CN110069867A - Comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state - Google Patents
Comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state Download PDFInfo
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Abstract
The invention discloses fatigue safety coefficient calculation methods comprehensive under a kind of drive axle transmission system components multi-state, comprising the following steps: establishes the Static Analysis Model of Micro-machined of drive axle transmission system, calculates stress of the components under a certain single operating condition；Calculate the synthetic finite service life fatigue safety coefficient in multiple operating condition lower axles；Calculate synthesis fatigue safety coefficient of each bearing in transmission system under multiple operating conditions；Calculate synthesis fatigue safety coefficient of each gear in transmission system under multiple operating conditions.The calculation method of synthesis fatigue safety coefficient of the drive axle transmission system part disclosed by the invention under multi-state integrated condition can ensure that the fatigue safety performance of drive axle transmission system all reaches design requirement without influencing its service life, the stabilization enhanced product performance, and then improve the qualification rate of product.
Description
Technical field
The present invention relates to automobile technical fields, and in particular to synthesis is tired under a kind of drive axle transmission system components multi-state
Labor safety coefficient calculation method.
Background technique
The important spare parts such as axis, bearing, gear are contained in drive axle transmission system.Carrying out drive axle transmission system
When design, present design method is the following steps are included: firstly, establish the Static Analysis Model of Micro-machined of transmission system；Then, to it
Typical condition carries out the load that force analysis obtains each components；Finally, according to Its Relevant Technology Standards to axis, bearing, gear etc.
Components carry out fatigue safety check, the fatigue safety coefficient of the components under single operating condition are calculated, if safety coefficient is unsatisfactory for
It is required that then modifying to element size model, until meeting the requirements.
Present drive axle Design of Transmission System method only calculates single single when carrying out fatigue safety coefficient calculating
Safety coefficient under operating condition, although the check by single operating condition, product may meet the requirement of service life, so
And it often is faced with various working in actual use, existing drive axle Design of Transmission System method is not according to all works
Condition is to the comprehensive fatigue safety coefficient of the combined influence calculation and check of components.Under the influence of multi-state, the safety coefficient of product
Usually can also be lower than either simplex condition check result, therefore only use the check of either simplex condition and will lead to and meet safe system in independent check
Several requirements, but safety coefficient can decline under multiple operating conditions, be allowed to be unsatisfactory for requirement, this will lead to drive axle biography
The fatigue safety performance of dynamic system sometimes up to influences its service life less than design requirement, and shows properties of product shakiness
Fixed, qualification rate is low.
Summary of the invention
The purpose of the present invention is to provide fatigue safety coefficients comprehensive under a kind of drive axle transmission system components multi-state
Calculation method, the fatigue safety performance to solve drive axle transmission system sometimes up to influence it less than design requirement and use the longevity
Life, and show the problem that properties of product are unstable, qualification rate is low.
Comprehensive fatigue safety coefficient calculation method under a kind of drive axle transmission system components multi-state provided by the invention,
The components include axis, bearing and gear, if the operating condition number of the drive axle transmission system components is NL(NLFor greater than 1
Natural number), the calculation method the following steps are included:
Step A: establishing the Static Analysis Model of Micro-machined of drive axle transmission system, calculates components in a certain single operating condition Ni(i
It is 1 to NLNatural number) under stress；
Step B: it calculates in NLThe synthetic finite service life fatigue safety coefficient of a operating condition lower axle；
Step C: each bearing in transmission system is calculated in NLSynthesis fatigue safety coefficient under a operating condition；
Step D: each gear in transmission system is calculated in NLSynthesis fatigue safety coefficient under a operating condition.
Further, the step B the following steps are included:
Step B1: single operating condition N is calculatediThe damage ratio of lower axle:
According to components in a certain single operating condition NiUnder stress and reference standard " selection of closed gear transmission device and
Design " in infinite life fatigue safety coefficient calculation formula calculate single operating condition NiThe infinite life fatigue safety system of lower axle
Number；
Wherein, FsfSafety coefficient is represented,For meter Sai Si alternate stress,For meter Sai Si mean stress, SfIt is tired strong
Degree, SyFor tensile yield strength.
Step B2: calculating the equivalent cycle number of the total damage ratio and all operating conditions of axis under damage ratio maximum duty,
Wherein NLTotal damage ratio D of a operating conditionACalculation formula are as follows:
Calculate corresponding operating condition maximum damage ratio D when damage ratio maximum in all operating conditionsE, its calculation formula is
DE=max { D1, D2... Di... DNL}
In formula, DiFor the damage ratio of single operating condition.
If maximum damage ratio DECorresponding cycle-index is NE, then all operating conditions are in maximum damage ratio DEUnder total damage ratio
Equivalent cycle times NACalculation formula are as follows:
Step B3: according to the infinite life fatigue safety coefficient calculation formula again to equivalent cycle-index NAIn maximum
Damage ratio DEAxis under operating condition is checked, and calculates the synthesis fatigue safety coefficient of the axis under multi-state.
Further, in the step B1, if infinite life fatigue safety coefficient is greater than 1, illustrate axis in the operating condition
Under damage ratio be 0；If infinite life fatigue safety coefficient is less than 1, damage ratio DiFor
Wherein, NiFor cycle-index of the axis at operating condition i, the cycle-index N0iCalculation formula it is as follows:
Wherein, coefficient c and m is related with the Tensile strength limit, σaAnd σmRespectively meter Sai Si alternate stress peace should all
Power, SyFor tensile yield strength.
Further, for the bearing in the drive axle transmission system, the step C the following steps are included:
Step C1: according to the basic volume of the rolling bearing of international standard " rolling bearing: dynamic load rating and rated life time "
The calculation formula for determining the service life calculates the damage ratio of each operating condition lower bearing；Wherein basic rating life L10Calculation formula be
Wherein, CdFor the basic dynamic load rating of bearing, k is bearing index, PrFor dynamic equivalent radial load；
If the number of run of the i-th operating condition bearing is Li, then the fatigue safety coefficient S under the i-th operating condition is utilizediI-th can be calculated
The damage ratio D of operating condition lower bearingiFor
Step C2: the total damage ratio of bearing and comprehensive fatigue safety coefficient are calculated
The calculation formula of total damage ratio D of all operating conditions of bearing are as follows:
The calculation formula of the comprehensive fatigue safety coefficient S of multi-state are as follows:
Further, the step D the following steps are included:
Step D1: the damage ratio D of each operating condition lower gear fatigue is calculatedi, wherein the i-th operating condition lower gear flexural fatigue is damaged
Rate DiCalculation formula are as follows:
In formula, NiFor actual motion number, NHRiFor specified number of run；
Step D2: the total damage ratio of gear and all ahead condition A and all anti-turner condition B are calculated under maximum damage ratio
Equivalent cycle number；
Step D3: equivalent cycle number is used respectivelyWithIn maximum damage ratio DEIt is checked under load under operating condition
It calculates, acquires fatigue safety coefficient S new under ahead condition A againHAWith fatigue safety coefficient S new under anti-turner condition BHB, then
The comprehensive fatigue safety coefficient of multi-state takes the two smaller value as follows:
SHM=min (SHA,SHB)
Further, in the step D1, if static fatigue cycle-index separation NH0Corresponding fatigue safety coefficient
Less than 1, then the fatigue damage rate D under the operating conditioniFor infinity；If cycle-index NH0+ n Δ N reaches infinite life fatigue and cyclic
Number separation NHCFatigue safety coefficient is still greater than 1 afterwards, then the flexural fatigue damage ratio D under the operating conditioniIt is zero.
The beneficial effects of the present invention are:
Comprehensive fatigue safety coefficient calculation method under a kind of drive axle transmission system components multi-state disclosed by the invention,
The comprehensive fatigue safety coefficient of multi-state for realizing the key components and parts such as axis, bearing, the gear in transmission system calculates, and makes to design
Person can check the synthesis fatigue safety coefficient of part under multi-state integrated condition when being designed, to ensure that drive axle is driven
The fatigue safety performance of system all reaches design requirement without influencing its service life, the stabilization enhanced product performance, Jin Erti
The qualification rate of high product.The calculation method, which is easy to program under all kinds of common programming language environment, to be realized, meter with higher
Efficiency is calculated, can be widely applied in the multi-state comprehensive design check of various more support shafting drive mechanisms.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of drive axle transmission system provided by the invention；
Fig. 2 is the change curve of bending fatigue stress provided by the invention and cycle-index.
Specific embodiment
The following examples are intended to illustrate the invention, but is not limited to protection scope of the present invention.
Drive axle transmission system includes 3 axis, 5 bearings and a pair of of hypoid gear pair, as shown in Figure 1, wherein 3
Axis is respectively small wheel shaft 31, big wheel shaft 32 and differential axle 33；5 bearings are respectively the first roller bearing 51, the second Roller Shaft
52, third roller bearing 53, the 4th roller bearing 54 and the 5th roller bearing 55 are held, a pair of of hypoid gear pair 2 includes one
A pinion gear and a gear wheel, the both ends of drive axle transmission system are respectively arranged with input torque 10 and output torque 11；Its
In the components successively from top to bottom installed on small wheel shaft be the first roller bearing, the second roller bearing, hypoid gear
Secondary pinion gear and third roller bearing；Torque input position is small axle ends, input torque as shown in fig. 1；In differential
The components successively installed from left to right on device axis be the 5th roller bearing, big wheel shaft, hypoid gear pair gear wheel and
4th roller bearing.
Embodiment 1
Synthesis fatigue safety coefficient calculating side of the bearing in Driven Gear of Final Reduction Gear that embodiment 1 provides under multi-state
Method, comprising the following steps:
Step A: establishing the Static Analysis Model of Micro-machined of the system, and the Static Analysis Model of Micro-machined includes 3 axis, 5 bearings
With a pair of of hypoid gear pair, components are calculated in a certain single operating condition Ni(i is 1 to NLNatural number) under stress.Its
In, the foundation of Static Analysis Model of Micro-machined please refer to that " automobile engineering " 2016 the 8th phase of volume 38 publishes " automobile drive axle master subtracts
The finite element analysis of fast device support stiffness " (author Zhou Chi etc.).
The Force Calculation of 3 axis:
Small wheel shaft shares 23 nodes and 22 beam elements, and the elasticity modulus of material is 200GPa, and Poisson's ratio is
0.252, density 7880kg/m3, the stiffness matrix group collection of each beam element is obtained into the Bulk stiffness matrix of small wheel shaft.
Sharing 7 nodes and 6 beam elements on big wheel shaft, the elasticity modulus of material is 207GPa, Poisson's ratio 0.29,
Density is 7800kg/m3, the stiffness matrix group collection of each beam element is obtained into the Bulk stiffness matrix of big wheel shaft.Differential axle is shared
21 nodes and 20 beam elements, the elasticity modulus of shaft material are 207GPa, Poisson's ratio 0.29, density 7800kg/m3,
The stiffness matrix group collection of each beam element is obtained into the Bulk stiffness matrix of differential axle.
The Force Calculation of 5 bearings:
First roller bearing model FAG31312, internal diameter 60mm, outer diameter 130mm, width 33.5mm, average diameter are
95mm, roller number 16, roller diameter 17.18mm, roller effective length 19.8mm, 28.81 ° of bearing contact angle；
Second roller bearing model FAG546439, internal diameter 70mm, outer diameter 165mm, width 57mm, average diameter
117.5mm, roller number 15, roller diameter 22.6mm, roller effective length 39.556mm, 25 ° of bearing contact angle；
Third roller bearing model FAG575867, internal diameter 40mm, outer diameter 94mm, width 30mm, average diameter 67mm,
Roller number 13, roller diameter 16mm, roller effective length 19mm；
4th roller bearing model SKF33021, internal diameter 105mm, outer diameter 160mm, width 43mm, average diameter
132.5mm, roller number 28, roller diameter 13.74mm, roller effective length 29.76mm, 10.67 ° of bearing contact angle；
5th roller bearing model FAG32021, internal diameter 105mm, outer diameter 160mm, width 35mm, average diameter
132.5mm, roller number 28, roller diameter 13.4mm, roller effective length 23.48mm, 16.5 ° of bearing contact angle.Furthermore own
The elasticity modulus of bearing material is 210GPa, and Poisson's ratio is 0.3.
According to the non-linear rigidity calculation formula of roller bearing, the respective non-linear rigidity square of each bearing is calculated
Battle array.
The Force Calculation of a pair of of hypoid gear pair:
Comprising a pair of of hypoid gear pair in transmission system, parameter is as shown in table 1, according to the power of hypoid gear
It learns model calculation formula and gear unit stiffness matrix and equivalent mesh stiffness matrix is calculated.
The design parameter of 1 hypoid gear pair of table
The number of total operating condition is NL=4, the corresponding input load of 4 kinds of operating conditions is as shown in table 2, utilizes Static Analysis Model of Micro-machined
The stress of components under each operating condition can be calculated.The gear train assembly will be calculated using the present invention below sequentially running 4
The synthesis fatigue safety coefficient of each components after kind operating condition.
The corresponding input load situation of 2 operating condition of table
| Input torque (Nm) | Input speed (rpm) | Input cycle-index | |
| First operating condition (positive vehicle is fully loaded) | -5385 | -200 | 0.5e6 |
| Second operating condition (anti-vehicle is fully loaded) | 5385 | 200 | 0.5e6 |
| Third operating condition (positive vehicle is fully loaded) | -5385 | -200 | 0.5e6 |
| 4th operating condition (anti-vehicle is fully loaded) | 5385 | 200 | 0.5e6 |
Step B: synthetic finite service life fatigue safety coefficient of the axis in transmission system after running 4 operating conditions is calculated.This
It include following 3 step in embodiment by taking small wheel shaft as an example.
Step B1: the damage ratio of each operating condition lower axle is calculated.
According to components in a certain single operating condition NiUnder stress and reference standard " selection of closed gear transmission device and
Design " (Design and selection of components for enclosed gear drives, with specific reference to beauty
National standard ANSI/AGMA6001-D97 text page 5) in infinite life fatigue safety coefficient calculation formula calculate single operating condition
NiThe infinite life fatigue safety coefficient F of lower axlesf, calculation expression is；
Wherein, FsfIndicate infinite life fatigue safety coefficient,For meter Sai Si alternate stress,It is averagely answered for meter Sai Si
Power, SfFor fatigue strength, SyFor tensile yield strength.
It is 1.0918 according to the infinite life fatigue safety coefficient that formula 4 calculates axis for example, calculating under the 1st operating condition.Infinitely
Service life fatigue safety coefficient is greater than 1, then illustrates that damage ratio of the axis under the operating condition is 0, i.e. D1=0.
It calculates under the second operating condition, the infinite life fatigue safety coefficient of the axis is 0.5257.Infinite life fatigue safety system
Number calculates cycle-index N when finite lifetime fatigue safety coefficient is 1 under the operating condition less than 102
Wherein, coefficient c and m is related with the Tensile strength limit, σaAnd σmRespectively meter Sai Si alternate stress peace should all
Power, SyFor tensile yield strength, the specific obtaining value method of these parameters refers to ANSI/AGMA6001-D97, wherein σaSee the public affairs of page 8
Formula 13, σmSee the formula 14, S of page 8ySee the formula 31 of page 9.
The then damage ratio D under this operating condition2For
Since third operating condition is identical as the first operating condition, the 4th operating condition is identical as the second operating condition, therefore D3=D1, D4=D2。
Step B2: total damage ratio and all operating conditions are calculated in the equivalent cycle number under maximum damage ratio operating condition.
For 4 operating conditions, total damage ratio DAFor
Calculate corresponding operating condition maximum damage ratio D when damage ratio maximum in all operating conditionsE, i.e.,
DE=max { D1, D2... Di... DNL}
In formula, DiFor the damage ratio of single operating condition.
The case where the second operating condition is with four operating conditions in the present embodiment is identical, is maximum damage ratio DE, to choose the second work
For condition, corresponding cycle-index NE=0.5e6, damage ratio DE=6.8823.Then in maximum damage ratio DETotal damage under operating condition
Hurt rate equivalent cycle times NAFor
Step B3: equivalent cycle times N is usedA=1e6Under maximum damage ratio operating condition, according to the infinite life fatigue
Safety coefficient calculation formula carries out calculation and check to axis again, and acquiring new finite lifetime fatigue safety coefficient is 0.526, this is
Number is the multi-state synthetic finite service life fatigue safety coefficient of axis.
Step C: synthesis fatigue safety coefficient of each bearing in transmission system after running 4 operating conditions is calculated.
It include following 2 step in present embodiment by taking the second roller bearing as an example.
Step C1: the damage ratio of each operating condition lower bearing is calculated.
Firstly, by international standard " rolling bearing: dynamic load rating and rated life time " (Rolling bearings-
The base of rolling bearing in Dynamic load ratings and rating life, referred to as: ISO281-2007) page 10
This rated life time L10Calculation formula calculate the damage ratio of the 1st operating condition bearing, the basic rating life L of rolling bearing10For
The operating condition bearing number of run is L1=0.5e5, then the damage ratio D of the 1st operating condition lower bearing1For
Secondly, calculating the damage ratio of the second operating condition bearing, the basic rating life of rolling bearing is
The operating condition bearing number of run is L2=0.5e5, then the damage ratio D of the second operating condition lower bearing2For
Since third operating condition is identical as the first operating condition, the 4th operating condition is identical as the second operating condition, therefore D3=D1, D4=D2。
Step C2: the total damage ratio D of bearing and comprehensive fatigue safety coefficient S are calculated
The total damage ratio D of bearing is
When considering multi-state, the comprehensive fatigue safety coefficient S of multi-state is calculated according to total damage ratio
S=D-1/k=0.1566-1/(10/3)=1.744 (formulas 11)
Step D: synthesis fatigue safety coefficient of each gear in transmission system under 4 operating conditions is calculated.
Since gear is related to two kinds of safety coefficients of flexural fatigue and contact fatigue when checking, no matter flexural fatigue, still
The calculation method of the synthesis fatigue safety coefficient of contact fatigue, pinion gear and gear wheel is all identical, and the embodiment is with pinion gear
For flexural fatigue, then the calculating of the synthesis fatigue safety coefficient of hypoid gear pair includes the following steps:
Step D1: fatigue damage rate of the gear under each operating condition is calculated.
With reference to Fig. 2, in the relation curve of bending fatigue stress S and cycle-index N, abscissa represents parts turn circulation
Number, ordinate represent stress value, and each point on curve indicates the stress value of the failure of the flexural fatigue under some cycle-index.
For the first operating condition, the specified number of run when safety coefficient is 1 is calculated, in the flexural fatigue SN of gear material
In curve comprising two key points be such as the static fatigue cycle-index separation N in Fig. 2 respectivelyH0=0.001e6With the unlimited longevity
Order fatigue life cycle separation NHC=3e6。
First with biggish step delta N=1e4From cycle-index NH0Start using Gleason (Gleason) fatigue safety system
Number calculation formula checks criterion calculation gear fatigue safety coefficient, and wherein Gleason calculates check canonical reference Beijing Gear Factory and turns over
" intensive analysis of Gleason bevel gear and the calculating " of " the Gleason Prospects of Spiral Bevel Gears-Technology data collection of translations " the third volume of a work translated, with following
The increase of ring number, the fatigue safety coefficient acquired can be gradually reduced, when cycle-index increases to 7e4When, fatigue safety coefficient
Start less than 1, then corresponding cycle-index should be in 6e when safety coefficient is 14With 7e4Between；And then it is accurately looked for 1 for step-length
Corresponding cycle-index N when the safety coefficient arrived is closest to 1HR1=62580.
After acquiring specified number of run, tooth bending fatigue damage rate is
In formula, NiFor actual motion number, NHRiFor specified number of run, wherein specified number of run NHRiUsing Gleason
Fatigue safety coefficient calculation formula checks standard or international standard fatigue safety coefficient calculation formula and carries out Checking Fatigue to gear
And number of run when safety coefficient is 1 is calculated, international standard fatigue safety coefficient calculation formula refers to international standard " spur gear
With calculating (the Calculation of load capacity of spur and helical of helical gear bearing capacity
Gears) " (abbreviation ISO6336-2006).
For the second operating condition, the number of run when safety coefficient is 1 is calculated.First with biggish step delta N=1e4From
Cycle-index NH0Start to calculate using Gleason and checks criterion calculation gear fatigue safety coefficient, with the increase of cycle-index,
The fatigue safety coefficient acquired can be gradually reduced, when cycle-index increases to 1e4When, fatigue safety coefficient starts then to pacify less than 1
Corresponding cycle-index should be in 0.001e when being 1 for overall coefficient6With 1e4Between；And then the safety system accurately found with 1 for step-length
Corresponding cycle-index N when number is closest to 1HR2=7575.
After acquiring specified number of run, tooth bending fatigue damage rate is
Since third operating condition is identical as the first operating condition, the 4th operating condition is identical as the second operating condition, therefore D3=D1, D4=D2。
Step D2: the total damage ratio of gear and all ahead condition A and all anti-turner condition B are calculated in maximum damage ratio work
Equivalent cycle number under condition.
Include 2 ahead condition A and 2 anti-turner condition B in 4 operating conditions, then calculates separately the damage of all ahead conditions
Hurt DAWith the damage D of all anti-turner conditionsBIt is as follows
In all operating conditions, the maximum operating condition of damage ratio is third operating condition and the 4th work in ahead condition and anti-turner condition
Condition, corresponding damage ratio are respectively D3And D4, corresponding original loop number is respectively NAmax=0.5e6And NBmax=0.5e6.Institute
There is ahead condition in the equivalent cycle number under maximum damage ratio operating conditionAll anti-turner conditions are in maximum damage ratio work
Equivalent cycle number under conditionIt calculates as follows
Step D3: according to Gleason fatigue safety coefficient calculation formula or international standard fatigue safety coefficient calculation formula point
It Yong not equivalent cycle numberWithIn maximum damage ratio DECalculation and check is carried out under load under operating condition, acquires positive vehicle again
New fatigue safety coefficient S under operating condition AHAWith fatigue safety coefficient S new under anti-turner condition BHB, then the comprehensive fatigue of multi-state is pacified
Overall coefficient takes the two smaller value as follows:
SHM=min (SHA,SHB) (formula 18)
Gleason fatigue safety coefficient calculation formula are as follows:
Wherein, SPAnd SGThe safety coefficient of steamboat and bull wheel, S are respectively representedtPAnd StGRespectively represent steamboat and bull wheel
Calculate stress value, SwtPAnd SwtGRespectively represent steamboat and bull wheel allowable working stress value.
International standard fatigue safety coefficient calculation formula:
Wherein, SF1And SF2The safety coefficient of steamboat and bull wheel, σ are respectively representedFG1,σFG2Respectively represent steamboat and bull wheel
Allowable stress value, σF1,σF2It respectively represents steamboat and bull wheel calculates stress value.
By the available each multi-state COMPREHENSIVE CALCULATING for checking components of above-mentioned calculating as a result, by itself and single condition calculating
As a result it is listed in as in the following table 3.As can be seen that safety coefficient can be after considering multi-state in design and influencing in table
Decline, designer can use method of the invention by main operating condition (load, speed, circulation when designing transmission system
Number etc.) consider be more nearly with actual motion service condition, efficiently and accurately to each components carry out multi-state synthesis it is tired
Labor Security Checking.
Table 3 respectively checks the multi-state COMPREHENSIVE CALCULATING result of components compared with either simplex condition
Although above having used general explanation and specific embodiment, the present invention is described in detail, at this
On the basis of invention, it can be made some modifications or improvements, this will be apparent to those skilled in the art.Therefore,
These modifications or improvements without departing from theon the basis of the spirit of the present invention are fallen within the scope of the claimed invention.
Claims (6)
1. comprehensive fatigue safety coefficient calculation method, the components include under a kind of drive axle transmission system components multi-state
Axis, bearing and gear, if the operating condition number of the drive axle transmission system components is NL(NLFor the natural number greater than 1), it is special
Sign is, the calculation method the following steps are included:
Step A: establishing the Static Analysis Model of Micro-machined of drive axle transmission system, calculates components in a certain single operating condition Ni(i be 1 to
NLNatural number) under stress；
Step B: it calculates in NLThe synthetic finite service life fatigue safety coefficient of a operating condition lower axle；
Step C: each bearing in transmission system is calculated in NLSynthesis fatigue safety coefficient under a operating condition；
Step D: each gear in transmission system is calculated in NLSynthesis fatigue safety coefficient under a operating condition.
2. comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state as described in claim 1,
It is characterized in that, the step B the following steps are included:
Step B1: single operating condition N is calculatediThe damage ratio of lower axle:
According to components in a certain single operating condition NiUnder stress and reference standard " selection and design of closed gear transmission device "
In infinite life fatigue safety coefficient calculation formula calculate single operating condition NiThe infinite life fatigue safety coefficient of lower axle；
Wherein, FsfSafety coefficient is represented,For meter Sai Si alternate stress,For meter Sai Si mean stress, SfFor fatigue strength, Sy
For tensile yield strength；
Step B2: calculating the equivalent cycle number of the total damage ratio and all operating conditions of axis under damage ratio maximum duty,
Wherein NLTotal damage ratio D of a operating conditionACalculation formula are as follows:
Calculate corresponding operating condition maximum damage ratio D when damage ratio maximum in all operating conditionsE, its calculation formula is
DE=max { D1, D2... Di... DNL}
In formula, DiFor the damage ratio of single operating condition；
If maximum damage ratio DECorresponding cycle-index is NE, then all operating conditions are in maximum damage ratio DEUnder total damage ratio etc.
Imitate cycle-index NACalculation formula are as follows:
Step B3: according to the infinite life fatigue safety coefficient calculation formula again to equivalent cycle-index NAIt is damaged in maximum
Rate DEAxis under operating condition is checked, and calculates the synthesis fatigue safety coefficient of the axis under multi-state.
3. comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state as claimed in claim 2,
It is characterized in that, if infinite life fatigue safety coefficient is greater than 1, illustrating damage of the axis under the operating condition in the step B1
Hurting rate is 0；If infinite life fatigue safety coefficient is less than 1, damage ratio DiFor
Wherein, NiFor cycle-index of the axis at operating condition i, the cycle-index N0iCalculation formula it is as follows:
Wherein, coefficient c and m is related with the Tensile strength limit, σaAnd σmRespectively meter Sai Si alternate stress and mean stress,
SyFor tensile yield strength.
4. comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state as described in claim 1,
It is characterized in that, the step C the following steps are included:
Step C1: according to the substantially specified longevity of the rolling bearing of international standard " rolling bearing: dynamic load rating and rated life time "
The calculation formula of life calculates the damage ratio of each operating condition lower bearing；Wherein basic rating life L10Calculation formula be
Wherein, CdFor the basic dynamic load rating of bearing, k is bearing index, PrFor dynamic equivalent radial load；
If the number of run of the i-th operating condition bearing is Li, then the fatigue safety coefficient S under the i-th operating condition is utilizediThe i-th operating condition can be calculated
The damage ratio D of lower bearingiFor
Step C2: the total damage ratio of bearing and comprehensive fatigue safety coefficient are calculated
The calculation formula of total damage ratio D of all operating conditions of bearing are as follows:
The calculation formula of the comprehensive fatigue safety coefficient S of multi-state are as follows:
5. comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state as described in claim 1,
It is characterized in that, the step D the following steps are included:
Step D1: the damage ratio D of each operating condition lower gear fatigue is calculatedi, wherein the i-th operating condition lower gear flexural fatigue damage ratio Di
Calculation formula are as follows:
In formula, NiFor actual motion number, NHRiFor specified number of run；
Step D2: calculating the total damage ratio of gear and all ahead condition A and all anti-turner condition B are equivalent under maximum damage ratio
Cycle-index；
Step D3: equivalent cycle number is used respectivelyWithIn maximum damage ratio DECalculation and check is carried out under load under operating condition,
Again fatigue safety coefficient S new under ahead condition A is acquiredHAWith fatigue safety coefficient S new under anti-turner condition BHB, then multiplexing
The comprehensive fatigue safety coefficient of condition takes the two smaller value as follows:
SHM=min (SHA,SHB)。
6. comprehensive fatigue safety coefficient calculation method under drive axle transmission system components multi-state as claimed in claim 5,
It is characterized in that, in the step D1,
If static fatigue cycle-index separation NH0Corresponding fatigue safety coefficient is less than 1, then the fatigue damage rate under the operating condition
DiFor infinity；If cycle-index NH0+ n Δ N reaches infinite life fatigue life cycle separation NHCFatigue safety coefficient is still afterwards
Greater than 1, then the flexural fatigue damage ratio D under the operating conditioniIt is zero.
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