CN108416159A - A kind of naval vessel shafting optimization method and its Optimization Platform - Google Patents
A kind of naval vessel shafting optimization method and its Optimization Platform Download PDFInfo
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Abstract
The invention belongs to ship design field more particularly to a kind of naval vessel shafting optimization method and its Optimization Platforms.This method improves the designing quality of shafting, and in the initial design phase, the position by optimizing each bearing of shafting achievees the purpose that promote centering of shafting quality and reduces shafting vibration.For warship safety, steadily operation provides basis.For shafting, the design phase in school controls its vibration characteristics and provides a new departure present invention, has important theory and engineering practice value, can fill up the deficiency of prior art, improve the designing quality of various types of naval vessel shafting.
Description
Technical field
The invention belongs to ship design field more particularly to a kind of naval vessel shafting optimization method and its Optimization Platforms.
Background technology
Naval vessel shafting is to influence the important feature of Ship Motion performance.The basic role of shafting is transmission power, including will
The power transfer that the equipment such as main motor are sent out to propeller to drive propeller to rotate, and by propeller rotation generate thrust
Or pulling force is transferred to ship shell to drive moving forward and backward for hull in the form of bearing.
Due to naval vessel itself stress complexity, while navigation channel and hydrographic data are changeable, and naval vessel and its shafting are being navigated by water
A variety of different loads can be born in the process, while these load can also interact between each other, these load finally will be direct
The each bearing being transferred in shafting improves naval vessel shafting performance to improve the stress of bearing, needs shaft to carry out rational
In school, the problems such as preventing each bearing from generating abnormal load, abrasion deformation, influences the safe and reliable of naval vessel operation.Existing optimization is set
The emphasis and appraisal of meter method are different, commonly using sides such as frequency modulation method, the excitation of reduction vibration source and vibration isolation
Method realizes the vibration and noise reducing of shafting, but its effect is general, is shaken to bearing convolution using numerical operation technique study axis rigidity
The method of dynamic influence but since such method ignores the difference between bearing horizontal rigidity and vertical rigidity, shafting is returned
There are difference with actual value for result of calculation of the rotation vibration in horizontal and vertical direction.
Invention content
The purpose of the invention is, one is provided to promote naval vessel shafting alignment quality and reducing its whirling vibration characteristic
Plant easy and effective optimum design method.
The present invention is based on the bases for studying for a long period of time and analyzing to Ship Motion performance and naval vessel shafting actual working state
On plinth, it is found that the factor for influencing naval vessel shafting performance, including the factor of influence centering of shafting quality, influence shafting vibration are not only wrapped
Include shafting and bearing own material and architectural characteristic and external impact, load factor, the also position with each bearing in shafting
It is interrelated, meanwhile, optimization is with non-while the position of each bearing conjugates shaft alignment quality and reduces shafting vibration
Obvious effect is especially limited by existing shafting design thinking and method, and existing design or optimization method can not
The influence factor is carried out in design effectively and optimization, especially short axle system design process, due to only considering in straight line school, directly
Have ignored the influence to the influence factor shaft performance.
Because of the present circumstance and the gist of the invention, the application acquire in the principle and method in existing research straight line school
Its loading effects coefficient；The minimum direct target of load on later stern bearing, the measurable data of visual result show in high-ranking officers,
To improve design optimization efficiency；By reasonably being conjugated in range in bearing, stern bearing vertical direction is with one step after adjustment
It is conjugated, whirling vibration characteristic of the shafting Optimization Platform in different schools under state is calculated, further according to centering of shafting quality
With the weight coefficient of whirling vibration, preferably suitable bearing displacement data are to obtain optimal centering of shafting and convolution vibration damping knot
Fruit.
To achieve the above object, the invention adopts the following technical scheme that.
A kind of naval vessel centering of shafting optimization method, includes the following steps：
Step 1: obtaining the structural parameters and material parameter of naval vessel shafting to be optimized, including each axis in naval vessel shafting
The geometric parameter of section and the Support Position of material properties, each bearing, the axial and vertical support stiffness of each bearing, the ruler of axis
Very little, the material properties include elasticity modulus and Poisson's ratio, and the Support Position includes axial position and vertical position；
Step 2: establishing the finite element model of the naval vessel shafting based on above structure parameter and material parameter；Foundation has
Institute is limited in meta-model at any beam element K node by shearing vectorial { Q } and deformation vectors { δ },
And the stiffness matrix of K node unit
Wherein
The elasticity modulus of E --- material；
The shearing elasticity model of G --- material；
The moment of inertia of I --- the unit to X-axis；
The cross-sectional area of S --- unit；
L --- element length；
yj--- the change place value (mm) of j-th of bearing.
I, j --- bearing number is indicated respectively；
According to above-mentioned formula, the stiffness matrix of each beam element in finite element model is acquired, by the stiffness matrix of each unit
It reconfigures to obtain the stiffness matrix K of the naval vessel shafting；
Step 3: adjusting the offset Y of the vertical position of each bearing on naval vessel stern tube shaft0, ignore the support of bearing lubrication oil film
Stiffness variation is located at tolerance zone, the minimum restrictive condition of load difference on adjacent bearing, later stern tube shaft with load on each bearing
Load R on bearing1Minimum object function solves the optimized migration amount for obtaining each bearing of vertical position；Each bearing displacement of shafting
Load R on each bearing afterwardsiIt is represented by：
In formula：R0i--- the load (kn) in shafting straight line school under state on each bearing；Wherein Ti, Tj--- node i, j
On shearing；Mi, Mj--- the moment of flexure in node i, j；yi, yj--- node i, j along Y-axis (vertical direction) displacement；θi,
θj--- node i, j around X-axis (axial direction) corner；
Step 4: it is theoretical based on sliding bearing hydrodynamic lubrication, establish the Reynolds equation of bearing film movement：
Being transformed into cylindrical-coordinate system by rectangular coordinate system can obtain：
Wherein：R --- radial coordinate mm；The dynamic viscosity coefficient of μ --- oil film；P --- oil film pressure distribution p0；h——
Oil film thickness mm；θ --- axial coordinate rad；ω --- shafting rotating speed rad/s；
(h=h is arranged at oil film maximum gauge in coordinate originmax), utilize dimensionless group8. formula is carried out
Nondimensionalization obtains：
λ=2Z/L is the ratio of the radial coordinate Z and half bearing axial length L of oily neck；H=h/c is that oil film is thick
The ratio of degree and bearing shell axle journal gap；
Bearing support oil film pressure distribution is integrated, obtaining expression formula of the support reaction under circular cylindrical coordinate is：
In formula：The eccentricity of e --- bearing sections.
Each bearing support oil film pressure distribution under steady working condition 7., 8., 9., is 10. acquired by formula；
Step 5: in naval vessel shafting motion process, the variation of journal centre is reduced to quasistatic process, when bearing bias
Away from carrying out analysis calculating using linear perturbation theory when changing with the attitude angle；After process in aforementioned school, on rear stern bearing
Load is medium and small compared with straight line school, but increases close to propeller one end oil film pressure maximum value, according to the variation of eccentricity and the attitude angle
Variation and the rigidity definition for causing Oil Film Supporting thickness can calculate and acquire the Ship Axle and tie up in different schools each bearing under state
Oil Film Supporting stiffness Koil：
In formula：--- axle center initial steady state coordinate；
Step 6: the position according to each bearing in the optimum choice result data setting naval vessel shafting in step 3, it will be each
Bearing support effect uses Combin214 unit simulations, and thrust bearing is born axial thrust effect and simulated using spring unit, right
Naval vessel shafting carries out alignment calculation and model analysis.Maximum two of amplitude in whole shafting is chosen according to the conclusion of model analysis
Node is reference point, calculates their vibration amplitude-frequency response to evaluate the Vibration Condition of entire shafting；The shafting in the present embodiment
Two reference points be distributed near the 14 and 131 of attached drawing, amplitude part is most when the selection standard of reference point is shafting model analysis
Greatly, reference point locations are distributed in shafting apart from larger part and local amplitude relatively general goal, can more fully reflect so whole
The Vibration Condition of a shafting；
Step 7: using 1mm as step-length on the basis of in straight line school, in the range of rear stern bearing conjugates (- 5mm, 5mm)
Solving-optimizing object function：
In formula：α1、α2、α3--- it respectively represents load reduction degree, node A and node B whirling vibrations on rear stern bearing and subtracts
The weight coefficient for degree of shaking；
Wherein α1+α2+α3=1；According on tail bearing after shafting inordinate wear and load condition, determine α1Value, value
Ranging from 0.2≤α1≤0.7；Requirement situation according to shafting and naval vessel to vibration characteristics, determines α2And α3Value, and 0.15≤
α2=α3≤0.4；
fA、fB--- respectively represent state lower node A and node B whirling vibration Y-direction peak swing values in straight line school；
K --- rear stern bearing adjustment becomes place value (mm)；
R1k、fAk、fBk--- after respectively representing rear stern bearing adjustment k mm, load, node A and node B are returned on rear stern bearing
Rotation vibration Y-direction peak swing value.
Further refinement to said program further includes that the finite element model tool of the naval vessel shafting is established in the step 2
Body refers to that the naval vessel shafting is discrete for limited a Beam188 beam elements.
Further refinement to said program further includes the offset Y of the vertical position of each bearing in step 30∈[-
10mm, 10mm].
Further refinement to said program further includes that the structure ginseng of naval vessel shafting to be optimized is obtained in the step 1
Number and material parameter, in particular to：Using field survey, either detection method obtains existing naval vessel or the knot of naval vessel shafting
Structure parameter and material parameter；Either to directly export design in naval vessel or naval vessel shafting analog parameter.
A kind of naval vessel centering of shafting Optimization Platform of the present invention, including propeller load simulator, rear tube shaft bearing are real
Test seat, preceding tube shaft bearing experiment seat, thrust bearing experiment seat, driving motor；
Tube shaft bearing experiment seat, preceding tube shaft bearing experiment seat, thrust bearing are tested and are respectively arranged on seat vertically after described
Regulating device is to adjust bearing vertical position；
Tube shaft bearing experiment seat, preceding tube shaft bearing experiment seat, thrust bearing test and are also respectively provided with axis on seat after described
To load simulated and detection device；
The eccentricity and deviation angle detecting device being provided on each bearing between axle journal.
It to said program advanced optimizes including stern tube shaft is supported by forward and backward stern bearing, and thrust axis is by thrust bearing branch
Support, stern tube shaft are connect with jackshaft by half-coupling.
It to said program advanced optimizes including the forward and backward stern bearing in Optimization Platform platform is all water lubrication, thrust
Bearing is oil lubrication.
The beneficial effects of the present invention are：
The present invention can improve the designing quality of shafting, in the initial design phase, by the position for optimizing each bearing of shafting
It sets and achievees the purpose that be promoted centering of shafting quality and reduction shafting vibration.For warship safety, steadily operation provides basis.This hair
Bright for shafting, the design phase controls its vibration characteristics and provides a new departure in school, has important theory and engineering practice
Value can fill up the deficiency of prior art, improve the designing quality of various tired naval vessel shaftings.
Description of the drawings
Fig. 1 is a kind of structural schematic diagram of naval vessel centering of shafting Optimization Platform of the present invention.
Its reference numeral includes：
Revolve paddle load simulator 10, rear tube shaft bearing experiment seat 11, preceding tube shaft bearing experiment seat 12, thrust bearing experiment
Seat 13, stern tube shaft 14, preceding stern bearing 120, rear stern bearing 110, jackshaft 131, thrust bearing 130, stern tube shaft 14, motor 15, gear
Case 16.
Specific implementation mode
It elaborates to the invention below in conjunction with specific embodiment.
A kind of naval vessel centering of shafting optimization method, basic step include：
Step 1: obtaining the structural parameters and material parameter of naval vessel shafting to be optimized, specifically include：In naval vessel shafting
The geometric parameter and material properties of each shaft part, the Support Position of each bearing, the axial and vertical support stiffness of each bearing are described
Geometric parameter includes the size of axis, and the material properties include elasticity modulus and Poisson's ratio, and the Support Position includes axial
Position and vertical position；
Step 2: establishing the finite element model of the naval vessel shafting based on above structure parameter and material parameter；Based on upper
State finite element model carry out discrete processes, in particular to by the naval vessel shafting it is discrete be limited a Beam188 beam elements；
Then institute at the node of any beam element K is represented by respectively by shearing vectorial { Q } and deformation vectors { δ }：
The stiffness matrix of K units
Wherein
The elasticity modulus of E --- material；
The shearing elasticity model of G --- material；
The moment of inertia of I --- the unit to X-axis；
The cross-sectional area of S --- unit；
L --- element length；
Wherein
yj--- the change place value (mm) of j-th of bearing.
I, j --- bearing number is indicated respectively；
Shafting deformation is linear relationship in regime of elastic deformation, between stress and deformation when centering of shafting：
Qe=Keδe..........................................................③
Based on the stiffness matrix that 1., 2., 3. can acquire each beam element in finite element model, by the stiffness matrix of each unit
It reconfigures to obtain the stiffness matrix K of the naval vessel shafting, meanwhile, between shafting deformation δ and institute R (concentrated force and moment of flexure) loaded
Relationship meet：R=K δ.
Step 3: adjusting the offset Y of the vertical position of each bearing on naval vessel stern tube shaft0∈ [- 10mm, 10mm], ignores axis
Bearing lubrication oil film support stiffness changes, and is located at tolerance zone with load on each bearing, the load difference minimum on adjacent bearing is limited
Condition processed, the load R on later tube shaft bearing1Minimum object function solves the optimized migration for obtaining each bearing of vertical position
Amount；It due to the cantilever beam effect of propeller, causes the load of rear stern bearing excessive, easily leads to inordinate wear and the axis of rear stern bearing
It is that transversely excited is excessive.Therefore, when optimizing in optimizing shafting Optimization Platform school, the perpendicular of each bearing of shafting Optimization Platform need to be adjusted
Histogram is conjugated to (Y-direction), load R on later stern bearing1Minimum object function, the load on other bearings is within the allowable range
And the load difference in adjacent two bearings is minimum.Load R after each bearing displacement of shafting on each bearingiIt is represented by：
In formula：R0i--- the load (kn) in shafting straight line school under state on each bearing；Wherein Ti, Tj--- node i, j
On shearing；Mi, Mj--- the moment of flexure in node i, j；yi, yj--- node i, j along Y-axis (vertical direction) displacement；θi,
θj--- node i, j around X-axis (axial direction) corner；
Wherein aijIt is loading effects coefficient AijIn element；It is right after unit displacement that concrete meaning refers to that j-th bearing is completed
Load variations amount caused by i-th of bearing, loading effects coefficient AijIt is load variations moment matrix caused by each bearing influences each other,
Loading effects coefficient AijIt is obtained by the straight line alignment calculation result of corresponding naval vessel shafting.
Based on existing centering of shafting result data it is found that due to propeller cantilever beam effect, the degree of disturbing at rear stern bearing
Deformation, moment of flexure and corner are both greater than shafting other positions, relative to the bearing of other positions in naval vessel shafting, are easiest to occur
Abnormal phenomenon, the purposes of collateral security naval vessel shafting overall performance such as abrasion are set out, the load shape after should considering first on stern bearing
State.
Step 4: it is theoretical based on sliding bearing hydrodynamic lubrication, establish the Reynolds equation of bearing film movement：
Being transformed into cylindrical-coordinate system by rectangular coordinate system can obtain：
Wherein：R --- radial coordinate (mm)；Dynamic viscosity coefficient (the P of μ --- oil filma·s)；P --- oil film pressure distribution
(Pa)；H --- oil film thickness (mm)；θ --- axial coordinate (rad)；ω --- shafting rotating speed (rad/s)；
(h=h is arranged at oil film maximum gauge in coordinate originmax), utilize dimensionless group8. formula is carried out
Nondimensionalization obtains：
λ=2Z/L is the ratio of the radial coordinate Z and half bearing axial length L of oily neck；H=h/c is that oil film is thick
The ratio of degree and bearing shell axle journal gap；
Bearing support oil film pressure distribution is integrated, obtaining expression formula of the support reaction under circular cylindrical coordinate is：
In formula：E, the eccentricity and the attitude angle of θ --- bearing sections.
By formula 7.~10. can be according to the load on each bearing, the next bearing journal of state in shafting Optimization Platform difference school
Between eccentricity and the attitude angle, acquire each bearing support oil film pressure distribution under steady working condition.
Step 5: in naval vessel shafting motion process, the variation of journal centre is reduced to quasistatic process, when bearing bias
Away from carrying out analysis calculating using linear perturbation theory when changing with the attitude angle.After process in aforementioned school, on rear stern bearing
Load is medium and small compared with straight line school, but increases close to propeller one end oil film pressure maximum value, according to the variation of eccentricity and the attitude angle
Variation and the rigidity definition for causing Oil Film Supporting thickness can calculate and acquire the Ship Axle and tie up in different schools each bearing under state
Oil Film Supporting rigidity：
In formula：--- axle center initial steady state coordinate；
Step 6: the position according to each bearing in the optimum choice result data adjustment naval vessel shafting in step 3, by three
The radial support effect of a bearing uses Combin214 unit simulations, thrust bearing to bear axial thrust effect and use spring list
Member simulation carries out alignment calculation and model analysis to naval vessel shafting.And according to the conclusion of model analysis shafting attached drawing 14 Hes
Two nodes that 131 components nearby choose two vibratory response local maximas are as a reference point, calculate their vibration amplitude-frequency and ring
It should be to evaluate the Vibration Condition of entire shafting；Two reference points of the shafting are distributed in the 14 and 131 attached of attached drawing in the present embodiment
Closely；The selection principle of two reference point locations of shafting：(1) it is located at shafting local vibration maximum；(2) two reference point distances are not less than
The 1/4 of shafting overall length；(3) vibration amplitude of shaft part part is larger with respect to other parts near reference point
Step 7: establishing shafting Integrated Optimization Model, and optimizing is carried out, in particular to straight to rear stern bearing displacement situation
Using 1mm as step-length on the basis of in line school, the solving-optimizing object function in the range of rear stern bearing conjugates (- 5mm, 5mm)：
In formula：α1、α2、α3--- it respectively represents load reduction degree, node A and node B whirling vibrations on rear stern bearing and subtracts
The weight coefficient for degree of shaking；Wherein (1) α1+α2+α3=1；According on tail bearing after shafting inordinate wear and load condition, really
Determine α1Value, value range is generally 0.2≤α1≤0.7；(3) the requirement situation according to shafting and naval vessel to vibration characteristics determines
α2And α3Value, generally 0.15≤α2=α3≤ 0.4, high naval vessel, the corresponding increase of the value of the weight are required to vibration；
fA、fB--- respectively represent state lower node A and node B whirling vibration Y-direction peak swing values in straight line school；
K --- rear stern bearing adjustment becomes place value (mm)；
R1k、fAk、fBk--- after respectively representing rear stern bearing adjustment kmm, load, node A and node B are returned on rear stern bearing
Rotation vibration Y-direction peak swing value.
Based on the design principle and method of the present invention, the present invention also provides a kind of naval vessel shafting Optimization Platforms, specific to wrap
Include propeller load simulator 10, rear tube shaft bearing experiment seat 11, preceding tube shaft bearing experiment seat 12, thrust bearing experiment seat
13, driving motor 14；
Tube shaft bearing experiment seat 11, preceding tube shaft bearing experiment seat 12, thrust bearing are tested and are respectively set on seat 13 after described
There is vertical adjustment device to adjust bearing vertical position；
Tube shaft bearing experiment seat 11, preceding tube shaft bearing experiment seat 12, thrust bearing are tested and are also set respectively on seat 13 after described
It is equipped with axial load simulator；
The eccentricity and deviation angle detecting device being provided on each bearing test seat between axle journal；
During experiment porch use, stern tube shaft 14 is supported by preceding stern bearing 120, rear stern bearing 110, jackshaft 131 by
Thrust bearing 130 supports, and stern tube shaft 14 is connect with jackshaft 131 by half-coupling, passes through method between jackshaft 131 and thrust axis
Orchid connection.
Forward and backward stern bearing in this shafting Optimization Platform is all water lubrication, and thrust bearing is oil lubrication.It examines herein
When considering bearing lubrication characteristic, for ease of narration, each bearing is referred to as film lubrication, but when calculating to the difference of lubricating fluid
Attribute has done different simulation process respectively.The motor for simulating naval vessel shafting dynamical system is additionally provided on the experiment porch
15 and gear-box 16
Finally it should be noted that above example is only to illustrate the technical solution of the invention, rather than to this hair
It is bright create protection domain limitation, although being explained in detail to the invention with reference to preferred embodiment, this field it is general
Lead to it will be appreciated by the skilled person that can be modified or replaced equivalently to the technical solution of the invention, without departing from this
The spirit and scope of innovation and creation technical solution.
Claims (8)
1. a kind of naval vessel centering of shafting optimization method, which is characterized in that include the following steps：
Step 1: obtaining the structural parameters and material parameter of naval vessel shafting to be optimized, including each shaft part in naval vessel shafting
The Support Position of geometric parameter and material properties, each bearing, the axial and vertical support stiffness of each bearing, the size of axis, institute
It includes elasticity modulus and Poisson's ratio to state material properties, and the Support Position includes axial position and vertical position；
Step 2: establishing the finite element model of the naval vessel shafting based on above structure parameter and material parameter；Establish finite element
In model at any beam element K node institute by shearing vectorial { Q } and deformation vectors { δ },
And the stiffness matrix of K node unit
Wherein
The elasticity modulus of E --- material；
The shearing elasticity model of G --- material；
The moment of inertia of I --- the unit to X-axis；
The cross-sectional area of S --- unit；
L --- element length；
yj--- the change place value (mm) of j-th of bearing；
I, j --- bearing number is indicated respectively；
According to above-mentioned formula, the stiffness matrix of each beam element in finite element model is acquired, again by the stiffness matrix of each unit
Combination obtains the stiffness matrix K of the naval vessel shafting；
Step 3: adjusting the offset Y of the vertical position of each bearing on naval vessel stern tube shaft0, model allowable is located at load on each bearing
It encloses, the minimum restrictive condition of load difference on adjacent bearing, the load R on later tube shaft bearing1Minimum object function solves
Obtain the optimized migration amount of each bearing of vertical position；Load R after each bearing displacement of shafting on each bearingiIt is represented by：
In formula：R0i--- the load (kn) in shafting straight line school under state on each bearing；Wherein Ti, Tj--- cutting in node i, j
Power；Mi, Mj--- the moment of flexure in node i, j；yi, yj--- node i, j along Y-axis (vertical direction) displacement；θi, θj--- node
I, corners of the j around X-axis (axial direction)；
Step 4: it is theoretical based on sliding bearing hydrodynamic lubrication, establish the Reynolds equation of each bearing film movement：
Being transformed into cylindrical-coordinate system by rectangular coordinate system can obtain：
Wherein：R --- radial coordinate mm；The dynamic viscosity coefficient of μ --- oil film；P --- oil film pressure distribution p0；H --- oil film is thick
Spend mm；θ --- axial coordinate rad；ω --- shafting rotating speed rad/s；
(h=h is arranged at oil film maximum gauge in coordinate originmax), utilize dimensionless group8. formula is carried out immeasurable
Guiding principle obtains：
λ=2Z/L is the ratio of the radial coordinate Z and half bearing axial length L of oily neck；H=h/c be oil film thickness with
The ratio in bearing shell axle journal gap；
Bearing support oil film pressure distribution is integrated, obtaining expression formula of the support reaction under circular cylindrical coordinate is：
In formula：The eccentricity of e --- bearing sections；
Each bearing support oil film pressure distribution under steady working condition 7., 8., 9., is 10. acquired by formula；
Step 5: in naval vessel shafting motion process, the variation of journal centre is reduced to quasistatic process, when bearing eccentricity and
Analysis calculating is carried out using linear perturbation theory when the attitude angle changes；Calculating acquire the Ship Axle tie up in different schools it is each under state
Bearing support oil film rigidity Koil：
In formula：e0、--- axle center initial steady state coordinate；
Step 6: the position according to each bearing in the optimum choice result data setting naval vessel shafting in step 3, by each bearing
Supporting role uses Combin214 unit simulations, and thrust bearing is born axial thrust effect and simulated using spring unit, to naval vessel
Shafting carries out alignment calculation and model analysis；And maximum two sections of amplitude in whole shafting are chosen according to the conclusion of model analysis
Point is reference point, calculates their vibration amplitude-frequency response；
Step 7: using 1mm as step-length on the basis of in straight line school, solved in the range of rear stern bearing conjugates (- 5mm, 5mm)
Optimization object function：
In formula：α1、α2、α3--- it respectively represents load on rear stern bearing and reduces degree, node A and node B whirling vibration vibration damping journeys
The weight coefficient of degree；
Wherein α1+α2+α3=1；According on tail bearing after shafting inordinate wear and load condition, determine α1Value, value range
For 0.2≤α1≤0.7；Requirement situation according to shafting and naval vessel to vibration characteristics, determines α2And α3Value, and 0.15≤α2=α3
≤0.4；
fA、fB--- respectively represent state lower node A and node B whirling vibration Y-direction peak swing values in straight line school；
K --- rear stern bearing adjustment becomes place value (mm)；
R1k、fAk、fBk--- after respectively representing rear stern bearing adjustment kmm, load, node A and node B, which circle round, on rear stern bearing shakes
Dynamic Y-direction peak swing value.
2. a kind of naval vessel centering of shafting optimization method according to claim 1, which is characterized in that being established in the step 2 should
The finite element model of naval vessel shafting specifically refers to the naval vessel shafting is discrete for limited a Beam188 beam elements.
3. a kind of naval vessel centering of shafting optimization method according to claim 1, which is characterized in that each bearing is perpendicular in step 3
To the offset Y of position0∈ [- 10mm, 10mm].
4. a kind of naval vessel centering of shafting optimization method according to claim 1, which is characterized in that obtain and wait in the step 1
The structural parameters and material parameter of the naval vessel shafting of optimization, in particular to：
Using field survey, either detection method obtains existing naval vessel or the structural parameters and material parameter of naval vessel shafting；Or
Person to directly export design in naval vessel or naval vessel shafting analog parameter.
5. a kind of naval vessel centering of shafting optimization method according to claim 1, which is characterized in that the step 6 center shafting
Amplitude local maxima position when two reference points are located at shafting model analysis, and two reference points distance is not less than the 1/4 of shafting overall length.
6. a kind of naval vessel centering of shafting Optimization Platform, which is characterized in that real including propeller load simulator, rear tube shaft bearing
Test seat, preceding tube shaft bearing experiment seat, thrust bearing experiment seat, driving motor；
Tube shaft bearing experiment seat, preceding tube shaft bearing experiment seat, thrust bearing test and are respectively arranged with vertical adjustment on seat after described
Device is to adjust bearing vertical position；
Tube shaft bearing experiment seat, preceding tube shaft bearing experiment seat, thrust bearing test and are also respectively provided with axial load on seat after described
Lotus is simulated and detection device；
The eccentricity and deviation angle detecting device being provided on each bearing test seat between axle journal.
7. a kind of naval vessel centering of shafting Optimization Platform according to claim 6, which is characterized in that stern tube shaft is by forward and backward stern bearing
Support, thrust axis are supported by thrust bearing, and stern tube shaft is connect with jackshaft by half-coupling.
8. a kind of naval vessel centering of shafting Optimization Platform according to claim 6, which is characterized in that forward and backward in Optimization Platform
Stern bearing is all water lubrication, and thrust bearing is oil lubrication.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810239337.6A CN108416159B (en) | 2018-03-22 | 2018-03-22 | Ship shafting optimization method and optimization platform thereof |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109271681A (en) * | 2018-08-29 | 2019-01-25 | 中国舰船研究设计中心 | A kind of ship's fitting and the conformal design method of structure |
| CN109323831A (en) * | 2018-09-05 | 2019-02-12 | 哈尔滨工程大学 | A kind of elongate rotation shaft modal test device discharging advocate approach suddenly based on preload |
| CN110239698A (en) * | 2019-06-24 | 2019-09-17 | 高峰 | A kind of non-maintaining ship rear driving system from centering |
| CN110712731A (en) * | 2019-10-22 | 2020-01-21 | 中国人民解放军海军工程大学 | Ship shafting alignment and cyclotron vibration multidisciplinary optimization method |
| CN111259491A (en) * | 2020-01-21 | 2020-06-09 | 浙江大学 | Rail transit vehicle gearbox body static and dynamic characteristic joint analysis and optimization method |
| CN113806987A (en) * | 2021-09-26 | 2021-12-17 | 中国舰船研究设计中心 | Multi-objective optimization design method for propulsion system and electronic equipment |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101516719A (en) * | 2006-10-18 | 2009-08-26 | 日立造船株式会社 | Evaluation method and device for ship shafting calibration |
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| CN103810305A (en) * | 2012-11-07 | 2014-05-21 | 中国舰船研究设计中心 | Alignment computing method of propeller shaft system of ship |
| CN104760663A (en) * | 2015-01-22 | 2015-07-08 | 中国船舶工业集团公司第七〇八研究所 | Shipping shaft system alignment method |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN107622142A (en) * | 2017-07-13 | 2018-01-23 | 大连理工大学 | A kind of centering of shafting displacement optimization method |
-
2018
- 2018-03-22 CN CN201810239337.6A patent/CN108416159B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101516719A (en) * | 2006-10-18 | 2009-08-26 | 日立造船株式会社 | Evaluation method and device for ship shafting calibration |
| US20130158781A1 (en) * | 2006-10-18 | 2013-06-20 | Hitachi Zosen Corporation | Method and device for evaluating shafting alignment of ship |
| CN103810305A (en) * | 2012-11-07 | 2014-05-21 | 中国舰船研究设计中心 | Alignment computing method of propeller shaft system of ship |
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| CN104760663A (en) * | 2015-01-22 | 2015-07-08 | 中国船舶工业集团公司第七〇八研究所 | Shipping shaft system alignment method |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN107622142A (en) * | 2017-07-13 | 2018-01-23 | 大连理工大学 | A kind of centering of shafting displacement optimization method |
Non-Patent Citations (7)
| Title |
|---|
| GUOJUN LAI 等: "Application of Multi-objective Genetic Algorithm in Ship Shafting Alignment Optimization", 《2017 10TH INTERNATIONAL SYMPOSIUM ON COMPUTATIONAL INTELLIGENCE AND DESIGN》 * |
| HONGSHENG YIN 等: "Research On Multi-disciplinary Design Optimization For Marine Power Plant", 《2017 10TH INTERNATIONAL SYMPOSIUM ON COMPUTATIONAL INTELLIGENCE AND DESIGN》 * |
| 刘学伟 等: "轴系校中状态对艉轴承力传递特性影响", 《噪声与振动控制》 * |
| 刘金林 等: "舰船轴系纵向减振器参数优化方法", 《中国舰船研究》 * |
| 吴杰长 等: "舰船推进轴系轴承最优定位一体化设计", 《海军工程学院学报》 * |
| 周瑞平 等: "船舶推进轴系校中计算中轴承油膜的影响分析", 《船海工程》 * |
| 杨金中: "基于船台校装的舰船轴系校中技术研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109271681A (en) * | 2018-08-29 | 2019-01-25 | 中国舰船研究设计中心 | A kind of ship's fitting and the conformal design method of structure |
| CN109271681B (en) * | 2018-08-29 | 2023-04-07 | 中国舰船研究设计中心 | Conformal design method for ship equipment and structure |
| CN109323831A (en) * | 2018-09-05 | 2019-02-12 | 哈尔滨工程大学 | A kind of elongate rotation shaft modal test device discharging advocate approach suddenly based on preload |
| CN110239698A (en) * | 2019-06-24 | 2019-09-17 | 高峰 | A kind of non-maintaining ship rear driving system from centering |
| CN110712731A (en) * | 2019-10-22 | 2020-01-21 | 中国人民解放军海军工程大学 | Ship shafting alignment and cyclotron vibration multidisciplinary optimization method |
| CN110712731B (en) * | 2019-10-22 | 2021-03-12 | 中国人民解放军海军工程大学 | Ship shafting alignment and cyclotron vibration multidisciplinary optimization method |
| CN111259491A (en) * | 2020-01-21 | 2020-06-09 | 浙江大学 | Rail transit vehicle gearbox body static and dynamic characteristic joint analysis and optimization method |
| CN111259491B (en) * | 2020-01-21 | 2022-06-28 | 浙江大学 | Rail transit vehicle gearbox body static and dynamic characteristic joint analysis and optimization method |
| CN113806987A (en) * | 2021-09-26 | 2021-12-17 | 中国舰船研究设计中心 | Multi-objective optimization design method for propulsion system and electronic equipment |
| CN113806987B (en) * | 2021-09-26 | 2023-09-26 | 中国舰船研究设计中心 | Multi-target optimization design method for propulsion system and electronic equipment |
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