CN103837343B - Based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis - Google Patents
Based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis Download PDFInfo
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- CN103837343B CN103837343B CN201410103259.9A CN201410103259A CN103837343B CN 103837343 B CN103837343 B CN 103837343B CN 201410103259 A CN201410103259 A CN 201410103259A CN 103837343 B CN103837343 B CN 103837343B
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Abstract
The invention discloses a kind of ships and light boats axle system life-span prediction method based on vibrating fatigue coupling analysis, comprise and select Measuring Time point t
iand measure ships and light boats axle system and be in this Measuring Time point t
itime natural frequency ω
i(n time is measured, i=1,2,3 ..., n, i are positive integer), then calculate ships and light boats axle system and be in this Measuring Time point t
itime expection N fatigue lifetime
i, finally calculate ships and light boats axle system and be in this Measuring Time point t
itime residual life M
i.Instant invention overcomes now methodical shortcoming, from ships and light boats axle system model, based under vibration and tired coupling environment, ships and light boats axle system is calculated in the life-span, solve in prior art the problem not relating to and ships and light boats axle system is carried out to life-span calculating and prediction, the method easy to understand, easy realization, is more suitable for calculating and the prediction of ships and light boats axle system residual life.
Description
Technical field
The present invention relates to a kind of Life Calculating Methods, particularly relate to a kind of ships and light boats axle system life-span prediction method based on vibrating fatigue coupling analysis, belong to ships and light boats field of power equipment technology.
Background technology
Under sail, the vibration of axle system is one of key factor affecting the safe operation of ships and light boats propulsion system to ships and light boats, if can not get effective control, by a series of serious consequence of appearance, as the fracture etc. of axle system.Correct evaluation is made in vibration in order to shaft, avoids the generation of malicious event, not only should carry out detailed vibration calculating in the design phase, also needs to carry out vibration-testing in the operation phase, to investigate this propulsion system vibration characteristics whether reach required standard.Existing Many researchers has carried out deep discussion and analysis to the theory calculate of vibration and test both at home and abroad.
But for the life prediction of ships and light boats axle system, existing method then seldom relates to.Wherein main cause is: one is current check standard, and normally being derived by the fatigue strength of this axle as permissible stress draws, as long as meet standard, usually just thinks that this axle cording has infinite life, obviously, this inadequate science, not pointed yet; Two is that shaft is carried out life prediction itself and had certain complicacy because the environment residing for axle system.Under the effect of dynamic loading, ships and light boats axle system can vibrate, and vibration can produce alterante stress, if under being in alterante stress environment for a long time, structure fatigue damage can occur; In addition, the existence of fatigue damage reduces the rigidity of structure, reduces the natural frequency of structure, have impact on the vibration characteristics of structure.So axle system is in vibration with under the tired environment that is coupled.How to predict the life-span of ships and light boats axle system, answer the problem of " how long can also use ", depend on effective vibrating fatigue model of coupling to a great extent.
The existing pertinent literature about vibrating fatigue coupling analysis, from application, all there is specific suitable environment, such as tack-weld, plate etc., dynamic perfromance Changing Pattern in document all sets off a discussion based on these models, thus is not suitable for vibrating shaft system life prediction here; From damage type, be confined to crackle, the main theory of life prediction in document is according to the defect theory being fracturing mechanics Crack Extension, and with regard to ships and light boats axle system, as long as there is crackle, just must take measures in time, so fatigue lifetime refers to crack initiation life, main theory is according to being classical fatigue cumulative damage theory.
Summary of the invention
Object of the present invention, is to carry out on the basis of vibrating fatigue coupling analysis to ships and light boats axle system, provides a kind of ships and light boats axle system Life Calculating Methods.
To achieve these goals, the technical solution adopted in the present invention is as follows:
Based on a ships and light boats axle system life-span prediction method for vibrating fatigue coupling analysis, comprise and select Measuring Time point t
iand measure ships and light boats axle system and be in this Measuring Time point t
itime natural frequency ω
i, n time is measured, i=1,2,3 ..., n, i are positive integer, then calculate ships and light boats axle system and be in this Measuring Time point t
itime expection N fatigue lifetime
i, finally calculate ships and light boats axle system and be in this Measuring Time point t
itime residual life M
i, described ships and light boats axle system residual life M
icomputing method be:
Situation 1: ω
0during < ω, M
i=N
0-N
α;
Situation 2: ω
0> > ω, and ω
nduring > ω,
Situation 3: ω
0> ω
1> ... > ω
j-1> ω > ω
j> ... > ω
ntime, make D
*=max (1/N
j-1, 1/N
j),
Wherein: ω is the sinusoidal interference moment frequency of ships and light boats axle system, N
0for natural frequency ω when ships and light boats axle system does not use
0corresponding expection fatigue lifetime, N
αthe stress-number of cycles that when being i-th prediction, ships and light boats axle system has used, N
pbe the p time Measuring Time point t
pthe ships and light boats axle system expection fatigue lifetime of calculating, N
j-1for natural frequency ω when ships and light boats axle system is in jth-1 Measuring Time point
j-1corresponding expection fatigue lifetime, N
jfor natural frequency ω when ships and light boats axle system is in jth time Measuring Time point
jcorresponding expection fatigue lifetime, M
jfor the ships and light boats axle system residual life calculated when jth time is measured, N
βfor the stress-number of cycles that ships and light boats axle system when measuring to i-th time after jth time measurement has used.
Preferably, described selection Measuring Time point t
imethod be, residual life M when selecting ships and light boats axles system not use
01/2 place as first time Measuring Time point (obvious M
0=N
0), i.e. t
1=M
0/ 2, thereafter, 1/2 place of the residual life of prediction after each Measuring Time point is selected in and measures for last time, i.e. t
2=M
1/ 2 ..., t
n=M
n-1/ 2, wherein M
1, M
2..., M
n-1for Measuring Time point t
1, t
2..., t
n-1corresponding residual life.
Preferably, described expection N fatigue lifetime
icomputing formula be N
i=C (W
p/ T
0)
mμ
i -m, wherein: μ
ifor ships and light boats natural frequency of shafting ω
icorresponding vibration amplification factor, m, C are two material constants of the ships and light boats axle system curve of fatigue, W
pfor the torsion section factor of ships and light boats axle system, T
0for the amplitude of ships and light boats axle system periodic disturbing torque.
Preferably, described ships and light boats natural frequency of shafting ω
icorresponding vibration amplification factor μ
icomputing formula be
Wherein: ξ is the damping ratio of ships and light boats axle system.
After adopting such scheme, ships and light boats axle system life-span prediction method based on vibrating fatigue coupling analysis of the present invention, its beneficial effect is: instant invention overcomes now methodical shortcoming, from ships and light boats axle system model, based under vibration and tired coupling environment, ships and light boats axle system is calculated in the life-span, solve in prior art the problem not relating to and ships and light boats axle system is carried out to life-span calculating and prediction, the method easy to understand, easy realization, is more suitable for calculating and the prediction of ships and light boats axle system residual life.
Accompanying drawing explanation
Fig. 1 is ships and light boats axle system simple substance amount torsional vibration system schematic diagram in the embodiment of the present invention.
Fig. 2 is ships and light boats axle system of the present invention
graph of relation.
Fig. 3 is " residual life-natural frequency " i.e. M in the embodiment of the present invention
i-ω
igraph of relation.
Embodiment
Below in conjunction with accompanying drawing, technical scheme of the present invention is described in further detail.
Based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis, comprise the following steps:
1, the natural frequency of ships and light boats axle system is measured at specific Measuring Time point
Cause is in the early stage of fatigue lifetime, and natural frequency reduces smaller, and to the later stage of fatigue lifetime, natural frequency reduces very fast, and more and more faster, is namely nonlinear, so there is ω
0> ω
1> ... > ω
n.For this reason, following natural frequency measurement, method is provided: each Measuring Time point is selected in 1/2 place of the residual life calculated when measuring for last time.
Suppose that measuring corresponding residual life through n time is followed successively by: M
1, M
2..., M
n, natural frequency when ships and light boats axle system does not use is ω
0, and the residual life M of correspondence
0=N
0(N
0expection fatigue lifetime for when ships and light boats axle system does not use).1st time Measuring Time point exists: t
1=M
0/ 2 places; Thereafter, the time interval that each natural frequency Measuring Time point experiences relative to last Measuring Time point is expressed as successively: t
2, t
3..., t
n.So:
t
1=M
0/2,t
2=M
1/2,…,t
n=M
n-1/2。(1)
If the large, medium and small phase lead time of repairing of certain Measuring Time point and ships and light boats axle system is little, this Measuring Time point can be arranged in and large, medium and smallly repaiies the phase; If certain Measuring Time point once does not also arrive, but because task needs, current Measuring Time point also can be artificially given.
2, the expection fatigue lifetime of ships and light boats axle system is calculated
The vibration of ships and light boats axle system is rather complicated, from the form of vibration, can be divided into extensional vibration, whirling vibration and twisting vibration; From analytical model, single-degree-of-freedom, multiple degrees of freedom and continuous system model can be divided into.The present invention discusses for shafting torsional oscillation single-mode system, and (i.e. single quality system, only consider the quality of screw propeller, other quality are not considered, suppose that main frame rigidity is very large, quality is infinitely great simultaneously.For other system, method is similar).As shown in Figure 1, be the simple substance amount torsional vibration system schematic diagram in the embodiment of the present invention, wherein K
0for torsional rigidity when ships and light boats axle system does not use, W
pfor the torsion section factor of ships and light boats axle system, ξ is the damping ratio of ships and light boats axle system, and ω is the sinusoidal interference moment frequency of ships and light boats axle system, and I is the moment of inertia of screw propeller, acts on the periodic disturbing torque T=T that ships and light boats axle is fastened
0e
j ω t, T
0for the amplitude of ships and light boats axle system periodic disturbing torque, the vibration amplification factor can trying to achieve ships and light boats axle system is:
Wherein, ω
0for natural frequency when ships and light boats axle system does not use,
Maximum stress in ships and light boats axle system one-period can try to achieve into:
suppose that ships and light boats axle system Fatigue Property Curve meets:
wherein, N is expection fatigue lifetime, and m, C are two material constants of the ships and light boats axle system curve of fatigue, relevant with axle based material character etc., τ
maxfor the maximum stress that ships and light boats axle system bears, then expection is fatigue lifetime:
Utilize Miner linear progressive damage theory to calculate accumulative fatigue damage, after the circulation of experience primary stress, to the single damage that ships and light boats axle system causes be:
D=1/N。(4)
Suppose that ships and light boats axle system measures through i time the natural frequency obtained and is followed successively by ω
1, ω
2..., ω
n, because natural frequency reduces gradually, have ω
1> ω
2> ... > ω
n, corresponding expection is followed successively by N fatigue lifetime
1, N
2..., N
n, corresponding single damage is followed successively by D
1, D
2..., D
n.By (3) Shi Ke get, natural frequency ω when ships and light boats axle system does not use
0corresponding expection fatigue lifetime is N
0, by (4) Shi Ke get, corresponding single damage is D
0.
The natural frequency ω obtained is measured to i-th time
i, with ω
inatural frequency ω when replacing ships and light boats axle system not use
0, tried to achieve by (2), (3), (4) formula, ω
iunder amplification factor μ
i, expection fatigue lifetime N
iand single damage D
i.Draw
relation curve as shown in Figure 2.
3, the residual life of ships and light boats axle system is calculated
Based on the principle of security, point residual life of three kinds of situations to ships and light boats axle system calculates.
Situation 1: work as ω
0during < ω, ω > ω
0> ω
1> ω
2> ... > ω
n, therefore D
0> D
1> D
2> ... > D
n.
Get D
0for the fatigue damage that each Cyclic Stress is brought, expection N fatigue lifetime of ships and light boats axle system
0obtained by (3) formula.Now, do not need to arrange natural frequency measurement, re-use N
αresidual life after secondary is measurable is:
M
i=N
0-N
α,i=1,2,3,…,n,(5)
N
αthe stress-number of cycles that when being i-th prediction, ships and light boats axle system has used.
Situation 2: work as ω
0during > > ω, can imagine and work as ω
n> ω, so: D
0< D
1< D
2< ... < D
n.The residual life of prediction is:
Wherein: t
1, t
2..., t
nvalue calculates according to formula (1).Note, as wherein certain Measuring Time point is artificially given once or several times, then replace with set-point.
Situation 3: work as ω
0during > ω, ω may be had
i< ω.From the angle avoiding resonating, this kind of situation should be avoided as far as possible.The mode improving ω can be taked, make ω
0< ω, now becomes situation 1; Also can reduce ω, make ω
n> ω, now becomes situation 2.Certainly, also can improve ships and light boats shafting structure and then change ω
0, make it become situation 1 or 2.But in some occasion, if above-mentioned measure all cannot be carried out, quickly through resonance region, can be handled as follows: suppose now have ω
0> ω
1> ... > ω
j-1> w > w
j> ... > ω
n, and D
*=max (1/N
j-1, 1/N
j), the residual life of prediction is:
Wherein: t
1, t
2..., t
jvalue still according to formula (1) calculate, as wherein certain Measuring Time point is artificially given once or several times, then replace with set-point.After secondary from jth, do not need to arrange natural frequency measurement, re-use N
βresidual life after secondary:
M
i=M
j-N
β,i=j+1,…,n(8)
N
βfor the stress-number of cycles that ships and light boats axle system when predicting to i-th time after jth time measurement has used.
After the residual life of the natural frequency and correspondence that draw each Measuring Time point, " residual life-natural frequency " i.e. M can be drawn
i-ω
irelation curve, draws the residual life under arbitrary natural frequency, as shown in Figure 3, is the M of embodiment below
i-ω
igraph of relation.
Embodiment
1, embodiment explanation
Certain ships and light boats two stroke diesel engine screw propeller can be simulated with simple substance amount torsional vibration system, as shown in Figure 1.Torsional oscillation stiffness K when this axle does not use
0=94.336MNm/rad, reverses section factor W
p=0.0260m
3, damping ratio ξ=0.1 of this axle, the moment of inertia I=31420Kgm of screw propeller
3, act on periodic disturbing torque T=167.428sin12.4tKNm (the i.e. periodic disturbing torque amplitude T on this axle
0=167.428KNm).
This axle Fatigue Property Curve meets:
i.e. C=10
11, m=0.75.Diesel engine is two-stroke, and a Cyclic Stress turns around, so this diesel engine speed is
1 hour number of stress cycles is n
r60=118.460=7104 secondary, for clarity, hereinafter the unit in life-span is all converted into hour.
2, result of calculation
Natural frequency when this axle does not use is
must expection N fatigue lifetime of this axle by formula (3)
0=18839 hours.
The sinusoidal interference moment frequencies omega of this axle=12.4rad/s, ω
0> 4 ω, meet the situation 2 in " the 3rd step calculates residual life ", technician has arranged natural frequency measurement, according to preceding method, and has carried out life-span calculating.
Residual life M when not using
0=N
0, then have: M
0=18839 hours.
By formula (1): the 1st time Measuring Time point exists: t
1=M
0/ 2=9419 hour.
Measure to obtain ω 1st time
1=52.7rad/s, with ω
1replace natural frequency ω when not using
0, substituting into formula (3) must expect fatigue lifetime: N
1=18779 hours.
By formula (6): residual life
Hour.
By formula (1): the 2nd time Measuring Time point exists: t
2=M
1/ 2=4680 hour.
Measure to obtain ω 2nd time
2=50.3rad/s, with ω
2replace natural frequency ω when not using
0, substituting into formula (3) must expect fatigue lifetime: N
2=18700 hours.
By formula (6): residual life
hour.
By formula (1): the 3rd time Measuring Time point exists: t
3=M
2/ 2=2320 hour.
……
The like, arrange 4 natural frequency measurement,s.After the 4th is measured, ships and light boats have worked again 200 hours, although be less than due Measuring Time point, because task needs, have organized a natural frequency measurement, on request.5 times measurement result is as shown in the table.Now wonder how long this axle can also work, the navigation in 300 hours can finishing the work required.
Table natural frequency is measured and residual Life Calculation result
Number of times | 0 | 1 | 2 | 3 | 4 | 5 |
Interval (unit: hour) | 0 | 9419 | 4680 | 2320 | 1132 | 200 |
Natural frequency (unit: rad/s) | 54.8 | 52.7 | 50.3 | 45 | 42.8 | 41.5 |
Residual life (unit: hour) | 18839 | 9360 | 4640 | 2265 | 1118 | 913 |
Residual life-natural frequency and M
i-ω
icurve as shown in Figure 3.For clarity, test interval and residual life are also listed in table.After visible the 5th is measured, residual life is 913 hours, is greater than 300 hours, the 300 hours navigational duties namely can finishing the work required.
Above embodiment is only and technological thought of the present invention is described, can not limit protection scope of the present invention with this, and every technological thought proposed according to the present invention, any change that technical scheme basis is done, all falls within scope.
Claims (4)
1., based on a ships and light boats axle system life-span prediction method for vibrating fatigue coupling analysis, comprise and select Measuring Time point t
iand measure ships and light boats axle system and be in this Measuring Time point t
itime natural frequency ω
i, n time is measured, i=1,2,3 ..., n, i are positive integer, then calculate ships and light boats axle system and be in this Measuring Time point t
itime expection N fatigue lifetime
i, finally calculate ships and light boats axle system and be in this Measuring Time point t
itime residual life M
i, it is characterized in that: described ships and light boats axle system residual life M
icomputing method be:
Situation 1: ω
0during < ω, M
i=N
0-N
α;
Situation 2: ω
0> > ω, and ω
nduring > ω,
Situation 3: ω
0> ω
1> ... > ω
j-1> ω > ω
j> ... > ω
ntime, make D
*=max (1/N
j-1, 1/N
j),
Wherein: ω is the sinusoidal interference moment frequency of ships and light boats axle system, N
0for natural frequency ω when ships and light boats axle system does not use
0corresponding expection fatigue lifetime, N
αthe stress-number of cycles that when being i-th prediction, ships and light boats axle system has used, N
pbe the p time Measuring Time point t
pthe ships and light boats axle system expection fatigue lifetime of calculating, N
j-1for natural frequency ω when ships and light boats axle system is in jth-1 Measuring Time point
j-1corresponding expection fatigue lifetime, N
jfor natural frequency ω when ships and light boats axle system is in jth time Measuring Time point
jcorresponding expection fatigue lifetime, M
jfor the ships and light boats axle system residual life calculated when jth time is measured, N
βfor the stress-number of cycles that ships and light boats axle system when measuring to i-th time after jth time measurement has used.
2. as claimed in claim 1 based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis, it is characterized in that: described selection Measuring Time point t
imethod be, residual life M when selecting ships and light boats axles system not use
01/2 place as first time Measuring Time point, i.e. t
1=M
0/ 2, thereafter, 1/2 place of the residual life of prediction after each Measuring Time point is selected in and measures for last time, i.e. t
2=M
1/ 2 ..., t
n=M
n-1/ 2, wherein M
1, M
2..., M
n-1for Measuring Time point t
1, t
2..., t
n-1corresponding residual life.
3., as claimed in claim 1 based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis, it is characterized in that: described expection N fatigue lifetime
icomputing formula be N
i=C (W
p/ T
0)
mμ
i -m, wherein: μ
ifor ships and light boats natural frequency of shafting ω
icorresponding vibration amplification factor, m, C are two material constants of the ships and light boats axle system curve of fatigue, W
pfor the torsion section factor of ships and light boats axle system, T
0for the amplitude of ships and light boats axle system periodic disturbing torque.
4., as claimed in claim 3 based on the ships and light boats axle system life-span prediction method of vibrating fatigue coupling analysis, it is characterized in that: described ships and light boats natural frequency of shafting ω
icorresponding vibration amplification factor μ
icomputing formula be
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CN112623143B (en) * | 2020-12-25 | 2021-12-21 | 江苏集萃复合材料装备研究所有限公司 | Ship dynamic shafting torsional vibration fatigue parameter fitting method based on dynamics |
CN114264466B (en) * | 2021-12-23 | 2024-03-19 | 潍柴动力股份有限公司 | Method and device for predicting service life of shock absorber |
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CN201199195Y (en) * | 2008-02-29 | 2009-02-25 | 西安交通大学 | Simulated experiment bench for multi-fault coupling gear case |
CN103076400A (en) * | 2012-10-23 | 2013-05-01 | 中国石油化工股份有限公司 | Novel corrosion probe based on vibration frequency and measurement system thereof |
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CF01 | Termination of patent right due to non-payment of annual fee |