CN106886630A - A kind of pump-jet propulsor hydraulic model with shunting short blade and method for designing - Google Patents
A kind of pump-jet propulsor hydraulic model with shunting short blade and method for designing Download PDFInfo
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Abstract
The invention discloses a kind of pump-jet propulsor hydraulic model with shunting short blade and method for designing, including impeller primary blades and wheel hub, impeller shunting short blade, stator vane and wheel hub, conduit.Thrust load ratio between impeller primary blades and shunting short blade is 3：2.Shunting short blade is identical with primary blades number and single short blade is circumferentially located at two adjacent primary blade middles, and shunting short blade lagging edge axial location is identical with primary blades, to spray the ratio of inlet diameter be 0.63 for guide margin average diameter and pump.Impeller primary blades are respectively provided with big skew back feature with shunting short blade.The present invention can postpone vacuole generation, lift anti-cavitation performance, reduce radiated noise, can adapt to pump and spray during for auxiliary propeller the work characteristics that advance coefficient is small, be easy to produce vacuole.The design of hydraulic model when the technical measures are also applied for the integrated electric-motor pump spray of shaftless drive-type as auxiliary propeller.
Description
Technical field
The invention belongs to marine propeller technical field, and in particular to a kind of pump-jet propulsor waterpower with shunting short blade
Model and method for designing.
Background technology
Pump-jet propulsor (Pumpjet, the spray of abbreviation pump) is with the quilt with the notable feature that radiated noise is low, the critical speed of a ship or plane is high
Low noise submarine main thruster is widely used in, such as " extra large wolf level " submarine and " Virginia level " submarine.U.S. on our times,
Pump spray Push Technology has all been applied to submarine and promoted mainly into the country is there is not yet pump spray propulsion is latent by Britain, France and Russia
It is that ship is on active service main reason is that lacking outstanding pump spray hydraulic model.Outstanding concrete meaning is：Radiated noise is low, critical boat
Fast height (i.e. anti-cavitation ability is strong), propulsive efficiency are moderate.In order to realize this autonomous Design target, a kind of shaftless drive of patent of invention
The method for designing (CN 10446265A, 2015-03-25) and one kind of the integrated motor pump-jet propulsor hydraulic model of dynamic formula are preposition fixed
In the pump-jet propulsor hydraulic model and its method for designing (CN 105117564A, 2015-12-02) of sub- circumference asymmetric arrangement
Elaborate to be applied to the integrated electric-motor pump spray of shaftless drive-type and the conventional method for designing for thering is axle mechanical type pump to spray hydraulic model simultaneously,
Can be designed that the pump spray hydraulic model for meeting propulsion and noise perfomiance requirements simultaneously.In said pump spray hydraulic model, there is three big
Common ground：One is that impeller blade is single cascade primary blades, and considers that impeller blade number is most from blade processing difficulty and weight
Take 9 leaves greatly.Two is that pump is sprayed as main thruster, is saved as projected working point with the specified speed of a ship or plane 16, (general big with major diameter
In 2 meters), the physical features of the slow-speed of revolution (be less than 200 revs/min)；Three is that the spacious water efficiency of pump spray is more than 0.58, design point advance coefficient
Larger, the impeller blade section angle of attack is smaller, and the critical cavitation inception index of blade tip is smaller (typically smaller than 1.2), is more than deeply for latent
Relatively readily satisfied for the design requirement produced without vacuole at 30 meters.
When pump spray is used as latent device auxiliary propeller, because auxiliary propulsion motor speed (is higher than apparently higher than motor is promoted mainly
300 revs/min), and the hull speed of a ship or plane is very low (less than 4 sections) so that and advance coefficient is obviously reduced (typically smaller than 0.4), causes leaf
The piece section angle of attack increases, the critical cavitation inception index of blade tip increases (or even can be more than 4) so that impeller blade produces vacuole
Probability is significantly improved, anti-cavitation hydraulic performance decline (translate, Beijing by D. Rosss, underwater noise principle, underwater noise principle translation group：Sea
Foreign publishing house, 1983), blade design difficulty is also dramatically increased.
In turbomachine field, in order to improve the anti-cavitation performance of impeller blade, in impeller radial dimension, main engine power
Under conditions of being limited with rotating speed, the technical measures that typical case uses have：1. increase the number of blade to reduce the thrust load of unit blade；
2. increase inducer to improve the inlet pressure of impeller blade；3. optimize impeller blade Hydrodynamic design, directly reduce impeller leaf
The blade tip section thrust load of piece.In above-mentioned measure, 1., increase the number of blade increases directly impeller weight to scheme, and blade
The friction loss of fluid passage also increases, under cascade solidity restrictive condition, in order to avoid leaf curling degree is excessive, and big chi
(with diameter greater than 1 meter), the number of blade is usually no more than 13 leaves to the spray of degree pump.2., inducer causes that pump sprays axial length and increases to scheme, leads
The increase of stern vertical bending moment is caused, it is unfavorable to counterweight.3. scheme, by adjusting the Pattern of Radial Distribution Pattern that impeller blade is loaded, sacrifices
Efficiency lifts anti-cavitation performance in a small amount, for the impeller hydraulic model drawn by the design of parametrization ternary Reverse Design
Optimization space very little.Therefore, in order to solve pump spray be used as the latent device cavitation performance of auxiliary propeller be remarkably decreased, blade design it is difficult
The problem that degree is dramatically increased, is on the one hand referred to above-mentioned improved though, on the other hand can also look for another way, by significantly subtracting
The thrust load of leaflet impeller blade improves the purpose of anti-cavitation performance to reach.
About the Impeller Design aspect with shunting short blade, published pertinent literature report domestic at present is focused primarily upon
Centrifugal impeller and aerofoil fan, are mainly used in reducing loss, improve efficiency and reducing noise.
Be can be seen that for the pump spray this leaf with typical shaft stream feature of impeller from the studies above background and using present situation
It is not only feasible in theory to lift anti-cavitation performance using shunting short blade for grid passage, and in technology application
On open a new way of high-performance ship pump class propeller blade design.The technical measures can effectively solve pump spray and use
Make to cause cavitation performance to be difficult to meet desired problem during auxiliary propeller under water because operating point advance coefficient is small, be both applicable
In routinely there is the water spray power modelling of axle mechanical type pump, the integrated electric motor type pump spray hydraulic model of new shaftless driving is also applied for
Design, can effectively fill up the lacuna of the domestic application field, and the strong domestic latent utensil of promotion has the auxiliary of excellent anti-cavitation performance
Boosting enters the independent research and popularization and application sprayed with pump.
The content of the invention：
In order to overcome the defect of above-mentioned background technology, the present invention to provide a kind of pump-jet propulsor waterpower with shunting short blade
Model and method for designing.
In order to solve the above-mentioned technical problem the technical solution adopted in the present invention is：
A kind of pump-jet propulsor hydraulic model with shunting short blade, including conduit, are coaxially provided with preposition leaf in conduit
Wheel and rearmounted stator, impeller include impeller hub, and short with shunting along the impeller primary blades that impeller hub is arranged circumferentially
Blade, impeller primary blades and shunting short blade have skew angle；Stator includes the stator ring being coaxially disposed with the impeller hub
Hub, and the stator vane being arranged circumferentially along stator wheel hub, the blade tip of stator vane are connected with the internal face of conduit.
It is preferred that shunting short blade guide margin average diameter is more than 0.5 with the ratio of pump-jet propulsor inlet diameter, shunt short
Blade lagging edge is identical with the axial location of impeller primary blades lagging edge；The skew back degree of skew angle is not less than 50%.
It is preferred that there is phase between the blade tip section of the blade tip section of impeller primary blades and shunting short blade and pipe inner wall face
Same blade tip clearance, blade tip clearance is 2~the 5 ‰ of impeller diameter.
It is preferred that the skew angle of the impeller primary blades skew angle angle equal with shunting short blade is identical；Impeller primary blades side
Oblique angle more than angle between adjacent impeller primary blades half, shunting short blade skew angle more than adjacent shunting short blade it
Between angle half；The skew angle of impeller primary blades and the skew angle angle of shunting short blade are from blade root to blade tip section by linear
Rule increases.
It is preferred that conduit includes zero thrust and low thrust conduit, the cross section profile of pipe inner wall face and outside wall surface forms fertilizer
Thicker conduit.
It is preferred that impeller primary blades are identical with the number of sheets of shunting short blade, the number of sheets of impeller primary blades and shunting short blade
It is all higher than 5 leaves；The number of sheets of impeller primary blades and the number of sheets of stator vane are relatively prime.
A kind of method for designing of the pump-jet propulsor hydraulic model as described above with shunting short blade, including：
Step 1, the Selection and Design of pump fluid passage hydraulic parameters is carried out according to design requirement；
Step 2, determine pump spray preposition impeller, rearmounted stator and inside and outside conduit wall two-dimentional axis plane projection geometry；
Step 3, impeller and stator are determined by step 1 and step 2 acquired results using parametrization ternary Reverse Design
3 dimensional coil geometry；Led the two-dimentional axis plane projection geometry of conduit is circumferentially rotatable by step 1 and step 2 acquired results
Pipe 3 dimensional coil geometry；
Step 4, makes impeller primary blades and shunting short blade have skew angle, impeller primary blades and shunting short blade skew angle
Angle is identical；
Step 5, the hydrodynamic performance under the conditions of the gained model specification of calculation procedure 4 judges whether to meet design, if so,
Then enter step 6；If it is not, then returning to step 2 changes two-dimentional axis plane projection geometry, and impeller primary blades and fixed in set-up procedure 3
Blade surface of the blades during ternary reverse engineer loads the regularity of distribution radially and axially, redesigns impeller and determines
Sub- 3 dimensional coil geometry；
Step 6, using the gained model of Fluid Mechanics Computation method calculation procedure 5 given latent depth, design speed, rotating speed and
The cavitation performance of pump spray under the conditions of wake, judges that pump spray blade is in non-cavitating or has cavitation condition：If being in non-cavitating
State, then into step 7；If being in cavitation inception state, step 3 adjustment impeller primary blades and shunting short blade are returned to three
Blade surface during unit reverse-engineers loads axially distributed rule；If being in serious cavitation condition, return to step 2 and repair
Change corresponding two dimension axis plane projection geometry, and in set-up procedure 3 impeller primary blades lagging edge and stator vane guide margin circular rector along footpath
To the regularity of distribution, impeller and stator 3 dimensional coil geometry are redesigned；
Step 7, using the gained model of Fluid Mechanics Computation method calculation procedure 6 given latent depth, design speed, rotating speed and
The unsteady propulsive performance of pump spray under the conditions of wake, asks for the pulsation thrust coefficient with the pump spray of shunting short blade, and by theoretical public
Formula is calculated line spectrum noise, judges whether pump spray line spectrum noise meets design requirement：If so, then entering step 8；If it is not, then
Returning to step 2 increases the axial distance of impeller primary blades and stator vane；
Step 8, it is determined that the pump-jet propulsor hydraulic model with shunting short blade.
It is preferred that the axial distance in step 2 between impeller primary blades and stator vane is more than the 0.5 of primary blades chord length
Times.
It is preferred that impeller primary blades, shunting short blade and stator vane use the profile thicknesses of NACA 16 in step 3
Distribution.
It is preferred that making impeller primary blades skew angle in step 4 more than the half of angle between adjacent fan-wheel primary blades, shunting
Short blade skew angle makes the skew back of impeller primary blades and shunting short blade more than the half of angle between adjacent shunting short blade
Angle angle increases from blade root to blade tip section by linear rule.
It is preferred that the modification two dimension axis plane projection geometry in step 5 includes：Impeller in the two-dimentional axis plane projection geometry of modification
Main vane diameter and axial length.
It is preferred that the modification two dimension axis plane projection geometry in step 6 includes：Impeller in the two-dimentional axis plane projection geometry of modification
The axial location and blade tip section chord length of primary blades guide margin.
The beneficial effects of the present invention are：It is short by introducing shunting on the basis of conventional mechanical formula pump spray hydraulic model
Blade, has obtained the rearmounted stator pump-jet propulsor hydraulic model with shunting short blade, it is adaptable to which pump spray is used as auxiliary propeller
When the characteristics of operating point advance coefficient is small, anti-cavitation performance requirement is high.Impeller primary blades and shunting in design pump spray hydraulic model
The number of blade of short blade is 7 leaves, and stator vane count is 9 leaves, and conduit is low thrust hypertrophic conduit.Impeller primary blades, shunting
Short blade and stator vane use NACA16 profile thickness distribution characteristics.Impeller primary blades and shunting short blade are respectively provided with big side
Oblique feature, and skew angle is identical.Design pump be sprayed on the specified speed of a ship or plane 4 save, under rated speed 300rpm, it is 0.28, ship to open water efficiency
Axial thrust is produced to be less than 250kW, the non-cavitating when depth of water is more than 10 meters more than 37kN, consumption power under the conditions of trailing edge interlayer influent stream
Produce, pump spray line spectrum noise is less than 125dB at the corresponding single order leaf frequency of axial pulse thrust coefficient.Used in the design
The design of hydraulic model when technical measures are also applied for the integrated electric-motor pump spray of shaftless drive-type as auxiliary propeller, the technology is arranged
The popularization and application that pump sprays auxiliary propulsion technology can be rapidly promoted after applying popularization and application.
Brief description of the drawings
Fig. 1 is the rearmounted stator pumps spray hydraulic model 3 dimensional coil geometry of embodiment of the present invention band shunting short blade；
Fig. 2 is the rearmounted stator pumps spray hydraulic model two dimension axis plane projection geometry of embodiment of the present invention band shunting short blade；
Fig. 3 is the rearmounted stator pumps water spray power modelling flow chart of embodiment of the present invention band shunting short blade.
Specific embodiment
The present invention is described further with reference to the accompanying drawings and examples.
A kind of pump-jet propulsor hydraulic model with shunting short blade 2, includes conduit 6 as shown in Figure 1, coaxial in conduit 6
Preposition impeller and rearmounted stator is provided with, impeller includes impeller hub 3, and the impeller being arranged circumferentially along impeller hub 3
Primary blades 1 and shunting short blade 2, impeller primary blades 1 and shunting short blade 2 have skew angle, and the skew back degree of skew angle is
50%；Stator includes the stator wheel hub 5 being coaxially disposed with the impeller hub 3, and along determining that stator wheel hub 5 is arranged circumferentially
Blades 4, the blade tip of stator vane 4 is connected with the internal face 14 of conduit 6.Impeller primary blades 1, shunting short blade 2 and stator leaf
Piece 4 is using the distribution of the profile thicknesses of NACA 16.
Conduit 6 is zero thrust conduit 6 or low thrust conduit 6, and internal face 14, the cross section profile of outside wall surface 15 form hypertrophic
Conduit 6.Conduit 6 is low thrust conduit 6 in the present embodiment.
The ratio of the average diameter and pump-jet propulsor inlet diameter that shunt the guide margin 8 of short blade 2 is more than 0.5, the present embodiment
In be preferably 0.63.The shunting lagging edge 9 of short blade 2 is identical with the axial location of the lagging edge 9 of impeller primary blades 1.
There is phase between the blade tip section of impeller primary blades 1 and the blade tip section of shunting short blade 2 and the internal face 14 of conduit 6
Same blade tip clearance, blade tip clearance is 2~the 5 ‰ of impeller diameter.
The skew angle of impeller primary blades 1 is identical with the skew angle angle of shunting short blade 2；The skew angle of impeller primary blades 1 is big
The half of angle between adjacent impeller primary blades 1, shunting short blade 2 skew angle is more than between adjacent shunting short blade 2
The half of angle；The skew angle of impeller primary blades 1 and the skew angle angle of shunting short blade 2 are from blade root to blade tip section by linear
Rule increases.
Impeller primary blades 1 are identical with the number of sheets of shunting short blade 2, and the number of sheets of impeller primary blades 1 and shunting short blade 2 is big
In 5 leaves；The number of sheets of impeller primary blades 1 and the number of sheets of stator vane 4 are relatively prime.In the present embodiment, impeller primary blades 1 and the short leaf of shunting
The number of sheets of piece 2 is 7 leaves, and the number of sheets of stator vane 4 is 9 leaves.
A kind of method for designing of the pump-jet propulsor hydraulic model as described above with shunting short blade 2, including：
Step 1, the Selection and Design of pump fluid passage hydraulic parameters is carried out according to design requirement；During Selection and Design, according to ship
Oceangoing ship hydraulic jet propulsion is theoretical, and lift, flow, discharge area, specific speed and the suction inlet of pump spray blade grid passage are determined by rapidity requirement
5 parameters of specific speed.
Step 2, determines that pump sprays preposition impeller, rearmounted stator and the internal face 14 of conduit 6, the two-dimentional axis plane projection of outside wall surface 15
Geometry；The internal face 14 of conduit 6, the cross section profile shape of outside wall surface 15 in rearmounted stator pumps spray hydraulic model with shunting short blade 2
It is into the meaning of hypertrophic conduit 6：The radial thickness in axial direction of conduit 6 is long with the axial direction of the ratio more than 0.8 of maximum gauge
Degree scope is more than 0.5 with the ratio of the total axial length of conduit 6.
As shown in Fig. 2 two-dimentional axis plane projection geometry includes impeller primary blades guide margin 7, shunting short blade guide margin 8, primary blades
Lagging edge 9, impeller hub 10, stator vane guide margin 11 and lagging edge 12, stator wheel hub 13, the internal face 14 of conduit 6 and outside wall surface 15
Axis plane projection.The shunting lagging edge of short blade 2 overlaps with the axis plane projection of primary blades lagging edge 9.Impeller primary blades 1 and shunting short blade 2
The internal face 14 of blade tip cross-sectional distance conduit 6 be provided with blade tip clearance, and clearance distance is equal.Shunting short blade 2 guide margin is put down
Equal diameter is 0.63 with the ratio of pump spray inlet diameter.Axial distance of the guide margin of stator vane 4 away from the lagging edge 9 of impeller primary blades 1 with
The ratio of primary blades chord length is 0.75.
Step 3, impeller and stator are determined by step 1 and step 2 acquired results using parametrization ternary Reverse Design
3 dimensional coil geometry；Obtained the two-dimentional axis plane projection geometry of conduit 6 is circumferentially rotatable by step 1 and step 2 acquired results
The 3 dimensional coil geometry of conduit 6；
Blade (impeller primary blades 1, shunting short blade 2 and stator vane 4) 3 dimensional coil geometry is by hydraulic parameters (primary blades
With load percentage, the blade load regularity of distribution radially and axially of shunting short blade 2) and geometric parameter (axial plane geometry, leaf section
Face thickness is distributed and stacking angle) together decide on.The load percentage of primary blades and shunting short blade 2 determines that primary blades are pushed away to total
The contribution of power load；The axially distributed rule of blade load determines distribution of the leaf sectional pressure coefficient along chord length direction, and then
Directly determine its capacity for work and anti-cavitation performance；The radially distributed rule of blade load is used to control the He of impeller primary blades 1
Shunting short blade 2 improves efficiency along the secondary flow in the capacity for work and blade grid passage in span direction.Blade thrust load
The derivative of (pressure differential between blade face pressure face and suction surface) with circumferentially average circular rector rVt on meridian streamline direction is close
Cut is closed, and Mathematical Modeling is,
In formula, ρ is the density of seawater；R is any section radius on impeller blade；VmIt is circumferentially average axial plane speed
The ratio of both degree, area corresponding with diameter in axis projection equal to flow；VtIt is circumferentially average tangential velocity point
Amount, equal to circular rector rVtThe ratio of radius, circular rector rV in value and axis projectiontIt is worth and is determined by lift and rotating speed,ηhIt is hydraulic efficiency, initial value is taken as 0.88 during design；p+、p-It is respectively blade pressure surface and suction surface
Static pressure, both differences are equal to blade and produce thrust；B is the number of blade, is empirically given, such as impeller primary blades 1 and the short leaf of shunting
Piece 2 is 7 leaves, the leaf of stator vane 9；M is dimensionless meridian streamline length, is geometric parameter at blade difference span, from blade
Import is 0 to 1 to value is exported.
When impeller primary blades 1, shunting 43 dimensional coil geometry of short blade 2 and stator vane are designed：Impeller primary blades 1 with
Adopted using increment type swirl distribution, the guide margin of stator vane 4 using increment type swirl distribution, the impeller shunting lagging edge 9 of short blade 2 on side 9
Use quadratic power swirl distribution；The blade root section of impeller primary blades 1 and stator vane 4 use in load type load distribution, blade tip cut
Face uses rear bearing type load distribution；Small positive incidence, the blade tip of stator vane 4 are used at the blade root section guide margin of impeller primary blades 1
Small negative angle of attack is used at section lagging edge 12.
Ratio in the present embodiment between impeller primary blades 1 and the shunting thrust load of short blade 2 is preferably 3：2.
Step 4, makes impeller primary blades 1 and shunting short blade 2 have skew angle, namely make it have big skew back feature, leaf
Wheel primary blades 1 are identical with the shunting skew angle angle of short blade 2, and skew back degree is 50%；
Make the skew angle of impeller primary blades 1 more than the half of angle between adjacent fan-wheel primary blades 1 in this step, shunt short leaf
The skew angle of piece 2 makes the skew back of impeller primary blades 1 and shunting short blade 2 more than the half of angle between adjacent shunting short blade 2
Angle angle increases from blade root to blade tip section by linear rule.
Step 5, the hydrodynamic performance under the conditions of the gained model specification of calculation procedure 4 judges whether to meet design, if so,
Then enter step 6；If it is not, then returning to step 2 changes two-dimentional axis plane projection geometry, and impeller primary blades 1 and fixed in set-up procedure 3
The blade surface load radially and axially regularity of distribution of the blades 4 during ternary reverse engineer, redesign impeller and
Stator 3 dimensional coil geometry；Two-dimentional axis plane projection geometry is changed in this step to be included：Leaf in the two-dimentional axis plane projection geometry of modification
The wheel diameter of primary blades 1 and axial length.
Step 6, using the gained model of Fluid Mechanics Computation method calculation procedure 5 given latent depth, design speed, rotating speed and
The cavitation performance of pump spray under the conditions of wake, judges that pump spray blade is in non-cavitating or has cavitation condition：If being in non-cavitating
State, then into step 7；If being in cavitation inception state, return to step 3 adjustment impeller primary blades 1 and shunting short blade 2 exists
Blade surface during ternary is reverse-engineered loads axially distributed rule；If being in serious cavitation condition, step 2 is returned to
The corresponding two dimension axis plane projection geometry of modification, and in set-up procedure 3 lagging edge 9 of impeller primary blades 1 and the guide margin 11 of stator vane 4 ring
Radially distributed rule is measured, impeller and stator 3 dimensional coil geometry is redesigned；Modification two dimension axis plane projection in this step is several
What includes：The axial location and blade tip section chord length of the guide margin 7 of impeller primary blades 1 in the two-dimentional axis plane projection geometry of modification.
When calculating pump spray cavitation performance, the modified Sauer cavitation models that cavitation model is preferentially proposed using inventor：
Wherein,WithRepresent respectively water vapour evaporation (air bubble growth) and condense (bubble is crumbled and fall) process, evaporation with
Condensation coefficient takes C respectivelyprod=50 and Cdest=0.01, the average initial radium R of bubbleB=1.5 μm, αvAnd ρvRepresent that water steams respectively
Gas fraction and density, ρlThe density of water is represented, p represents Fluid pressure, pvPhase transformation critical pressure is represented, value is such as during calculating
Formula (2)：
Wherein, psatPressure for vaporization constant is represented, k represents Hydrodynamic turbulence energy, ρmFluid-mixing density is represented, is taken during calculating
Value such as formula (3)：
ρm=(αvρv+(1-αv-αg)ρl)/(1-fg) (3),
Wherein, αgAnd fgThe volume fraction and mass fraction of not concretive gas core NCG are represented respectively, and value is αg=7.8 ×
10-4And fg=1.0 × 10-6.For the three-phase mixed flow body being made up of water, water vapour and NCG, the volume fraction of each phase
Relational expression is satisfied by with mass fraction
In addition, when calculating pump spray cavitation performance, cavitation model can also be using the Zwart models such as formula (4)
Wherein,rnucIt is gas nucleome fraction,RBIt is gas nuclear radius, parameter value is rnuc=5.0 × 10-4,RB=2.0 ×
10-6, Fe=50, Fc=0.01.
Hybrid density ρ=ρ=αvρv+(1-αv)ρl。
Carrying out can also be using the Sauer model such as formula (5) when cavitation performance is calculated：
Wherein,n0It is constant
Step 7, using the gained model of Fluid Mechanics Computation method calculation procedure 6 given latent depth, design speed, rotating speed and
The unsteady propulsive performance of pump spray under the conditions of wake, asks for the pulsation thrust coefficient with the pump spray of shunting short blade 2, and by theoretical public
Formula is calculated line spectrum noise, judges whether pump spray line spectrum noise meets design requirement：If so, then entering step 8；If it is not, then
Returning to step 2 increases the axial distance of impeller primary blades 1 and stator vane 4；Calculate pump spray pulsation thrust coefficient and assess line
Analogy method SAS combination pulsating force radiated noises theoretical formula can be adapted to during spectral noise using yardstick to complete.
When unsteady propulsive performance is calculated, using unsteady transient state CFD computational methods, analogy method is such as adapted to using yardstick
SAS separates whirlpool analogy method DES or Large eddy simulation method LES.It is preferential to be simulated using SAS, pump spray pulsation thrust can improved
Effectively shorten the R＆D cycle under conditions of coefficient computational accuracy.
When calculating pump spray line spectrum noise, using the theoretical model of such as formula (6)
Wherein, p is acoustic pressure, and t' is lag time, and F is pulsation thrust, and r is pulsating force source to measuring point distance, and θ is that F and r is sweared
Angle between amount, the cos θ dipole sound field directive property for being used to characterize pulsating force source.Once pulsation thrust amplitude determines, then line spectrum
Noise spectrum source class determines.
Step 8, it is determined that the pump-jet propulsor hydraulic model with shunting short blade 2.
It should be appreciated that for those of ordinary skills, can according to the above description be improved or converted,
And all these modifications and variations should all belong to the protection domain of appended claims of the present invention.
Claims (10)
1. a kind of pump-jet propulsor hydraulic model with shunting short blade, including conduit, is provided with preposition impeller in the conduit
With rearmounted stator, it is characterised in that：The impeller includes impeller hub, and the leaf being arranged circumferentially along the impeller hub
Wheel primary blades and shunting short blade, the impeller primary blades and the shunting short blade have skew angle；The stator include with
The stator wheel hub that the impeller hub is coaxially disposed, and the stator vane being arranged circumferentially along the stator wheel hub, it is described fixed
The blade tip of blades is connected with the internal face of the conduit.
2. it is according to claim 1 it is a kind of with shunting short blade pump-jet propulsor hydraulic model, it is characterised in that：It is described
The ratio of shunting short blade guide margin average diameter and pump-jet propulsor inlet diameter is more than 0.5, the shunting short blade lagging edge with
The axial location of the impeller primary blades lagging edge is identical.
3. it is according to claim 1 it is a kind of with shunting short blade pump-jet propulsor hydraulic model, it is characterised in that：It is described
There is identical leaf between the blade tip section and the pipe inner wall face of the blade tip section of impeller primary blades and the shunting short blade
Top gap, the blade tip clearance is 2~the 5 ‰ of impeller diameter.
4. it is according to claim 1 it is a kind of with shunting short blade pump-jet propulsor hydraulic model, it is characterised in that：It is described
The skew angle of impeller primary blades is identical with the skew angle angle of the shunting short blade；The impeller primary blades skew angle is more than phase
The half of angle between the adjacent impeller primary blades, the shunting short blade skew angle is more than the adjacent shunting short blade
Between angle half；The skew angle angle of the skew angle of the impeller primary blades and the shunting short blade is from blade root to blade tip
Section is increased by linear rule.
5. it is according to claim 1 it is a kind of with shunting short blade pump-jet propulsor hydraulic model, it is characterised in that：It is described
Conduit includes the cross section profile formation hypertrophic conduit of zero thrust and low thrust conduit, the pipe inner wall face and outside wall surface.
6. it is according to claim 1 it is a kind of with shunting short blade pump-jet propulsor hydraulic model, it is characterised in that：It is described
Impeller primary blades are identical with the number of sheets of shunting short blade, and the number of sheets of the impeller primary blades and shunting short blade is all higher than 5 leaves；Institute
State impeller primary blades the number of sheets and the stator vane the number of sheets it is relatively prime.
7. it is a kind of as described in claim any one of 1-5 with shunting short blade pump-jet propulsor hydraulic model method for designing,
It is characterised in that it includes：
Step 1, the Selection and Design of pump fluid passage hydraulic parameters is carried out according to design requirement；
Step 2, determine pump spray preposition impeller, rearmounted stator and inside and outside conduit wall two-dimentional axis plane projection geometry；
Step 3, the three of impeller and stator is determined by step 1 and step 2 acquired results using parametrization ternary Reverse Design
Dimension geometry；Conduit three is obtained by the two-dimentional axis plane projection geometry of conduit is circumferentially rotatable by step 1 and step 2 acquired results
Dimension geometry；
Step 4, makes the impeller primary blades and the shunting short blade have skew angle, the impeller primary blades and the shunting
Short blade skew angle angle is identical；
Step 5, calculates the hydrodynamic performance under the conditions of the step 4 gained model specification speed of a ship or plane, rotating speed and wake, judges described
Whether satisfaction is designed, if so, then entering step 6；If it is not, then returning to step 2 changes two-dimentional axis plane projection geometry, and adjust described
The blade surface of impeller primary blades and the stator vane during ternary reverse engineer is loaded radially and axially in step 3
The regularity of distribution, redesigns impeller and stator 3 dimensional coil geometry；
Step 6, using the gained model of Fluid Mechanics Computation method calculation procedure 5 in given latent depth, design speed, rotating speed and wake
Under the conditions of pump spray cavitation performance, judge that pump spray blade is to be in non-cavitating or to have cavitation condition：If being in non-cavitating state,
Then enter step 7；If being in cavitation inception state, return to step 3 adjustment impeller primary blades and shunting short blade is inverse in ternary
Axially distributed rule is loaded to the blade surface in design process；If being in serious cavitation condition, step 2 modification phase is returned to
The two-dimentional axis plane projection geometry answered, and the circular rector of impeller primary blades lagging edge and stator vane guide margin is radially divided in set-up procedure 3
Cloth rule, redesigns impeller and stator 3 dimensional coil geometry；
Step 7, using the gained model of Fluid Mechanics Computation method calculation procedure 6 in given latent depth, design speed, rotating speed and wake
Under the conditions of pump spray unsteady propulsive performance, ask for the pulsation thrust coefficient that band shunting short blade pump sprays, and by theoretical formula meter
Calculation obtains line spectrum noise, judges whether pump spray line spectrum noise meets design requirement：If so, then entering step 8；If it is not, then returning to
Step 2 increases the axial distance of impeller primary blades and stator vane；
Step 8, it is determined that the pump-jet propulsor hydraulic model with shunting short blade.
8. according to claim 7 with shunting short blade pump-jet propulsor hydraulic model method for designing, it is characterised in that：
The regularity of distribution includes radially and axially for adjustment blade surface load in the step 5：Load radially increment type ring
Amount distribution and quadratic power swirl distribution, load middle load type distribution and the distribution of rear bearing type vertically.
Make the impeller primary blades skew angle in the step 4 more than the half of angle between the adjacent impeller primary blades, point
Stream short blade skew angle makes the impeller primary blades and the shunting short more than the half of angle between adjacent shunting short blade
The skew angle angle of blade increases from blade root to blade tip section by linear rule.
9. according to claim 7 with shunting short blade pump-jet propulsor hydraulic model method for designing, it is characterised in that
Modification two dimension axis plane projection geometry in the step 5 includes：The impeller master in the two-dimentional axis plane projection geometry of modification
Blade diameter and axial length.
10. the method for designing of the pump-jet propulsor hydraulic model according to claim 7 with shunting short blade, its feature exists
In the modification two dimension axis plane projection geometry in the step 6 includes：Impeller main lobe in the two-dimentional axis plane projection geometry of modification
The axial location and blade tip section chord length of piece guide margin.
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