefficient Y F , stress correction factor Y S , helix angle coefficient Y β , rim thickness coefficient Y B , tooth height coefficient Y DT Both can be calculated or selected according to ISO6336 standard or GB / T3480 standard.

[0092] The present embodiment provides a method for calculating the bending strength correction of helical gears. The bending strength safety factor of the helical gears can be calculated according to the above formula, or it can be calculated using Kisssoft, Romax or other software compiled based on standards. The gear bending strength safety factor is calculated as follows:

[0093] S F =P α P β S' F

[0094] Among them, S' F is the safety factor calculated by Kisssoft, Romax or other software based on the standard, P α is the helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

[0095] Example 2

[0096] This embodiment proposes a method for calculating the bending strength correction of helical gears, and takes a carburized and quenched helical gear pair as an example to specifically illustrate the calculation method.

[0097] In this embodiment, the relevant parameters of the helical gear pair are the module m n =18.7, pressure angle α n =22.5°, helix angle β=7.5°, number of teeth on small gear Z1=31, number of teeth on large gear Z2=49, tooth width b=440, displacement coefficient x1=0, center distance a=756, tooth top height coefficient h a =1.08, top clearance coefficient c * =0.32, end face overlap ε α =1.65, longitudinal overlap ε β =1.04, input torque is 500KNm, speed is 200rpm, and life requirement is 175000h.

[0098] According to ISO6336-2006 standard, we can get σ Flim =460Mpa, Y ST =2,Y δrelT =1,Y X =1, K A =1, K γ =1, K v =1.05, K Fβ =1.033, K Fα =1, F t =1710280N,Y F =1.37, Y S =1.977, Y β =0.933, Y B=1,Y DT =1,Y ST =2,Y NT =0.916, Y δrelT =0.996, Y RrelT =1.002, Y X =0.863.

[0099] The bending strength correction calculation method for helical gears provided in this embodiment uses the above data to calculate the bending strength safety factor of the helical gears.

[0100] Calculation of the required root bending stress σ for helical gears FG ;

[0101] The specific calculation results are:

[0102]

[0103] Calculate bending stress in helical gears;

[0104] First calculate the helical gear end face correction coefficient P α and the helical gear longitudinal correction factor P β The calculation results are

[0105]

[0106] Then according to the helical gear end face correction coefficient P α and the helical gear longitudinal correction factor P β Calculate the basic value of bending stress, the calculation results are as follows:

[0107]

[0108] Finally, the bending stress of the helical gear is calculated. The calculation results are as follows:

[0109] σ FG =σ Flim Y ST Y NT Y δrelT Y RrelT Y X =500×2×0.916×0.996×1.002×0.863=788.92Mpa.

[0110] Calculate the bending strength safety factor of the helical gear based on the bending stress of the helical gear and the required tooth root bending stress;

[0111] The specific calculation results are:

[0112] For this helical gear, if the ISO6336-2006 standard is used, the bending strength safety factor of the gear is calculated to be 1.39, which is too conservative compared with the calculation result of the method of the present invention. If the ISO6336-2019 standard is used, the bending strength safety factor of the gear is calculated to be 1.79, which is too radical compared with the calculation result of the method of the present invention.

[0113] Example 3

[0114] This embodiment also provides a method for calculating the bending strength correction of helical gears. This method introduces the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient in Embodiment 1. The calculation method of the helical gear bending strength safety factor is:

[0115] S F =P α P β S' F

[0116] Among them, S' F is the safety factor calculated using international or national standards, P α is the helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

[0117] Optionally, the method can use Kisssoft, Romax or other software compiled based on international or national standards to calculate the safety factor S' F .

[0118] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

[0119] It should be noted that, in this article, relational terms such as first and second, etc. are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the existence of other identical elements in the process, method, article or device including the elements.

[0120] The logic and / or steps represented in the flowchart or otherwise described herein, for example, can be considered as an ordered list of executable instructions for implementing logical functions, which can be embodied in any computer-readable medium for use by an instruction execution system, apparatus or device (such as a computer-based system, a system including a processor or other system that can fetch instructions from an instruction execution system, apparatus or device and execute instructions), or used in combination with these instruction execution systems, apparatuses or devices.

[0121] It should be noted that, in the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, unless they are contradictory.

Claims

1. A method for calculating the bending strength correction of helical gears, characterized in that: The method comprises: Calculation of the required tooth root bending stress σ of helical gears FG ; Introduce the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient to calculate the helical gear bending stress σ F ; According to the required tooth root bending stress σ of the helical gear FG and the bending stress σ of the helical gear F Calculation of the safety factor S of the bending strength of helical gears F .

2. The method for calculating the bending strength correction of helical gears according to claim 1, characterized in that: The calculation method for the required tooth root bending stress of the helical gear is: σ FG =σ Flim AND ST AND NT AND δrelT AND RrelT AND X Among them, σ Flim is the bending fatigue limit of the test gear, Y ST is the stress correction factor, Y NT is the tooth root stress life factor, Y δrelT is the relative tooth root fillet sensitivity coefficient, Y RrelT is the relative tooth root surface condition coefficient, Y X is the size factor.

3. The method for calculating the bending strength correction of helical gears according to claim 1, characterized in that: The helical gear end face correction coefficient is: Among them, ε α is the gear end face overlap, A, B, C are correction coefficients.

4. The method for calculating the bending strength correction of helical gears according to claim 3, characterized in that: The longitudinal correction factor of the helical gear is Among them, ε β is the longitudinal overlap of the gears, and D, E, and F are correction coefficients.

5. The method for calculating the bending strength correction of helical gears according to claim 4, characterized in that: When calculated using the ISO6336-2006 standard, the helical gear end face correction factor P α The values ​​of correction coefficients A, B, and C in are as follows: When 1.2≤ε α When <2, A=-0.024±0.005, B=0.06±0.005, C=0.974±0.005; The helical gear longitudinal correction factor P β The values ​​of correction coefficients D, E, and F in are as follows: When 0<ε β When ≤1, D = 0.263 ± 0.005, E = -0.398 ± 0.005, C = 1 ± 0.005; When 1<ε β When ≤2, D = -0.103 ± 0.005, E = 0.387 ± 0.005, C = 0.579 ± 0.005; When 2<ε β When ≤3, D=0.189±0.005, E=-0.74±0.005, C=1.656±0.

005.

6. The method for calculating the bending strength correction of helical gears according to claim 4, characterized in that: When calculated using ISO 6336.3-2019 or GB3480.3-2021, the helical gear end face correction factor p α The values ​​of correction coefficients A, B, and C in are as follows: When 1.2≤ε α When <2, A=-0.161±0.005, B=0.721±0.005, C=0.3±0.005; The helical gear longitudinal correction factor P β The values ​​of correction coefficients D, E, and F in are as follows: When 0<ε β When ≤1, D = 0.312 ± 0.005, E = -0.234 ± 0.005, C = 1 ± 0.005; When 1<ε β When ≤2, D = -0.133 ± 0.005, E = 0.421 ± 0.005, C = 0.801 ± 0.005; When 2<ε β When ≤3, D=-0.032±0.005, E=0.253±0.005, C=0.699±0.

005.

7. The method for calculating the bending strength correction of helical gears according to claim 4, characterized in that: The helical gear end face correction coefficient and the helical gear longitudinal correction coefficient are introduced into the basic value for calculating the gear bending stress. The basic value for calculating the gear bending stress is calculated as follows: Among them, F t is the nominal end face tangential load on the pitch circle, b is the tooth width, m n is the normal module of the gear, Y F is the tooth profile coefficient, Y S is the stress correction factor, Y β is the helix angle coefficient, Y B is the rim thickness coefficient, Y DT is the tooth height coefficient, P α is the helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

8. The method for calculating the bending strength correction of helical gears according to claim 7, characterized in that: The basic value σ is calculated by introducing the helical gear end face correction coefficient and the helical gear longitudinal correction coefficient into the gear bending stress. F0 Calculation of bending stress σ of helical gear F , the bending stress of the helical gear is calculated as follows: s F =s F0 K A K γ K V K Fβ K Fα Among them, σ F0 is the basic value for calculating the gear bending stress, K A is the service factor, K γ is the load-balancing factor, K V is the dynamic load coefficient, K Fβ is the helix load distribution factor for bending strength calculation, K Fα Load distribution factor between teeth calculated for bending strength.

9. The method for calculating the bending strength correction of helical gears according to claim 2 or 8, characterized in that: The calculation method of the bending strength safety factor of the helical gear is: Among them, σ F is the bending stress of the helical gear, σ FG It is the required root bending stress of the helical gear.

10. A computer-readable storage medium, characterized in that: The computer-readable storage medium includes a stored computer program, wherein when the computer program is executed by a processor, the device where the storage medium is located is controlled to execute the steps of the helical gear bending strength correction calculation method according to any one of claims 1 to 9.

11. A method for calculating the bending strength correction of helical gears, characterized in that: The method introduces the helical gear end face correction factor and the helical gear longitudinal correction factor as claimed in claim 4. The helical gear bending strength safety factor is calculated as follows: S F =P α P β S’ F Among them, S' F is the safety factor calculated using international or national standards, P α is the helical gear end face correction factor, P β is the longitudinal correction factor of the helical gear.

12. The method for calculating the bending strength correction of helical gears according to claim 11, characterized in that: The method uses software Kisssoft or Romax compiled based on international or national standards to calculate the safety factor S' F .

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