CN109708889A - The horizontal choosing method of accelerated stress of space grease lubrication bearing accelerated life test - Google Patents
The horizontal choosing method of accelerated stress of space grease lubrication bearing accelerated life test Download PDFInfo
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Abstract
The present invention relates to mechanical devices life test fields, disclose a kind of horizontal choosing method of accelerated stress of space grease lubrication bearing accelerated life test, with solve the problems, such as can not Rational choice grease lubrication bearing accelerated life test accelerated stress it is horizontal.Main points of the invention are as follows: first calculate bearing the ratio between roughness of oil film thickness and contact surface Λ when working under normal stress is horizontal, the minimum grease film thickness H between bearing ball and inner peripheral surface is calculated further according to resulting Λ, the minimum oil film thickness h between bearing ball and inner ring is obtained further according to Hmin, then using rotary speed threshold value as defined in lubricant grease design manual as the revolving speed n of accelerated life test, and according to hminThe maximum loaded load Q of ball is calculated with nmax, further according to QmaxThe accelerated stress for accelerated life test is acquired, then judges whether the accelerated stress acquired exceeds the carrying range of experimental bench, adjustment n value is reduced if exceeding, recalculates Qmax, until meeting the requirements.The present invention is suitable for bearing accelerated life test.
Description
Technical field
The present invention relates to mechanical devices life test field, in particular to space grease lubrication bearing accelerated life test
The horizontal choosing method of accelerated stress.
Background technique
Due in space have alternating temperature-changing, condition of high vacuum degree, microgravity, intense radiation, the presence of the complex situations such as elemental oxygen,
And space flight engineering goods have the characteristics of expensive, the long-life, unrepairable.Aerospace field is to component of machine
More stringent requirements are proposed for reliability and life prediction.For the running time of bearing can up to several years it is even more,
Especially bearing used in aerospace field, therefore the development service life for carrying out 1:1 to bearing in the actual use environment can
It is still all economically either unacceptable from the time by property verification test.Therefore we just need to pass through acceleration
Life test verifies the reliably working ability of bearing and the predicting residual useful life of bearing.Do not changing fault mode and event
Under conditions of hindering mechanism, life test is carried out to components with the method for increasing stress, to reach accelerated life test shortening
The effect of test period.
Accelerated life test is the method in the case where not changing product failure mechanism, by increasing stress level, is added
Fast product failure shortens test period, goes out product service life under normal stress effect in relatively short test period interior prediction
The method of feature.The premise for increasing stress level is not change failure mechanism.If loaded stress level is excessive, production is changed
The failure mechanism of product, then accelerated life test just loses meaning, if loaded stress level is too small, leads to accelerated aging
Test period excessive cycle, accelerated life test are unable to get optimal effect, meanwhile, test period cost input increases.
Rotary mechanical part (especially outside station module) is tested for space science, is mainly with solid lubrication
It is main.According to being directed to admittedly in " GBT 28878.7-2016 space science tests the 7th part of rotatable parts specification: reliability test "
The accelerated life test plan of body lubricating ball bearings rotary part, what lubricating system was selected is solid lubrication, and is only chosen
As its accelerated stress, acceleration effect is not obvious bearing revolving speed.Become gravity experiment for the space station of grease mixed lubrication
Cabinet (in cabin) centrifuge turntable bearing, wherein " GBT 28878.7-2016 space science tests the 7th part of rotatable parts specification:
Reliability test " it the wear-out failure model of rotatable parts solid lubrication ball bearing that is mentioned and is not suitable for.
It is relatively difficult that effective accelerated life test is carried out for oil lubrication long-life spacecraft mechanism (rolling bearing).Needle
To the accelerated stress water in the spacecraft mechanism accelerated life test of grease lubrication long-life for how to choose accelerated life test
It is flat, it is not all studied deeply both at home and abroad.Hereby, the present invention proposes that one kind adds about grease lubrication bearing accelerated life test
The choosing method of fast stress level.
Summary of the invention
The technical problem to be solved by the present invention is proposing that a kind of acceleration of space grease lubrication bearing accelerated life test is answered
The horizontal choosing method of power, with solve can not the accelerated stress of Rational choice grease lubrication bearing accelerated life test horizontal ask
Topic.
To achieve the above object, the technical solution adopted by the present invention is that: space grease lubrication bearing accelerated life test
The horizontal choosing method of accelerated stress, comprising the following steps:
A. bearing the ratio between roughness of oil film thickness and contact surface Λ when working under normal stress is horizontal is calculated, and will
The Λ being calculated is as the ratio between oil film thickness in accelerated life test and the roughness of contact surface；
B. the minimum grease film thickness H between bearing ball and inner peripheral surface is calculated according to the Λ that step A is obtained；
C. the minimum oil film thickness h between bearing ball and inner ring is obtained according to Hmin；
D. using rotary speed threshold value as defined in lubricant grease design manual as the revolving speed n of accelerated life test, and according to hminWith
N calculates the maximum loaded load Q of ballmax；
E. according to QmaxAcquire the accelerated stress for accelerated life test；
Whether the accelerated stress that F. judgment step E is acquired exceeds the carrying range of experimental bench, if exceeding the carrying of experimental bench
Range then reduces in step D and calculates QmaxWhen n value, recalculate Qmax, and continue step E, until the acceleration that step E is acquired
Carrying range of the stress without departing from experimental bench.
Preferably, the range for the Λ that step A is obtained are as follows: 1.5 < Λ < 2.
Further, in step B, H can be calculated by the following formula:
Wherein, σ1With σ2For the roughness of two contact surfaces of bearing ball.
Further, in step C, hminFormula H=1.5~1.7h can be passed throughminIt obtains.
Further, in step D, rotary speed threshold value as defined in lubricant grease design manualWherein, KaIt is axis
Coefficient is held, n is revolving speed, dmFor nominal diameter.
Further, in step D, QmaxIt can be calculated by the following formula:
Wherein, DwFor the diameter of bearing ball；dmFor the pitch diameter of bearing；α is pressure viscosity coefficient；η0For under atmospheric pressure
Lubricating oil dynamic viscosity；E0For equivalent modulus of elasticity；K is the ellipticity of contact area；E is the bottom of natural logrithm；γiBearing
Structural parameters,α is bearing contact angle.
Further, in step E, the calculation of accelerated stress is as follows:
1) when bearing is only acted on by radial force Fr, Fr passes through formulaIt obtains, wherein Fr is radial carries
Lotus, Z are bearing ball number, and α is bearing contact angle；
2) when bearing is only acted on by bearing Fa, Fa passes throughIt obtains, wherein Fa is radial load, and Z is
Bearing ball number, α are bearing contact angle；
3) when bearing by bearing Fa with and when radial force Fr synergy, Fr and Fa pass through formulaIt obtains, wherein α is bearing contact angle, Jr(ε) is power load distributing Radial Integrals, Ja
(ε) is that power load distributing axially integrates.
The beneficial effects of the present invention are: the present invention accelerates the longevity for the centrifuge turntable bearing of the grease compounded lubrication in space station
It is horizontal for how to choose the accelerated stress of accelerated life test in life test, by lubricant medium to the threshold limit of revolving speed with
And guarantee lubricating status consistency carry out the appropriate accelerated stress that reverse-direction derivation accelerated life test is taken, reach controllability compared with
High accelerated stress chooses effect, can guarantee test consistency, also can carry out effect to test tape in time, economically.
Detailed description of the invention
Fig. 1 is flow chart of the invention.
Specific embodiment
For rolling ball bearing, the accelerated stress during accelerated life test is chosen to accelerated life test to Guan Chong
It wants.Appropriate selection accelerated stress not merely can be effectively carried out accelerated life test, while economically also greatly save pre-
It calculates.In conjunction with increasing load and increasing revolving speed, they are combined as accelerated stress, accelerated aging examination is carried out to test turntable bearing
It tests, compensates for deficiency brought by independent loading stress, while ensure that failure mechanism is consistent, appropriate acceleration can be selected
Stress level, and reach biggish acceleration effect, while loading revolving speed and reaching the effect of accelerated stress controllability with loaded load
Fruit.
(1) selection of accelerated stress
From bearing calculation of the rating life formula:
Wherein, C is basic dynamic load rating, and P is equivalent radial load, and n is revolving speed.
From the calculation of the rating life formula of above-mentioned bearing it is found that bearing life and load, revolving speed are all related.Plus load
When as accelerated stress, acceleration effect is obvious, and load is easy to control during the test.When revolving speed is as accelerated stress
When, acceleration effect is not apparent.
Meanwhile it lubricating film thickness and being closely related with temperature, pressure, speed.Due to the uncontrollability of temperature, and then we do not adopt
Use temperature as the accelerated stress of test specimen bearing accelerated life test.Pressure when bearing loaded load, between ball and raceway
Power just will increase, and film thickness can reduce；When revolving speed increases, film thickness will increase again.If we can find balanced revolving speed and load
Lotus is just able to maintain its film thickness and stablizes in a certain range, keeps film thickness certain, be just able to maintain the consistency of lubricating status, into
And keep the consistency of failure mechanism during accelerated life test.
(2) selection of stress level
The feature of accelerated life test most critical be exactly the product in the case where accelerated stress is horizontal failure (failure) mode with
Failure (failure) mechanism should under normal stress horizontal force failure (failure) mode and failure (failure) mechanism institute it is consistent.
Test bearing failure often since the change of lubricating status, and lubricating status be by oil film thickness Lai
It determines, and oil film thickness depends primarily on following factor: the viscosity of lubricating oil, speed parameter, load (accelerated stress)
Parameter, structural parameters, elastic parameter etc..
For rolling ball bearing, the oil film thickness between usual rolling element and outer rollaway nest will be greater than inner ring and rolling element
Between oil film thickness.Minimum oil film thickness calculation formula between ball and inner ring is as follows:
Wherein, hminFor minimum thickness, unit m；DwFor the diameter of bearing ball, unit m；dmFor the pitch diameter of bearing,
Unit m；α is pressure viscosity coefficient, unit Pa-1；η0For lubricating oil dynamic viscosity under atmospheric pressure, unit Pas；N is revolving speed,
Unit is r/min；E0For equivalent modulus of elasticity, unit Pa；QmaxFor loaded maximum ball load；K is the ellipse of contact area
Circle rate；E is the bottom of natural logrithm；γiBearing structural parameters (by design bearing handbook refering to).α is to connect
Feeler；Wherein,R is interior rollaway nest radius of curvature,For viscous pressure factor alpha, lubricating oil viscosity η0And equivalent modulus of elasticity E0, used by can looking into respectively
Lubricant parameter and bearing material it can be seen that.Qmax, loaded load maximum for bearing ball can " rolling bearing be set according to bearing
Meter principle " (Deng Si bis- editions) calculated.Middle low speed bearing and the even ultralow revolving speed of space station turntable bearing are turned
Dish axle is held, and does not consider the influence of movement, is calculated by dead load power load distributing.
For angular contact ball bearing:
1) when bearing is only acted on by radial force Fr,Wherein Fr is radial load, and Z is bearing ball
Number, α are bearing contact angle；
2) when bearing is only acted on by bearing Fa,Wherein Fa is radial load, and Z is bearing ball
Number, α is bearing contact angle；
3) when bearing by bearing Fa with and when radial force Fr synergy, need basis " rolling bearing design principle "
Detailed its Q of calculating in (Deng Si bis- editions)max.Particularly with this double-row angular contact bal bearing of space station centrifuge turntable bearing
For, according to bearing Fa with and radial force Fr and contact angular dependenceObtain meeting point for double-row bearing
Cloth situation, and table look-up and obtain parameter power load distributing Radial Integrals Jr(ε) and axial integral Ja(ε), further according toRelational expression, and then Q can be calculatedmaxValue.
In summary three kinds of calculating QmaxMethod, the Q that will be obtainedmaxValue, which is brought into, calculates hminIt goes, can will lubricate in the process
Oil film thickness is effectively joined together with revolving speed n, load triadic relation, facilitates subsequent true fixed value calculation.
As film thickness formula it is found that minimum oil film thickness is to load suffered by bearing and insensitive, and for bearing
For service life, accelerated factor can by chance be significantly increased again by increasing load.And accelerated factor controllability is high.The revolving speed pair of bearing
Minimum oil film thickness also has an impact, and also has an impact to bearing life, and controllable.By formula also it is found that temperature is to minimum oil
The influence highly significant of film thickness.But temperature as accelerated factor when, be difficult to control, make oil film thickness keep with just
Consistency under ordinary water is flat.
In conjunction with minimum oil film thickness calculation formula, we are using revolving speed and load as accelerated stress, in addition, referring to lubricating oil
Rouge design manual learns, maximum speed (K under the bearing slow-speed of revolution under grease lubricationa×n×dm≤ 350000, wherein KaIt is bearing
Coefficient, n are revolving speed, dmFor nominal diameter), and load suffered by bearing is combined, ensuring oil film thickness and is operating normally
When it is consistent after, finally determine the level of accelerated stress, the consistency of its accelerator ensured by calculating.So that accelerating
Journey is controllably changed, concise.
In addition, needing to consider the composite film thickness of grease lubrication during determining accelerated stress.Studies have shown that rouge moistens
Sliding lubrication film thickness in start-up conditions is greater than the oil film thickness of the oil lubrication under square one, but again due to lubricating grease
Crowding-out effect, the lubricating film film thickness of final rouge can stablize the rouge profit the 50%~70% of base oil oil film thickness, after stablizing
The 1/2 of the close basic oil film thickness of synovial membrane thickness.So oil film thickness takes H=1.5~1.7h when final grease compounded lubricationmin。
After obtaining minimum grease lubrication film thickness H, the roughness of minimum grease Film thickness values H and contact surface is carried out
Compare, and then the ratio between roughness of oil film thickness and contact surface (film thickness ratio Λ) is at losing quasi- accelerated life test middle (center) bearing
The key point that effect mechanism is consistent.
(H the smallest grease film thickness, unit μm between ball and inner peripheral surface；σ1With σ2To contact table
The roughness in face, unit μm)
Wherein, Λ is the important parameter for determining lubricating property.Research shows that: 1) when Λ < 1, the surface to contact with each other can be sent out
It is raw directly to contact, it is equivalent to dry friction, will cause scratch gluing etc.；2) when 1 < Λ < 3, referred to as pertical-film EHL, contact
Partial region will form elastohydrodynamic lubrication film between surface, be in mixed lubricating state；3) when Λ > 3, referred to as full film
Elastohydrodynamic lubrication, the thickness of oil film are enough two contact surfaces are completely separated, formation hydrldynamic pressure lubrication film.Profit in rolling bearing
Sliding state is largely to be in mixed lubricating state, therefore be directed to ordinary circumstance, the present invention can be excellent between 1.5 < Λ < 2
The Λ value for guaranteeing bearing inner race and ball is in 1.5 < Λ <, 2 range by choosing.
To sum up, guarantee that the Λ value and bearing of bearing inner race and ball when accelerated life test work in the case where normal stress is horizontal
When Λ value be in same range, can guarantee that the lubricating status consistency of bearing and the revolving speed factor are limited in grease lubrication model
In enclosing, while ensuring that accelerated life test, suitable accelerated stress value is got.
In conjunction with the above analysis, the invention proposes a kind of accelerated stress water of space grease lubrication bearing accelerated life test
Flat choosing method, with solve the problems, such as can not Rational choice grease lubrication bearing accelerated life test accelerated stress it is horizontal.The party
Method to the threshold limit of revolving speed and guarantees lubricating status consistency come reverse-direction derivation accelerated life test institute by lubricant medium
The appropriate accelerated stress taken, as shown in Figure 1, specific steps are as follows:
A. bearing the ratio between roughness of oil film thickness and contact surface Λ when working under normal stress is horizontal is calculated, and will
The Λ being calculated is as the ratio between oil film thickness in accelerated life test and the roughness of contact surface.1 < Λ under normal circumstances
< 3 is the lubricating status consistency that can guarantee bearing；But since the lubricating status in rolling bearing is largely in 1.5 < Λ
Between < 2, the Λ value for guaranteeing bearing inner race and ball is preferably in 1.5 < Λ <, 2 range by the present invention.
B. the minimum grease film thickness H between bearing ball and inner peripheral surface is calculated according to the Λ that step A is obtained, wherein H can
It is calculated by the following formula:
Wherein, σ1With σ2For the roughness of two contact surfaces of bearing ball.
C. the minimum oil film thickness h between bearing ball and inner ring is obtained according to Hmin, wherein hminFormula H=can be passed through
1.5~1.7hminIt obtains.
D. using rotary speed threshold value as defined in lubricant grease design manual as the revolving speed n of accelerated life test, and according to hminWith
N calculates the maximum loaded load Q of ballmax.Wherein, rotary speed threshold value as defined in lubricant grease design manualKaIt is axis
Coefficient is held, n is revolving speed, dmFor nominal diameter；QmaxIt can be calculated by the following formula:
Wherein, DwFor the diameter of bearing ball；dmFor the pitch diameter of bearing；α is pressure viscosity coefficient；η0For under atmospheric pressure
Lubricating oil dynamic viscosity；E0For equivalent modulus of elasticity；K is the ellipticity of contact area；E is the bottom of natural logrithm；γiBearing
Structural parameters,α is bearing contact angle,R is interior rolling
Road radius of curvature,
E. according to QmaxAcquire the accelerated stress for accelerated life test.
Wherein, QmaxIt can be calculated by the following formula:
Wherein, DwFor the diameter of bearing ball；dmFor the pitch diameter of bearing；α is pressure viscosity coefficient；η0For under atmospheric pressure
Lubricating oil dynamic viscosity；E0For equivalent modulus of elasticity；K is the ellipticity of contact area；E is the bottom of natural logrithm；γiBearing
Structural parameters,α is bearing contact angle,R is interior rolling
Road radius of curvature.
For angular contact ball bearing, the calculation of accelerated stress is as follows:
1) when bearing is only acted on by radial force Fr, Fr passes through formulaIt obtains, wherein Fr is radial carries
Lotus, Z are bearing ball number, and α is bearing contact angle；
2) when bearing is only acted on by bearing Fa, Fa passes throughIt obtains, wherein Fa is radial load, and Z is
Bearing ball number, α are bearing contact angle；
3) when bearing by bearing Fa with and when radial force Fr synergy, Fr and Fa pass through formulaIt obtains, wherein α is bearing contact angle, Jr(ε) is power load distributing Radial Integrals, Ja
(ε) is that power load distributing axially integrates.
Whether the accelerated stress that F. judgment step E is acquired exceeds the carrying range of experimental bench, if exceeding the carrying of experimental bench
Range then reduces in step D and calculates QmaxWhen n value, recalculate Qmax, and continue step E, until the acceleration that step E is acquired
Stress finally obtains appropriate accelerated stress without departing from the carrying range of experimental bench.
Claims (7)
1. the horizontal choosing method of accelerated stress of space grease lubrication bearing accelerated life test, which is characterized in that including as follows
Step:
A. bearing the ratio between roughness of oil film thickness and contact surface Λ when working under normal stress is horizontal is calculated, and will be calculated
Obtained Λ is as the ratio between oil film thickness in accelerated life test and the roughness of contact surface；
B. the minimum grease film thickness H between bearing ball and inner peripheral surface is calculated according to the Λ that step A is obtained；
C. the minimum oil film thickness h between bearing ball and inner ring is obtained according to Hmin；
D. using rotary speed threshold value as defined in lubricant grease design manual as the revolving speed n of accelerated life test, and according to hminIt is counted with n
Calculate the maximum loaded load Q of ballmax；
E. according to QmaxAcquire the accelerated stress for accelerated life test；
Whether the accelerated stress that F. judgment step E is acquired exceeds the carrying range of experimental bench, if exceeding the carrying range of experimental bench,
It then reduces in step D and calculates QmaxWhen n value, recalculate Qmax, and continue step E, until accelerated stress that step E is acquired not
Carrying range beyond experimental bench.
2. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, the range for the Λ that step A is obtained are as follows: 1.5 < Λ < 2.
3. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, in step B, H is calculated by the following formula:
Wherein, σ1With σ2For the roughness of two contact surfaces of bearing ball.
4. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, in step C, hminPass through formula H=1.5~1.7hminIt obtains.
5. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, in step D, rotary speed threshold value as defined in lubricant grease design manualWherein, KaIt is bearing module, n
For revolving speed, dmFor nominal diameter.
6. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, in step D, QmaxIt is calculated by the following formula:
Wherein, DwFor the diameter of bearing ball；dmFor the pitch diameter of bearing；α is pressure viscosity coefficient；η0To be lubricated under atmospheric pressure
Oily dynamic viscosity；E0For equivalent modulus of elasticity；K is the ellipticity of contact area；E is the bottom of natural logrithm；γiThe structure of bearing
Parameter,α is bearing contact angle.
7. the horizontal choosing method of accelerated stress of grease lubrication bearing accelerated life test in space as described in claim 1,
It is characterized in that, in step E, the calculation of accelerated stress is as follows:
1) when bearing is only acted on by radial force Fr, Fr passes through formulaIt obtains, wherein Fr is radial load, and Z is
Bearing ball number, α are bearing contact angle；
2) when bearing is only acted on by bearing Fa, Fa passes throughIt obtains, wherein Fa is radial load, and Z is bearing
Ball number, α are bearing contact angle；
3) when bearing by bearing Fa with and when radial force Fr synergy, Fr and Fa pass through formulaIt obtains, wherein α is bearing contact angle, Jr(ε) is power load distributing Radial Integrals, Ja
(ε) is that power load distributing axially integrates.
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