CN106248379B - A kind of bearing with solid lubricant accelerated life test loading spectrum design method - Google Patents
A kind of bearing with solid lubricant accelerated life test loading spectrum design method Download PDFInfo
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Abstract
The present invention relates to a kind of bearing with solid lubricant accelerated life test loading spectrum design methods, which is characterized in that includes the following steps：1) the operation on orbit section of bearing with solid lubricant is obtained；2) it converts obtained loading spectrum block to loads typical and composes block；3) according to the failure mechanism of bearing with solid lubricant and Dynamic wear rule, classification processing is carried out to loading spectrum block.Under the premise of not changing bearing with solid lubricant failure mechanism, realize that the accelerated life test of bearing with solid lubricant has the purpose of preferable acceleration effect.
Description
Technical field
The invention belongs to the spaceborne transmission mechanism critical component reliability fields of space flight, and in particular to a kind of acquisition solid lubrication
The method of bearing accelerated life test loading spectrum.
Background technology
Shown according to external satellite statistics：Spaceborne transmission mechanism is defended caused by insufficient lubrication caused by " stuck " is
One of the main reason for star fails, and the fretting wear of spaceborne transmission mechanism is the major reason for causing its performance to decline.Gu
Body lubrication bearing is the critical component of spaceborne transmission mechanism, and performance degradation caused by long time running and precision forfeiture are to influence
The key factor of satellite life-span in-orbit, thus its high reliability and long-life are to the development of China's spacecraft and using heavy to closing
It wants.The life characteristics of usual product are obtained by doing the method for life test under normal operation.But solid is moistened
For plain besring, design is accurate, weaving process is complicated, production cost is high, specificity is strong, will not generally carry out large batch of life
The case where producing, carrying out its Life cycle life test and relevant destructive life test is with regard to less.And with design, manufacture
The service life of the development of technology and the use of new material, space flight bearing with solid lubricant is increasingly longer, so that life test
It needs to expend very long test period and a large amount of testing expenses, it could even be possible to required test period is caused to be far longer than
Lead time, it is difficult to life appraisal and verification are completed before being taken into use, thus to the accelerated life test of bearing with solid lubricant
Gradually it is valued by people.
Currently, in industrial quarters, electronic product stress accelerated life test method comparative maturity has perfect experiment rule
Model and statistical method can be followed, but the test sample amount needed is big, and test period is long.Engineering goods are because failure mechanism compares electricity
Sub- product is increasingly complex, not yet forms standardized accelerated life test specification at present.Bearing with solid lubricant is as a kind of precision
Mechanical part, residing space environment and cyclic stress section determines its failure when distinctive lubricating system, work
Pattern is various, the serious characteristic of stress coupling, leads to traditional stress accelerated life test loading spectrum and existing acceleration
Model is difficult to provide accurate life appraisal result.Therefore, the failure mechanism of bearing with solid lubricant how is deeply disclosed, refinement adds
How fast stress is based on the distinctive failure mechanism of bearing with solid lubricant and working stress Section Design accelerated life test loading spectrum
It is the key that break through bearing with solid lubricant accelerated life test theory and statistical method.
Accelerated life test is, by reinforcing the method for stress, to accelerate production under the premise of not changing product failure mechanism
Product failure shortens test period, the method for predicting product life characteristics under normal stress effect in a relatively short period of time.No
Change the premise that failure mechanism is accelerated life test, the environmental stress or working stress that reinforcement product is born are to be accelerated
The necessary means of life test.Accelerated life test is to shorten test period by reinforcing stress, but if stress is excessive, is changed
The failure mechanism of product is become, then accelerated life test just loses meaning.If stress is less than normal, test period can be caused to contract
Short to be not obvious, accelerated life test is unable to get best effect.Accelerated life test loading spectrum refers in accelerated aging
The stress reinforced in experiment and the relationship corresponding to the opposite period.How the actual condition of combination product, determination do not change
It is always to perplex designer's to become product failure mechanism and can play the accelerated life test loading spectrum of preferable acceleration
Problem.
The reference of external product accelerated life test can be retrieved at present, but has focused largely on grinding for statistical method
Study carefully, the content about loading spectrum design is considerably less.Closing policy is taken to China's the relevant technologies in view of foreign countries, we are to state's external-navigation
How its bearing with solid lubricant, which designs accelerated life test loading spectrum, is had no way of learning, accelerated aging of the China to bearing with solid lubricant
The research of experiment is also at the early-stage, and up to the present there has been no the bearing with solid lubricant accelerated agings for being suitable for engineer application in China
Test load composes design method.
Invention content
The present invention is in order to solve under the premise of not changing bearing with solid lubricant failure mechanism, to realize bearing with solid lubricant
Accelerated life test has the purpose of preferable acceleration effect, proposes a kind of bearing with solid lubricant combined stress accelerated life test
Loading spectrum design method provides for bearing with solid lubricant and a kind of not changing failure mechanism and acceleration effect more significantly accelerates
Life test loading spectrum design method, this method practicability and operability are strong, are the rows to bearing with solid lubricant life appraisal
Effective accelerated method.
A kind of bearing with solid lubricant combined stress accelerated life test loading spectrum design method proposed by the present invention, specifically
For：
Step 1: obtaining the operation on orbit section of bearing with solid lubricant.
Operation on orbit section refers to the component to complete a kind of working condition figure that in-orbit aerial mission is drawn, horizontal seat
It is designated as the time, ordinate is the corresponding loading stress of corresponding task and working condition.
Step 2: converting obtained loading spectrum block to loads typical composes block.
Loading spectrum be component in actual operation, the loading stress being subject to, between the time used in working condition and every grade
Correspondence.Such as the axial load suffered by this example middle (center) bearing, the rotating speed of bearing and the correspondence between the duration.
Loads typical spectrum block, that is, representative, can reflect the different grades of loading spectrum of practical working situation.
Step 3: according to the failure mechanism of bearing with solid lubricant and Dynamic wear rule, loading spectrum block is carried out at classification
Reason.
Specifically, the present invention obtains above-mentioned purpose by subordinate's scheme.
A kind of bearing with solid lubricant accelerated life test loading spectrum design method, which is characterized in that include the following steps：
1) the operation on orbit section of bearing with solid lubricant is obtained；
2) it converts obtained loading spectrum block to loads typical and composes block；
3) according to the failure mechanism of bearing with solid lubricant and Dynamic wear rule, classification processing is carried out to loading spectrum block.
Method according to aforementioned schemes, which is characterized in that step 1) includes：By analyzing in bearing with solid lubricant
The abrasion and transfer of lubricating film, provide the pass of plated film wear rate and retainer lubriation material transfer rate and applied stress respectively
System obtains the abrasion of bearing with solid lubricant dynamic complex.
Method according to aforementioned schemes, which is characterized in that step 2) includes：By directly intercepting the load that will be obtained
Lotus spectrum is converted into loads typical spectrum block.
Method according to aforementioned schemes, which is characterized in that step 3) includes：Retainer transfer rate is higher than
Raceway groove plated film wear rate and cause lubricating film excess situation and/or retainer transfer rate be less than raceway groove plated film wear rate
And the loading spectrum block for causing lubricating film to lack merges.
Method according to aforementioned schemes, which is characterized in that step 3) includes：
The abrasion of bearing with solid lubricant dynamic complex obtains in the following way：
For raceway groove plated film rate of depreciation, speed and time are introduced to characterize sliding distance, obtaining wear extent formula is：
Wherein W1For raceway groove plated film wear extent, p1For pressure, v1For sliding speed, t is test period, K1, a, b, c be all
The constant determined based on statistical data；
The relationship between raceway groove plated film wear rate and accelerated stress is fitted by statistical data；In view of solid lubrication
The common accelerated stress of bearing is rotating speed and axial load, this relationship is characterized as：
Ioff=F1(V,P) (2)
Wherein IoffIndicate that raceway groove plated film wear rate, V and P indicate the amplitude of rotating speed and axial load stress respectively；
The recessed of polishing scratch based on retainer is in paraboloid shape, the expression formula for the frame lubricating film transfer amount that is maintained：
Wherein W2For retainer lubricating film transfer amount, p2For average Hertz contact forces, D=v2T is sliding distance, K2、j、m
For the constant determined based on statistical data, v2For relative sliding velocity；Retainer lubriation material moves between rate and accelerated stress
Relationship be：
Ibr=F2(V,P) (4)
Wherein IbrIndicate retainer lubriation material transfer rate；
The lubrication membrane volume W of attrition in interior outer raceway groove is obtained based on (2) formula and (4) formulaoff(t) and retainer is through rolling
The lubrication membrane volume W shifted in the inside outer raceway groove of kinetoplastbr(t), to obtain the Expression of lubrication film thickness under different stress
Formula：
Wherein δ is lubrication film thickness, δ0For raceway groove plated film original depth, A is raceway groove plated film area.According to aforementioned schemes institute
The method stated, which is characterized in that step 3) includes：
The expression formula of the merging is：
Wherein N is the number of loading spectrum block, △ δiFor total lubricating film knots modification corresponding to i-th of loading spectrum block, △ δA
The corresponding lubricating film knots modification of block is composed for accelerating load.
The advantages and positive effects of the present invention are：
It (1), being capable of largely accelerating solid lubrication bearing event in the case where conventional life test loading spectrum determines
Barrier process, quickening obtain the speed of Test to Failure sample；
(2) the loading spectrum design method based on spectrum block-grading and equivalent damage is provided, can preferably reflect that solid moistens
The actual motion load section of plain besring；
(3) when designing bearing with solid lubricant accelerated life test loading spectrum, the amplitude by adjusting stress and time protect
Card does not change the failure mechanism of bearing with solid lubricant.
Description of the drawings
Fig. 1 is the structure and lubrication film transfer schematic diagram of bearing with solid lubricant；
Fig. 2 is bearing with solid lubricant accelerated life test loading spectrum design method；
Fig. 3 is the derivation of bearing with solid lubricant dynamic complex wear law；
Fig. 4 is the Elliptical Contacts region of rolling element and raceway groove.
Wherein attached drawing is schematically illustrated to present disclosure, not uses content shown in the drawings to the present invention
Content specifically limited.
Specific implementation mode
Below in conjunction with the accompanying drawings and embodiment is to bearing with solid lubricant accelerated life test loading spectrum design side of the invention
Method is described in detail.
Fig. 1 is the schematic diagram of bearing with solid lubricant, bearing with solid lubricant generally use bearing internal external circle, retainer and rolling
The structure type that body is combined.Wherein 1 is outer ring, and 2 be inner ring, and 3 be retainer, and 4 be the outer ring lubricating film on outer ring 1, and 5 be interior
Inner ring lubricating film on circle 2,6 be rolling element.Outer ring is held generally stationary, and inner ring usually rotates with the axis, two in practical application
The movement relation of person can also need to change, you can it is fixed with inner ring 2, and outer ring 1 rotates.When between inner ring 1 and outer ring 2
When relative motion occurs, rolling element 6 rotates.Outer ring lubricating film 4 is located in the raceway groove on 1 inner surface of outer ring, and inner ring lubricating film 5 is then
In the raceway groove on 2 outer surface of inner ring.The most popular material of lubricating film is molybdenum disulfide.Plated film may be used in lubricating film
Mode prepare.Retainer 3 is the retainer of a kind of self-lubricating function, is made of " expendable " lubriation material, most frequently
The material used is PI (polyimides) and MoS2.In bearing with solid lubricant operation process, raceway groove plated film plays lubricating action；And
Retainer is then designed to controllable speed and mode and the lubriation material of itself is transferred in interior outer raceway groove through rolling element rotation,
Play the role of supplementing the loss of lubricating film, to keep lubricant effect.
As shown in Fig. 2, the method for carrying out accelerated life test loading spectrum design is as follows：
Step 1: obtaining the operation on orbit section of bearing with solid lubricant.In start of run, the mainly ditch of lubricating action is played
Road plated film.Contact with the rotation and rolling element of rolling element with retainer and mutually collision, the lubriation material of retainer are logical
The rotation for crossing rolling element is constantly shifted on raceway groove, and in the process, raceway groove plated film gradually wears out and consumes, and raceway groove plated film is gradual
Transition is transfer lubrication, and final transfer membrane plays primary lubricant, as shown in Figure 1.It is all consumed to raceway groove plated film and transfer membrane
After, bearing is gradually worn out until failure.During real-world operation, it is also possible to the too fast feelings of lubriation material transfer velocity occur
Condition causes lubriation material to be accumulated in interior outer raceway groove.It causes moment of friction excessive, make bearing stall or is difficult to smooth working, into
And cause to fail.Therefore, it is necessary to further investigate the abrasion of lubricating film and metastatic rule in bearing with solid lubricant, plated film is provided respectively
The relationship of wear rate and retainer lubriation material transfer rate and applied stress obtains bearing with solid lubricant dynamic complex abrasion rule
Rule, in order to the design of follow-up accelerated life test loading spectrum.
The derivation of bearing with solid lubricant dynamic complex wear law is as shown in Figure 3.For raceway groove plated film rate of depreciation,
Speed and time are introduced to characterize sliding distance, obtaining wear extent formula is：
Wherein W1For raceway groove plated film wear extent, p1For pressure, v1For sliding speed, t is test period, K1, a, b, c be all
The constant determined based on statistical data.
Rolling element belongs to point contact with the contact of interior outer raceway groove.According to Hertz contact theories, can by force analysis and
The external load (i.e. accelerated stress) applied obtains the stress distribution of contact zone.It is based on macroscopical theory of wear again, can pass through
Statistical data fits the relationship between raceway groove plated film wear rate and accelerated stress.In view of bearing with solid lubricant commonly adds
Fast stress is rotating speed and axial load, this relationship can be characterized as：
Ioff=F1(V,P) (8)
Wherein IoffIndicate that raceway groove plated film wear rate, V and P indicate the amplitude of rotating speed and axial load stress respectively.
The transfer rate of retainer lubriation material can equally be obtained based on tribology method.Polishing scratch based on retainer
Recessed is in paraboloid shape, provides the expression formula of retainer lubricating film transfer amount：
Wherein W2For retainer lubricating film transfer amount, p2For average Hertz contact forces, D=v2T is sliding distance, K2、j、m
For the constant determined based on statistical data, v2For relative sliding velocity.It is same to be managed based on macroscopical theory of wear and Hertz contacts
By.Using the methods of finite element analysis, the relationship that can be maintained between frame lubriation material transfer rate and accelerated stress, table
Sign is：
Ibr=F2(V,P) (10)
Wherein IbrIndicate retainer lubriation material transfer rate.In conjunction with actual load history, (8) formula of being based on can be divided into
(10) the lubrication membrane volume W of attrition in interior outer raceway groove is calculated in formulaoff(t) and retainer is through the inside outer fissure of rolling element
The lubrication membrane volume W shifted on roadbr(t), and then the Expression formula of lubrication film thickness under different stress can be provided：
Wherein δ is lubrication film thickness, δ0For raceway groove plated film original depth, A is raceway groove plated film area.Above-mentioned lubrication film thickness
Expression formula i.e. characterize bearing with solid lubricant dynamic complex abrasion.It is obtained according to Dynamic wear rule and based on statistical data
Fault threshold can obtain the physical essence and coupled relation of bearing with solid lubricant failure mechanism under different stress levels, be it
The design of accelerated life test loading spectrum lays the foundation.
Step 2: converting obtained loading spectrum block to loads typical composes block.Because bearing with solid lubricant commonly accelerates
There are two stress --- rotating speed and axial load, and practical in-orbit bearing with solid lubricant may bear increasingly complex stage
Loading spectrum, so, loads typical spectrum block can be converted by directly intercepting the loading spectrum that will be obtained.
Step 3: according to the failure mechanism of bearing with solid lubricant and Dynamic wear rule, level Four, I are divided into loading spectrum block
Grade indicates that retainer transfer rate is too fast, and bearing with solid lubricant will be formed in interior outer raceway groove quickly under such stress level
Lubricating film is measured, stall is caused and is quickly invalidated.This kind of loading spectrum block generally will not in practice occur in engineering, or entirely carry
Shared ratio very little in lotus spectrum, but bearing fault can be caused quickly, thus belong to the loading spectrum block for changing failure mechanism,
Loading spectrum should give reservation when working out.II grades indicate that retainer transfer rate is higher than raceway groove plated film wear rate, but not short
Cause lubricating film excessive in time, it is bigger than normal to be often reflected as moment of friction in practice in engineering, causes to fail after extended periods.
III level indicates that retainer transfer rate is less than raceway groove plated film wear rate, thus bearing can gradually consume raceway groove plated film and transfer
Film finally causes to fail because lubricating film lacks.IV grades indicate retainer transfer rate and raceway groove plated film wear rate all very
Slowly, in such cases, bearing lubrication film thickness is kept approximately constant, thus such loading spectrum block is to the performance of bearing with solid lubricant
It degenerates and the influence in service life can almost be ignored；For bearing with solid lubricant in orbit, such load occupies significant proportion,
It usually can be omitted when loading spectrum is worked out.
To above II grades and III level loading spectrum block, the shape that generally use merges when working out accelerated life test loading spectrum
Formula.For bearing with solid lubricant, combined principle is equivalent damage principle (i.e. equivalent lubrication film thickness knots modification).II grades of loads
It is transfer membrane excess failure that it is corresponding, which to compose block, for lotus, and corresponding lubrication film thickness increases, and combination principle is：
Wherein N is the number of II grades of loading spectrum blocks, △ δiChange for total lubricating film corresponding to i-th of II grades of loading spectrum block
Variable, △ δAThe corresponding lubricating film knots modification of block is composed for accelerating load.According to the △ δ being calculatedA, it can be based on formula (11), adopted
Calculate the value of accelerated stress V and P with optimization method, when practical operation also needs to consider engineering realizability.
Corresponding III level loading spectrum block is lubricating film miss fault, and corresponding lubrication film thickness reduces, combination principle with II grades
Loading spectrum block is identical.
Example：
It is as follows to certain spaceborne bearing with solid lubricant accelerated life test loading spectrum design using the method for the present invention：
The working environment of analysis bearing with solid lubricant and the stress born first, and carry out the selection of accelerated stress.Gu
It is a kind of spaceborne transmission component of basic space flight that body, which lubricates bearing, is widely used in each quasi-instrument and mechanism of spacecraft.
The environmental stress that bearing with solid lubricant is born mainly has temperature, radiation etc., working stress mainly to have rotating speed, radial load, axial direction
Load etc..
In real work, bearing with solid lubricant failure is mostly caused by insufficient lubrication or abrasion.Solid lubricant film is gradually worn out
Consumption, destruction of lubricating film and cause bearing moment increase or vibration increase, eventually lead to failure.Carry out bearing with solid lubricant acceleration
When life test, mainly select rotating speed and axial load as accelerated stress.
Table 1 gives certain spaceborne bearing with solid lubricant in-orbit load history, and each experience total time in period is 11min.
Load history shown in table 1 is divided into 6 stages, respectively corresponding corresponding in-orbit operating mode, i.e., low speed rotates in the forward direction, low-speed reverse is revolved
Turn, high-speed forward rotation, high-speed reverse rotation etc. the stages.Because there are two the common accelerated stress of bearing with solid lubricant, will
To loading spectrum block be converted into loads typical compose block.It, can be with according to the failure mechanism of bearing with solid lubricant and Dynamic wear rule
Its loading spectrum block is divided into level Four, composes block wherein the 1-5 stages in table 1 can be intercepted for II grades and III level, the 6th stage was I grades of spectrums
Block.
The in-orbit load history of certain the spaceborne bearing with solid lubricant of table 1
Spacecraft mechanism bearing with solid lubricant is generally operational under underloading speed operation.And for rolling body bearing, often apply
Add certain axial pretightening load to improve the rigidity and running accuracy of bearing.It calculates for simplifying the analysis, does following two herein
Point is assumed：
1) under speed operation, inertial load is ignored caused by rolling element movement.
2) under space microgravity environment, rolling body bearing is subjected only to prefastening load.
When bearing bears central axial prefastening load Fa, the contact load Q of each rolling element is identical, i.e.,
In formula, Z is the number of rolling element, and α is bearing the actual contact angle.It is theoretical according to point contact Hertz, according to point contact
The contact zone of Hertz theory, rolling element and interior outer raceway groove is ellipse.Establish coordinate system s={ o, x y z }, the origin o of coordinate system s
It is located at elliptical center, x-axis is directed toward the rotating direction of rolling element along ellipse short shaft along transverse direction, y-axis, and z-axis is along contact surface
Normal direction, as shown in figure 4, the contact force at elliptical contact any point (x, y) is：
In formula, p0For the Max.contact stress of elliptical contact, a, b are respectively elliptical long and short semiaxis according to maximum
The calculation formula of Hertz contact stress, obtaining its Max.contact stress is：
π e in formulaaebFor constant, Hertz contact coefficient tables can be looked into and obtained, ∑ ρ2For the principal curvatures of contact object and this
In take εE=1.
The following is introduced to the motion analysis of rolling body bearing to assume:
1) bearing outer ring is fixed, inner ring rotates；
2) under speed operation, the contact angle of bearing internal external circle is identical, and does not consider the gyration of rolling element；
3) rolling element is only rolled in bearing outer ring channel, and has spin in the existing rolling of bear inner ring grooved railway.
4) rolling element and the relative sliding velocity v (x, y) of bear inner ring grooved railway are at this along ellipse at elliptical contact point (x, y)
The vector sum of the differential sliding speed v1 (x, y) and revolving sliding speed v2 (x, y) of circle short-axis direction, are shown in Fig. 4.
Sliding speed v (x, y) is at point (x, y)：
In formula, ω is the absolute angular velocities of bearing inner race rotation；G (x, y) is elliptical contact x, the function of y, with bearing
Geometrical property, operating mode (load) etc. are related.
By formula (7) it is found that the line wear rate of rolling element and solid lubricant film at any point (x, y) in raceway groove elliptical contact
For：
As shown in figure 4, taking minute area unit dxdy at point (x, y).By formula (4) it is found that each rolling element and ditch stage property
There is identical contact, γ (x, y) is integrated in elliptical contact, the abrasion of bearing inner race raceway groove solid lubrication membrane volume can be obtained
Rate w is：
In formula, Ω is the elliptical contact of rolling element and bearing inner race raceway groove.Formula (14), (16) are substituted into formula (18) and obtained
It arrives：
A in formulai, biThe respectively semi-major axis and semi-minor axis of rolling element and bearing inner race raceway groove elliptical contact, subscript i tables
Show inner ring.
It enables
Parameter K3It is related with elliptical contact shape, bearing operating mode and bearing geometrical property etc..
At this point, formula (19) is represented by：
In the Volume erosion rate w for stablizing wear stage and being believed that solid lubricant film1It remains unchanged at any time.At this point, formula (7)
In parameter c=1, take K=K1K3=4.0 × 10-9.Bearing with solid lubricant wear out failure model under vacuum environment is verified, is needed
Testing data of life-span is obtained under vacuum environment, and obtains corresponding parameter K according to the testing data of life-span under vacuum environment1、K3、
A, the numerical values recited of b, since experiment condition is limited, the working condition of practical in-orbit bearing with solid lubricant is complex, Wu Fa
Ground obtains its accurate numerical values recited and takes a=0.127, b=1.3849 according to statistical data.It similarly, can be in the hope of retainer
Lubricating film transfer amount is represented by：
Ibid, K is taken2=1.2 × 10-8, j=0.103, m=1 then can be in the hope of：
In the loading spectrum block of II grades of correspondence and III level, the knots modification of the lubricating film of i-th of spectrum block is：
δi=W1-W2 (23)
Corresponding first five stage interception of table 1 is composed into block for II grades and III level,
Certain first five stage of spaceborne bearing with solid lubricant of table 2 intercepts
Therefore it can be obtained by above formula (21) (22) (23)：
δ1=2.5069 × 10-5-3.0930×10-5=-5.8610 × 10-6
δ3=4.4105 × 10-5-3.1727×10-5=1.2379 × 10-5
δ5=0.0011-5.9539 × 10-4=4.5549 × 10-4
According under the premise of not changing bearing with solid lubricant failure mechanism, according to actual condition, II and III level are composed into block
Merge, make it have acceleration effect as well as possible, we take axial load 20N, rotating speed 240rpm to merge as it herein
Operating mode afterwards then acquires the acceleration time according to formula (11) (21) (22)：
T=253.5394s=4.2257min
The time of experience a cycle can be equivalent to 5.2257min.Finally, the constant stress life testing spectrum of bearing with solid lubricant
As table 3 is shown as：
Certain the spaceborne bearing with solid lubricant constant stress life testing spectrum of table 3
By above-mentioned accelerated life test loading spectrum translation method, bearing with solid lubricant failure mechanism can not changed
Under the premise of, using the typical condition taken, the in-orbit load history of the bearing with solid lubricant in six stages originally is equivalent to
Two typical stages are stated, the total time used in each of which period has also been reduced to 5.2257min by original 11min, accelerates effect
Fruit is more apparent, the crashed process of accelerating solid lubrication bearing that can be largely, to obtain the effective acceleration longevity
Order test load spectrum.
Obviously, the above embodiment is merely an example for clearly illustrating the present invention, and is not to the present invention
The restriction of embodiment.For those of ordinary skill in the art, it can also be made on the basis of the above description
Its various forms of variation or variation.There is no necessity and possibility to exhaust all the enbodiments.And these belong to this hair
The obvious changes or variations that bright spirit is extended out are still in the protection scope of this invention.
Claims (4)
1. a kind of bearing with solid lubricant accelerated life test loading spectrum design method, which is characterized in that
Include the following steps：
1) the operation on orbit section of bearing with solid lubricant is obtained；By analyzing the abrasion of lubricating film in bearing with solid lubricant and turning
It moves, provides the relationship of plated film wear rate and retainer lubriation material transfer rate and applied stress respectively, obtain solid lubrication axis
Hold dynamic complex wear law；
2) it converts obtained loading spectrum block to loads typical and composes block；It is converted into allusion quotation by directly intercepting the loading spectrum block that will be obtained
Type loading spectrum block；
3) according to the failure mechanism of bearing with solid lubricant and dynamic complex wear law, loads typical spectrum block is classified
Processing.
2. according to the method described in claim 1, it is characterized in that, step 3) includes：
In the case of retainer transfer rate causes lubricating film excessive higher than raceway groove plated film rate of depreciation and/or retainer turns
The loading spectrum block that rate causes lubricating film to lack less than raceway groove plated film rate of depreciation is moved to merge.
3. according to the method described in claim 1, it is characterized in that, step 3) includes：
Bearing with solid lubricant dynamic complex wear law obtains in the following way：
For raceway groove plated film rate of depreciation, speed and time are introduced to characterize sliding distance, obtaining wear extent formula is：
Wherein W1For raceway groove plated film wear extent, p1For pressure, v1For sliding speed, t is test period, K1, a, b, c all be based on system
Count determining constant；
The relationship between raceway groove plated film rate of depreciation and accelerated stress is fitted by statistical data；In view of bearing with solid lubricant
Common accelerated stress is rotating speed and axial load, this relationship is characterized as：
Ioff=F1(V,P) (2)
Wherein IoffIndicate that raceway groove plated film rate of depreciation, V and P indicate the amplitude of rotating speed and axial load stress respectively；
The recessed of polishing scratch based on retainer is in paraboloid shape, the expression formula for the frame lubricating film transfer amount that is maintained：
Wherein W2For retainer lubricating film transfer amount, p2For mean Hertz contact force, D=v2T is sliding distance, K2, j, m be based on
The constant that statistical data determines, v2For relative sliding velocity；
Relationship between retainer lubriation material transfer rate and accelerated stress is：
Ibr=F2(V,P) (4)
Wherein IbrIndicate retainer lubriation material transfer rate；
The lubrication membrane volume W of attrition in interior outer raceway groove is obtained based on (2) formula and (4) formulaoff(t) and retainer is through rolling element
The lubrication membrane volume W shifted in inside outer raceway groovebr(t), to obtain the Expression formula of lubrication film thickness under different stress, i.e.,
Characterize bearing with solid lubricant dynamic complex wear law：
Wherein δ is lubrication film thickness, δ0For raceway groove plated film original depth, A is raceway groove plated film area.
4. according to the method described in claim 2, it is characterized in that, step 3) includes：
The expression formula of the merging is：
Wherein N is the number that loads typical composes block, Δ δiTotal lubricating film knots modification corresponding to block is composed for i-th of loads typical,
ΔδAThe corresponding lubricating film knots modification of block is composed for accelerating load.
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| CN201610696760.XA CN106248379B (en) | 2016-08-19 | 2016-08-19 | A kind of bearing with solid lubricant accelerated life test loading spectrum design method |
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| CN106885702B (en) * | 2017-01-24 | 2019-04-16 | 中车株洲电力机车研究所有限公司 | A kind of rail transit rolling stock equipment life appraisal procedure |
| CN107664575A (en) * | 2017-08-30 | 2018-02-06 | 中国科学院上海技术物理研究所 | A kind of life test method of spaceborne solid lubrication sweep mechanism complete machine |
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| CN111947950B (en) * | 2020-07-01 | 2022-03-08 | 北京工业大学 | Multi-dimensional comprehensive stress life test load spectrum design method based on load information matrix |
| CN111896255B (en) | 2020-08-12 | 2021-06-04 | 上海理工大学 | Method for rapidly evaluating service life of hub bearing based on multi-axis random road load |
| CN112557037B (en) * | 2020-11-30 | 2022-03-11 | 南京工业大学 | Accelerated life test method for wind power main shaft bearing model |
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| CN114297820A (en) * | 2021-11-26 | 2022-04-08 | 上海航天控制技术研究所 | Design method of bearing assembly with long space life |
| CN114509260B (en) * | 2021-11-29 | 2023-12-15 | 中国航发沈阳发动机研究所 | Acceleration equivalent test method for high-speed inner-outer ring co-rotating roller bearing of aero-engine |
| CN114509262B (en) * | 2022-01-25 | 2024-07-30 | 中国铁建重工集团股份有限公司 | Acceleration test method for main bearing of heading machine |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3436268C2 (en) * | 1984-10-03 | 1990-01-04 | Siemens Ag, 1000 Berlin Und 8000 Muenchen, De | |
| US5726905A (en) * | 1995-09-27 | 1998-03-10 | General Electric Company | Adaptive, on line, statistical method and apparatus for motor bearing fault detection by passive motor current monitoring |
| JP4003088B2 (en) * | 2006-12-20 | 2007-11-07 | 日本精工株式会社 | Rotating body abnormality diagnosis method and apparatus |
| JP4120099B2 (en) * | 1999-07-09 | 2008-07-16 | 日本精工株式会社 | Bearing abnormality diagnosis method and abnormality diagnosis device |
| CN101957261A (en) * | 2010-04-21 | 2011-01-26 | 中国人民解放军国防科学技术大学 | Antifriction bearing multi-functional fatigue life test bed |
| CN102494880A (en) * | 2011-11-24 | 2012-06-13 | 北京航空航天大学 | Design method for integrated stress, acceleration and service life testing profile of astronautic drive component |
| CN103674546A (en) * | 2012-09-06 | 2014-03-26 | 上海欧际柯特回转支承有限公司 | Accelerated fatigue life test method for wind power slewing bearing |
| EP2746541A3 (en) * | 2012-12-20 | 2016-04-20 | Doosan Skoda Power S.r.o. | A method of detecting and localizing partial rotor-stator rubbing during the operation of a turbine |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006313169A (en) * | 2000-12-06 | 2006-11-16 | Nsk Ltd | Abnormality diagnostic method and abnormality diagnostic device of machine or equipment |
| JP2004093357A (en) * | 2002-08-30 | 2004-03-25 | Nsk Ltd | Evaluation method and evaluation device |
-
2016
- 2016-08-19 CN CN201610696760.XA patent/CN106248379B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3436268C2 (en) * | 1984-10-03 | 1990-01-04 | Siemens Ag, 1000 Berlin Und 8000 Muenchen, De | |
| US5726905A (en) * | 1995-09-27 | 1998-03-10 | General Electric Company | Adaptive, on line, statistical method and apparatus for motor bearing fault detection by passive motor current monitoring |
| JP4120099B2 (en) * | 1999-07-09 | 2008-07-16 | 日本精工株式会社 | Bearing abnormality diagnosis method and abnormality diagnosis device |
| JP4003088B2 (en) * | 2006-12-20 | 2007-11-07 | 日本精工株式会社 | Rotating body abnormality diagnosis method and apparatus |
| CN101957261A (en) * | 2010-04-21 | 2011-01-26 | 中国人民解放军国防科学技术大学 | Antifriction bearing multi-functional fatigue life test bed |
| CN102494880A (en) * | 2011-11-24 | 2012-06-13 | 北京航空航天大学 | Design method for integrated stress, acceleration and service life testing profile of astronautic drive component |
| CN103674546A (en) * | 2012-09-06 | 2014-03-26 | 上海欧际柯特回转支承有限公司 | Accelerated fatigue life test method for wind power slewing bearing |
| EP2746541A3 (en) * | 2012-12-20 | 2016-04-20 | Doosan Skoda Power S.r.o. | A method of detecting and localizing partial rotor-stator rubbing during the operation of a turbine |
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