CN105117564A - Pumpjetpropulsor hydraulic model with front stators circumferentially and asymmetrically arranged and design method thereof - Google Patents
Pumpjetpropulsor hydraulic model with front stators circumferentially and asymmetrically arranged and design method thereof Download PDFInfo
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Abstract
The invention discloses a pumpjetpropulsor hydraulic model with front stators circumferentially and asymmetrically arranged and a design method thereof. The pumpjetpropulsor hydraulic model comprises stator blades, a stator hub, impeller blades, an impeller hub and a guide tube. The stator blades are circumferentially and asymmetrically arranged on the stator hub, and blade tips of the stator blades are fixed to the inner wall face of the guide tube. The axis of the stator hub, the axis of the impeller hub and the axis of the guide tube coincide. The impeller blades have the characteristics of large side skewing and tail longitudinal inclination. The pitch angles of the stator blades are changed according to the sine rule on the basis of the pitch angles of reference pumpjet stator blades, and the change quantity of the pitch angles is related to the circumferential angle positions of the stator blades, impeller turning directions and amplitude coefficients. According to the pumpjetpropulsor hydraulic model with front stators circumferentially and asymmetrically arranged and the design method thereof, the amplitude of pumpjet pulsation thrust coefficients can be reduced, pumpjet radiation noise is lowered, and the pulsation thrust coefficients of the pumpjet with the front stators circumferentially and asymmetrically arranged are reduced by 3.4% compared with a reference pumpjet under the same design condition. The technical measure is also suitable for noise optimization design of shaftless driving type integration motor pumpjet hydraulic models.
Description
Technical field
The present invention relates to marine propeller technical field, particularly relate to and there is low noise and the critical speed of a ship or plane feature of height, may be used for the pump-jet propulsor advancing underwater hiding-machine.
Background technology
Pump-jet propulsor (Pumpjet, be called for short pump spray) be widely used in low noise submarine propulsion to have the high notable feature of low, the critical speed of a ship or plane of radiated noise, as " extra large wolf level " submarine and " Virginia level " submarine all have employed the spray of stator before rotor formula pump.On our times, pump has all been sprayed Push Technology and has been applied to nuclear submarine propelling by the U.S., Britain, France and Russia, domesticly there is not yet the main cause that pump spray advances submarine to be on active service and is to lack outstanding pump spray hydraulic model.Outstanding concrete meaning is: radiated noise is low, propulsive efficiency is moderate, the critical speed of a ship or plane high (namely anti-cavitation ability is strong) (a kind of method for designing of shaftless drive-type integrate motor pump-jet propulsor hydraulic model, publication number: 104462652A, publication date: 2015-03-25).In order to realize this autonomous Design target, set forth in foregoing invention patent and be applicable to the spray of shaftless drive-type integrated electric pump and the conventional method for designing having axle mechanical type pump to spray hydraulic model simultaneously, the pump spray numerical model simultaneously meeting propelling and noise perfomiance requirements can be designed, and illustrate the shaftless pump spray hydraulic model of a type stator before rotor 13 leaf blade and the rearmounted impeller blade of 9 leaves.In this design proposal, no matter be stator vane or impeller blade, all have employed circumference and be arranged symmetrically with design, arrange identical with all the time traditional marine propeller, as screw propeller, no matter be the modern times 5 leaf highly skewed propeller that surface vessel adopts, or the 7 leaf highly skewed propellers that conventional submarine adopts, geometry and the angle of pitch of every sheet blade are all identical.To design and after placing a slice blade, the design only needing symmetric replication in the circumferential can complete all the other blades with lay.The advantage of this design arrangement is: 1. design comparatively simple.Reason is: the hydraulic model meeting efficiency and cavitation performance requirement under normally first designing uniform incoming flow during marine propeller design, and then consider that the true non-uniform wake of stern is on the impact of propeller performance, and the suitable former design proposal blade profile of modification and perfection thus.Circumference is arranged symmetrically with blade profile and is just in time adapted to uniform incoming flow condition, and it is more much smaller than the calculated amount analyzing all blades to analyze the individual blade stressing conditions after adopting circumferential symmetrical boundary condition, and the design cycle is shorter.2. processing and manufacturing is comparatively simple.Reason is: under the same limit of machining precision, blade strength and complex blade, and the processing and manufacturing difficulty of marine propeller is always comparatively large, and particularly modern marine propellers, as highly skewed propellers and hydraulic propeller.When adopting 5 axles or 7 axis linkage numerical control machine tooling, the more circumferential asymmetric arrangement of blade design instruction that circumference is arranged symmetrically with is simply too much.3. blade profile mapping is more simple.Reason is: when not having its three-dimensional numerical value geometric model only there being thruster in kind, as introduced thruster, needs to survey and draw its blade profile data; Or after thruster injury repair, also need to survey and draw blade profile data during assessment repairing effect.The data of single vane foil that mapping circumference is arranged symmetrically with are more simply too much than all blades of mapping, lower to the requirement of surveying instrument.
But although circumference is arranged symmetrically with blade profile have above-mentioned advantage, thruster real work this essential characteristic in the non-uniform wake field of naval vessels afterbody does not become.Interact just because of the periodicity between the influent stream of circumferential non-uniform Distribution and rotating vane, thruster is just made to there is significant line spectrum noise, and noise frequency be positioned at leaf frequently (product of rotating speed and the number of blade) and doubly leaf frequency locate (JSCarlton.Marinepropellersandpropulsion (propeller for vessels and propelling), Secondedition, ElsevierLtd.2007).This physical phenomenon essence makes thruster noise-reducing design be mainly derived from reduction rotating speed, increases the number of blade and reduce blade cyclic pulsating force amplitude.Submarine propeller is pump spray from 7 leaf highly skewed propellers evolving developments, also considers based on this just.When modern low noise warship design this index of overriding concern radiated noise traction under, especially for submarine, Low Noise Design effect becomes weighs the impeller design whether successfully first element.Under this design requirement, the main advantage that circumference is arranged symmetrically with blade profile is more and more desalinated.Want on the basis of pump-jet propulsor, obtain significant noise-reducing design further to break through, except from except Curve guide impeller method on source, can only be consider from the architectural feature changing pump spray, as added high performance acoustic absorbant in pump spray conduit, pump being sprayed the part or all of employing high-performance composite materials etc. of stator and impeller blade.In view of the parametrization ternary Reverse Design adopted during pump spray blade design in patent of invention " a kind of method for designing of shaftless drive-type integrate motor pump-jet propulsor hydraulic model " has been in theory the top being in current rotating machinery blade design method, can directly control blade 3 dimensional coil geometry by the blade load regularity of distribution, large breakthrough cannot be had again in a short time.Therefore, can only be consider that emphatically the architectural feature changing pump spray is to carry out Acoustic Optimization design.
In order to reduce the radiated noise of pump spray further, have at present and adopt the rapidoprint of acoustical behavior excellence to carry out pump spray acoustical behavior optimal design, but compound substance pump-jet propulsor designing technique is at present international and be domesticly still in the exploratory stage, so risk is larger.In order to reduce risk, the application proposes to adopt the stator before rotor blade design method of circumferential asymmetric arrangement to carry out Acoustic Optimization design, more simple on design realizes, and also easier basis of spraying hydraulic model at original metal pump has been improved.The technical risk of being carried out noise reduction by the arrangement changing blade is more much smaller than adopting new material, also more feasible in Project Realization.
The circumferential asymmetric arrangement of pump spray stator before rotor blade, there are three layers of implication: one is that the puberty of the blade profile of different circumferential angle position own changes, but two is that the identical angle of pitch of the vane foil of different circumferential angle position is different, but three be that the vane foil of different circumferential angle position is identical, corner dimension between the identical adjacent blades of the angle of pitch is different.In the cases of design that the application realizes, indication is the blade pitch angle difference of different circumferential angle position.
Circumference asymmetric arrangement blade, not arbitrarily change angle between the angle of pitch of former symmetrical blade and adjacent blades, but make the spatial distribution characteristic being circumferentially adapted to ship tail circumference non-uniform Distribution wake of blade, be the equal of for each individual vanes carries out the design of " cutting the garment according to the figure " formula ground, reduce pump with this and spray total pulsating force amplitude, and then suppress line spectrum noise size.While carrying out acoustical behavior optimal design, circumferential asymmetric arrangement blade can also additional elevation pump spray maneuvering performance.Reason is: hull boundary layer flow is the main source of the circumferential non-homogeneous influent stream of pump spray, and pump spray performance is very responsive to hull wake of boundary layer.When hull is handled, boundary layer flow occurs significantly to change, and pump may be made to spray propulsive performance and decline more (Wang Yongsheng, Liu Chengjiang etc., the novel propulsion system in naval vessel, Beijing: National Defense Industry Press, 2014).When pump spray blade circumference is arranged symmetrically with, mainly produce axial force, and transverse force and vertical force component very little, under hull operation state, likely occur that pump spray cannot provide the phenomenon of enough transverse directions and vertical steering force, increased the weight of the manipulation burden of rudder face.When preposition stator vane adopts circumferential asymmetric arrangement scheme, design experiences shows: along with pump sprays the increase of spinner blade skew back degree and laden by the stern degree, pump spray can produce comparatively significantly side force and side direction moment, and side force amplitude is relevant to the size of stator vane circumference asymmetric arrangement angle.If design proper, effectively can utilize this side direction moment, increase security during pump spray propelling Submarine Control.
In the marine propeller design research and development of vane of concern circumference asymmetric arrangement, current domestic published pertinent literature report does not almost have.In Chinese patent net with " blade asymmetric arrangement " for keyword is retrieved, only there are 2 patents of invention directly related with it: one is " a kind of efficient asymmetric diffuser mating annular pumping chamber " (publication number: CN203067340U, 2013-07-17), the method mainly set forth by changing the angle between the diffuser adjacent blades of impeller rear improves efficiency and the stability of pump; Another is " asymmetric blade fan " (publication number: CN203297146U, 2013-11-20), is also to reduce eddy current between blade path and secondary flow by the angle changed between adjacent blades, and then reduces flabellum vibration noise.Above two patent formula Leaf blade profiles and the angle of pitch all do not change.In addition, in international monopoly net with " asymmetric blade " and " asymmetric blade " for keyword is retrieved, 2 are had to design directly related with propeller blade, United States Patent (USP) " Rotorwithasymmetricbladespacing (rotor of asymmetric blade arrangement; publication number: US2012/0288373A1; 2012.11) " and European patent " Asymmetricpreswirlstatorforship (the asymmetric stator before rotor of boats and ships; publication number: EP1955944A1,2008.08) " respectively.Wherein, patent " rotor of asymmetric blade arrangement " describes and changes circumferential angle between turbine rotor blade to suppress the design proposal of rotor leaf line spectrum noise peak frequently with certain rule, has certain enlightenment to the follow-up improvement of design proposal in this patent; Patent " the asymmetric preposition rotor of boats and ships " has been set forth at above water craft (mainly referring to civilian merchant ship) the asymmetrically distributed stator vane of installation left and right, tail undercarriage front string, essence be also the equal of by circumferential asymmetric arrangement stator before rotor adjacent blades between angle improve efficiency and the cavitation performance of screw propeller, mentality of designing there is certain similarity with design proposal of the present invention, but the technical measures specifically taked are different, and application is also different.Do not take as the above-mentioned technical measures enumerating angle between the change adjacent blades that adopts in patent in the application's design proposal, reason is: pump spray works in submarine afterbody, although because the existence of hull fairwater and the ship tail cross wing/Y-wing makes ship tail wake there is the feature of circumferential non-uniform Distribution, but the even degree of its circumferential asymmetry will be significantly less than aforementioned merchant ship potential wake, the drop shape of hull itself makes wake port and starboard difference also little, in this situation by the angle changed between stator before rotor adjacent blades come lift pump spray advance and the space of noiseproof feature very little.In follow-up study, these technical measures can be attempted to combine with the technical measures taked in design proposal of the present invention, play its noise-reducing design effect better.
As can be seen from above-mentioned research background and application present situation, spray the combined propeller of this complexity for pump, adopt the design proposal of stator before rotor circumference asymmetric arrangement to carry out noise reduction, open the approach that pump spray one of noise-reducing design is new.These technical measures be both applicable to routine the modelling of axle mechanical type pump water spray power, also the design of novel shaftless driving integrate motor formula pump spray hydraulic model is applicable to, effectively can fill up the lacuna of this application domestic, promote the independent research of domestic latent device propelling Low noise pump spray effectively and apply.
Summary of the invention
The object of the invention is to reduce pump spray radiated noise further, on the basis of original pump spray hydraulic model, by changing the angle of pitch of stator vane regularly, pump spray hydraulic model and the method for designing thereof of a kind of stator before rotor circumference asymmetric arrangement are provided, ship tail circumference non-uniform wake can be adapted to better, reduce pump spray line spectrum noise.
For achieving the above object, the pump-jet propulsor hydraulic model of the stator before rotor circumference asymmetric arrangement of the present invention's design, it is characterized in that: comprise conduit, be provided with coaxial impeller and stator in described conduit, described stator is preposition, and described impeller is rearmounted; Described impeller comprises impeller blade and impeller hub, and described impeller blade is axially symmetrically fixed on impeller hub; Described stator comprises stator vane and stator wheel hub, described stator vane is fixed on stator wheel hub and stator vane blade tip is fixed on pipe inner wall face, angle between two adjacent described stator vanes is 360 °/n (n is the quantity of stator vane), and the stator vane angle of pitch adjusts according to the following equation:
In formula: α
0be the angle of pitch of stator vane in benchmark pump spray hydraulic model, determined by the parametrization ternary reverse engineer of stator three-dimensional geometry;
A is amplitude coefficient, gets the integer between 1 to 9, and unit is degree;
N is the sequence numbering of stator vane, and value is the integer between 1 to 12, and blade sequence is numbered to increase progressively and completed in the direction of the clock, consistent with impeller clockwise direction, and N value difference describes the difference of circumference angle position, blade place.
The stator before rotor blade of pump spray adopts circumferential asymmetric arrangement form, and the angle of pitch of each stator vane is different.From the first direction of ship Caudad ship, the change of each stator vane angle of pitch has rotated a certain angle by around the line through stator wheel hub axis centre and this stator vane blade root cross section chord length mid point, and this rotation angle tolerance is the variable pitch amount changed by sinusoidal rule.The positive and negative value of variable pitch amount is relevant to the sense of rotation of circumference angle position, blade place and impeller blade.The stator vane angle of pitch is defined as the acute angle formed between stator vane leaf cross section chord length and the square section in direction perpendicular to axial direction.During impeller dextrorotation, the stator vane angle of pitch in right string space reduces relative to the reference vanes angle of pitch, and the stator vane angle of pitch in port space increases relative to the reference vanes angle of pitch; Otherwise stator vane angle of pitch during impeller left string in port space reduces relative to the reference vanes angle of pitch, and the stator vane angle of pitch in starboard space increases relative to the reference vanes angle of pitch.The direct impact of this arrangement is axial pulsating force amplitude when not only can reduce pump spray work, pump is suppressed to spray line spectrum noise peak and weaken the influence degree of vane rotary direction to pump spray sound directive property with this, and additional side can be produced to moment, be of value to the lifting of hull maneuvering performance.
Preferably, the number of sheets of described stator vane is 12 leaves, and the number of sheets of described impeller blade is 9 leaves or 7 leaves.Like this, circumferential angle between adjacent two panels stator vane is 30 degree, sequence numbering be 1 stator vane be positioned at 15 degree of angles, sequence numbering be 12 stator vane be positioned at 345 degree of angles, hull fairwater and upper vertical stabilizer wake flow from sequence numbering be 1 and sequence numbering be 12 stator vane between passage flow through, stator vane sequence numbering increases progressively and completes in the direction of the clock, consistent with impeller clockwise direction.During impeller dextrorotation, expression formula is:
in dextrorotation space, sequence numbering is the angle of pitch reduction of the stator vane of 1 to 6, and in left-handed space, sequence numbering is the angle of pitch increase of the stator vane of 7 to 12; Otherwise when impeller is left-handed, expression formula is
in dextrorotation space, sequence numbering is the angle of pitch increase of the stator vane of 1 to 6, and in left-handed space, sequence numbering is the angle of pitch reduction of the stator vane of 7 to 12.
Preferably, blade tip clearance is provided with between the blade tip cross section of described impeller blade and pipe inner wall face.
Preferred further, the ratio of described blade tip clearance and impeller diameter is taken as 2 ~ 5 ‰ depending on machining precision.
Preferably, impeller blade skew angle is greater than the half of angle between adjacent impeller blade; Impeller blade is from blade root to blade tip cross section, and different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases.
Preferred further, impeller blade is from blade root to blade tip cross section, and skew angle increases by given rule, and the skew angle mathematic(al) representation of different radii section is:
Wherein, θ
smaxblade tip sectional side oblique angle, for describing the skew angle of impeller blade; r
hbe impeller hub radius, R is impeller radius, and r is arbitrary section radius on impeller blade, θ
sit is the skew angle of radius r section.
Preferably, stator vane and impeller blade all adopt NACA16 profile thickness to distribute.
Preferably, the cross section profile of the inside and outside wall of described conduit is aerofoil profile.
The pump-jet propulsor hydraulic model method for designing of the stator before rotor circumference asymmetric arrangement of the present invention's design, comprises the following steps:
One) Selection and Design of pump fluid passage hydraulic parameters is carried out according to designing requirement;
Two) the two-dimentional axis plane projection geometry of wall inside and outside pump spray stator before rotor, rearmounted impeller and conduit is determined;
Three) by step one) and step 2) acquired results adopts the 3 dimensional coil geometry of parametrization ternary Reverse Design determination stator, impeller; By step one) and step 2) the two-dimentional axis plane projection geometry of conduit rotates and obtain conduit 3 dimensional coil geometry by acquired results vertically;
Four) Fluid Mechanics Computation method calculation procedure three is adopted) hydrodynamic performance of gained model pump spray under design speed, rotating speed and wake condition and cavitation performance, judge whether pump spray axial thrust, consumed power, propulsive efficiency and cavitation performance meet design requirement: if so, then carry out next step; If not, then get back to step 2) revise corresponding two-dimentional axis plane projection geometry, and adjust stator and the blade surface load distribution rule of impeller in ternary reverse engineer process, redesign stator and impeller 3 dimensional coil geometry;
Five) the large skew back of impeller blade and laden by the stern feature is introduced: make impeller blade skew angle be greater than the half of angle between adjacent blades, and impeller blade is from blade root to blade tip cross section, different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases;
Six) Fluid Mechanics Computation method calculation procedure five is adopted) the large skew back pump spray under design speed, rotating speed and wake condition of gained model pulses thrust coefficient obtain line spectrum noise, judge whether pump spray line spectrum noise meets design requirement: if so, then carry out next step; If not, then step 5 is got back to) increase impeller blade skew back and trim degree, increase the axial distance of stator and impeller;
Seven) angle of pitch of stator vane is adjusted according to circumference angle position, stator vane place, impeller rotation direction and amplitude coefficient;
Eight) Fluid Mechanics Computation method calculation procedure seven is adopted) thrust coefficient of gained model under wake condition forecast obtains line spectrum noise;
Nine) the pump-jet propulsor hydraulic model of preposition circumferential asymmetric arrangement is determined.
Preferably, described step one) in hydraulic parameters comprise lift, flow, discharge area, specific speed and suction inlet specific speed 5 parameters.
Preferably, described step 2) in two-dimentional axis plane projection geometry comprise the axis plane projection of conduit, stator before rotor and rearmounted impeller.
Preferably, described step 3) in design stator vane and impeller blade 3 dimensional coil geometry time: stator vane lagging edge adopts increment type swirl distribution, impeller blade guide margin to adopt quadratic power swirl distribution; Carry type load distribution during the blade root cross section of stator vane and impeller blade all adopts, blade tip cross section carries type load distribution before all adopting; Guide margin place, stator vane blade root cross section adopts little positive incidence, and lagging edge place, impeller blade blade tip cross section adopts little negative angle of attack.Blade (stator vane and impeller blade) 3 dimensional coil geometry is determined jointly by hydrodynamic parameter (blade load distributes and outlet circulation distributes) and geometric parameter (axial plane geometry, leaf section thickness distribute and stacking angle).
Preferably, described step 6) in assessment pump spray radiated noise reducing amount time pump can be adopted to spray pulsation axial thrust coefficient parameter.
Preferred further, pulsation thrust coefficient calculates and adopts unsteady flo w transient state CFD computing method.
Further preferred, pulsation thrust coefficient calculates and adopts yardstick to adapt to analogy method SAS or separated vorticcs analogy method DES or Large eddy simulation method LES.Preferential employing SAS simulates, and effectively can shorten computation period under the condition ensureing pulsating force amplitude forecast precision.
The invention has the beneficial effects as follows: the present invention has axle drive-type pump to spray on the basis of hydraulic model in routine, by changing the angle of pitch of stator before rotor blade regularly, developing the pump spray hydraulic model having drawn stator before rotor blade circumference asymmetric arrangement.Spray hydraulic model with benchmark pump to compare, the method for designing that blade three-dimensional geometry adopts and rapidoprint all do not change, and are easy to expansion.In design pump spray hydraulic model, stator vane number is 12 leaves, and impeller blade number is 9 leaves or 7 leaves, and catheter section profile is aerofoil profile.Stator vane and impeller blade all adopt NACA16 profile thickness distribution characteristics.Impeller blade has large skew back and laden by the stern feature.Design pump is sprayed on that the specified speed of a ship or plane 16 saves, under rated speed 200rpm, spacious water efficiency is 0.59, produce under ship tail wake condition that axial thrust is greater than 300kN, consumed power is less than 3.15MW, when the depth of water is greater than 30 meters, non-cavitating produces, the pump spray reduction 3.4% that be arranged symmetrically with more circumferential than benchmark of axial pulse thrust coefficient, can also obtain the lifting by a small margin of maneuvering performance while reducing low frequency spectrum lines noise.The technical measures adopted in this design proposal are also applicable to the noise optimization design of shaftless drive-type integrated electric pump water spray power model, and these technical measures can promote after applying that pump sprays the popularization and application of Push Technology fast.
Accompanying drawing explanation
Fig. 1 is the pump spray hydraulic model 3 dimensional coil geometry of the stator before rotor circumference asymmetric arrangement of the embodiment of the present invention;
The non-homogeneous nominal wake of ship tail circumference residing when Fig. 2 is the pump spray work of embodiment of the present invention stator before rotor circumference asymmetric arrangement;
Fig. 3 is the relative position figure before stator before rotor blade pitch angle changes in the pump spray of embodiment of the present invention stator before rotor circumference asymmetric arrangement and between the non-homogeneous nominal wake of ship tail circumference;
Fig. 4 is stator before rotor blade pitch angle definition figure in the pump spray of embodiment of the present invention stator before rotor circumference asymmetric arrangement;
Fig. 5 is stator vane angle of pitch distribution plan in the pump spray of embodiment of the present invention stator before rotor circumference asymmetric arrangement;
Fig. 6 is that the pump spray of embodiment of the present invention stator before rotor circumference asymmetric arrangement sprays three-dimensional geometry comparison diagram with the circumferential pump be arranged symmetrically with of benchmark; Wherein, light color is expressed as the stator before rotor blade that benchmark circumference is arranged symmetrically with, and dark color is expressed as the pump spray stator before rotor blade of circumferential asymmetric arrangement;
Fig. 7 is the pump water spray power modelling process flow diagram of embodiment of the present invention stator before rotor circumference asymmetric arrangement.
Embodiment
Below by Fig. 1 ~ Fig. 7 and the mode enumerating embodiment more of the present invention; be described in further detail technical scheme of the present invention (comprising optimal technical scheme), any technical characteristic in the present embodiment and any technical scheme all do not limit the scope of the invention.
The present invention design stator before rotor circumference asymmetric arrangement pump-jet propulsor hydraulic model method for designing process flow diagram as shown in Figure 7,
Step S1, carries out the Selection and Design of pump fluid passage hydraulic parameters according to designing requirement;
During Selection and Design, theoretical according to boats and ships hydraulic jet propulsion, spray the lift of blade grid passage, flow, discharge area, specific speed and suction inlet specific speed parameter 5 parameters by rapidity requirement determination pump.
Step S2, determines the two-dimentional axis plane projection geometry of wall inside and outside pump spray stator before rotor, rearmounted impeller and conduit; Two dimension axis plane projection geometry comprises the axis plane projection of blade (stator vane and impeller blade) guide margin and lagging edge, blade tip and blade root cross section, the inside and outside wall of conduit.
Step S3, is adopted the 3 dimensional coil geometry of parametrization ternary Reverse Design determination stator, impeller by step S1 and step S2 acquired results; By step S1 and step S2 acquired results the two-dimentional axis plane projection geometry of conduit rotated vertically and obtain conduit 3 dimensional coil geometry;
Blade (stator vane and impeller blade) 3 dimensional coil geometry is determined jointly by hydrodynamic parameter (blade load distributes and outlet circulation distributes) and geometric parameter (axial plane geometry, leaf section thickness distribute and stacking angle).Blade load distribution determines the distribution of leaf sectional pressure coefficient along chord length direction, and then directly determines its capacity for work and anti-cavitation performance; Outlet circulation distribution for controlling the secondary flow of impeller blade in the capacity for work and stator before rotor blade in span direction, and then improves the interaction flow field between stator before rotor and impeller, improves work doing efficiency.Stator before rotor blade exit circular rector is equal with impeller blade import circular rector.Blade face load (pressure differential between blade face pressure face and suction surface) and circumferentially average circular rector rV
tderivative on meridian streamline direction is closely related, and mathematical model is,
In formula, ρ is the density of seawater; R is arbitrary section radius on impeller blade; V
mbe circumferentially average axis plane velocity, equal the ratio of the flow area corresponding with diameter in axis projection; V
tbe circumferentially average tangential speed component, equal circular rector rV
tbe worth the ratio with radius in axis projection, circular rector rV
tbe worth and determined by lift and rotating speed,
η
hfor hydraulic efficiency, during design, initial value is taken as 0.92; p
+, p
-be the static pressure of blade pressure surface and suction surface respectively, both differences equal blade and produce thrust; B is the number of blade, empirically given, as stator vane 12 leaf, impeller blade 9 leaf or 7 leaves; M is dimensionless meridian streamline length, and being blade different span places geometric parameters, is 0 to 1 from vane inlet to outlet value.
When designing stator vane and impeller blade 3 dimensional coil geometry: stator vane lagging edge adopts increment type swirl distribution, impeller blade guide margin to adopt quadratic power swirl distribution; Carry type load distribution during the blade root cross section of stator vane and impeller blade all adopts, blade tip cross section carries type load distribution before all adopting; Guide margin place, stator vane blade root cross section adopts little positive incidence, and lagging edge place, impeller blade blade tip cross section adopts little negative angle of attack.
Step S4, adopt hydrodynamic performance and the cavitation performance of the pump spray under design speed, rotating speed and wake condition of Fluid Mechanics Computation method calculation procedure S3 gained model, judge whether pump spray axial thrust, consumed power, propulsive efficiency and cavitation performance meet design requirement: if so, then carry out next step; If not, then get back to step S2 and revise corresponding two-dimentional axis plane projection geometry, and adjust stator and the blade surface load distribution rule of impeller in ternary reverse engineer process, redesign stator and impeller 3 dimensional coil geometry;
Step S5, introduce the large skew back of impeller blade and laden by the stern feature: make impeller blade skew angle be greater than the half of angle between adjacent blades, and impeller blade is from blade root to blade tip cross section, different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases;
In the pump spray hydraulic model of stator before rotor circumference asymmetric arrangement, impeller blade has large skew back and laden by the stern feature indication is: impeller blade skew angle is greater than the half of angle between adjacent blades, and in the present embodiment, skew angle is taken as 30 degree, and skew back degree is 75%.Impeller blade is from blade root to blade tip cross section, and skew angle increases by given rule, and the skew angle mathematic(al) representation of different radii section is:
Wherein, θ
smaxbeing blade tip sectional side oblique angle, for describing the skew angle of impeller blade, in the present embodiment, being taken as 30 degree; r
hbe impeller hub radius, R is impeller radius, and r is arbitrary section radius on impeller blade, θ
sit is the skew angle of radius r section.Impeller blade is from blade root to blade tip cross section, and different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases, and in the present embodiment, the ratio of blade tip cross section trim value and impeller radius is 3/16.
Step S6, Fluid Mechanics Computation method calculation procedure S5 gained model large skew back pump under design speed, rotating speed and wake condition is adopted to spray pulsation thrust coefficient and obtain line spectrum noise, judge whether pump spray line spectrum noise meets design requirement: if so, then carry out next step; If not, then the axial distance that step S5 increases impeller blade skew back and trim degree, increase stator and impeller is got back to;
Pump can be adopted to spray pulsation axial thrust coefficient parameter when assessing pump spray radiated noise reducing amount, pulsation thrust coefficient calculates and adopts unsteady flo w transient state CFD computing method.Yardstick is adopted to adapt to analogy method SAS or separated vorticcs analogy method DES or Large eddy simulation method LES as thrust coefficient of pulsing calculates.Preferential employing SAS simulates, and effectively can shorten computation period under the condition ensureing pulsating force amplitude forecast precision.
Step S7 adjusts the angle of pitch of stator vane according to circumference angle position, stator vane place, impeller rotation direction and amplitude coefficient;
As shown in Figure 4, the angle of pitch is defined as the angle of leaf cross section chord length and circumferential direction;
The adjustment of the stator vane angle of pitch changes by sinusoidal rule, and variable pitch amplitude and circumferential angle position, blade place, impeller rotation direction are relevant with amplitude coefficient.Advantageous variant rule is:
Wherein, α
0be the angle of pitch of stator vane in benchmark pump spray hydraulic model, determined by the parametrization ternary reverse engineer of stator three-dimensional geometry; A is amplitude coefficient, gets the integer between 1 to 9, and unit is degree; N is the sequence numbering of stator vane, and value is the integer between 1 to 12.Circumferential angle between adjacent two panels stator vane is 30 degree, serial number be 1 stator vane be positioned at 15 degree of angles, sequence numbering be 12 stator vane be positioned at 345 degree of angles, stator vane sequence numbering increases progressively and completes in the direction of the clock, consistent with impeller clockwise direction.N value difference describes the difference of stator wheel hub circumference angle position, stator vane place.During impeller dextrorotation, expression formula is
in dextrorotation space, sequence numbering is the angle of pitch reduction of the stator vane of 1 to 6, and in left-handed space, sequence numbering is the angle of pitch increase of the stator vane of 7 to 12; Otherwise when impeller is left-handed, expression formula is
in dextrorotation space, sequence numbering is the angle of pitch increase of the stator vane of 1 to 6, and the angle of pitch that left-handed spatial sequence is numbered the stator vane of 7 to 12 reduces.
As shown in Figure 2, in wake, cruciform Non-Uniform Flow district is that the viscous wake impact of hull fairwater and cruciform tail generates, and two " hump shape " Non-Uniform Flow districts above wake are that hull fairwater and captain boat body junction surface horse shoe vortex affect and formed;
As shown in Figure 3, sequence numbering be 1 stator vane be positioned at circumference 15 degree angles, sequence numbering be 12 stator vane be positioned at circumference 345 degree of angles, in ship tail wake, cruciform Non-Uniform Flow district and " hump shape " Non-Uniform Flow district are all positioned at stator vane passage;
As shown in Figure 5, when impeller is left-handed, the stator vane angle of pitch in port space reduces relative to angle of pitch reference value, and the stator vane angle of pitch in starboard space increases relative to angle of pitch reference value.
Step S8, adopts the thrust coefficient of Fluid Mechanics Computation method calculation procedure S7 gained model under wake condition also to forecast and obtains line spectrum noise;
Step S9, determines the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement.The model finally drawn as shown in Figure 1, wherein, the stator vane of sequence numbering 1 to 6 is positioned at starboard space, the stator vane of sequence numbering 7 to 12 is positioned at port space, stator vane sequence numbering corresponds to the angular interval of circumferential angle 15 degree to 345 degree, and between adjacent two stator vanes, angle is 30 degree.As shown in Figure 6, benchmark circumference the sequence numbering be arranged symmetrically with in the pump model of model and circumferential asymmetric arrangement be 1 and 7 stator vane overlap completely.
Again as shown in Figure 1, the pump-jet propulsor hydraulic model of the stator before rotor circumference asymmetric arrangement of the present invention's design, comprise conduit 5, be provided with coaxial impeller and stator in described conduit 5, described stator is preposition, and described impeller is rearmounted; Described impeller comprises impeller blade 3 and impeller hub 4, and described impeller blade 3 is axially symmetrically fixed on impeller hub 4; Described stator comprises stator vane 1 and stator wheel hub 2, described stator vane 1 is fixed on stator wheel hub 2 and stator vane 1 blade tip is fixed on conduit 5 internal face, angle between two adjacent described stator vanes 1 is 30 ° (360 °/12, in this example, the quantity of stator vane is 12), and stator vane 1 angle of pitch adjusts according to the following equation:
In formula: α
0be the angle of pitch of stator vane in benchmark pump spray hydraulic model, determined by the parametrization ternary reverse engineer of stator three-dimensional geometry;
A is amplitude coefficient, gets the integer between 1 to 9, and unit is degree;
N is the sequence numbering of stator vane, and value is the integer between 1 to 12, and blade sequence is numbered to increase progressively and completed in the direction of the clock, consistent with impeller clockwise direction, and N value difference describes the difference of circumference angle position, blade place.
The stator vane of pump spray adopts circumferential asymmetric arrangement form, and the angle of pitch of each stator vane is different.From the first direction of ship Caudad ship, the change of each stator vane angle of pitch has rotated a certain angle by around the line through stator wheel hub axis centre and this stator vane blade root cross section chord length mid point, and this rotation angle tolerance is the variable pitch amount changed by sinusoidal rule.The positive and negative value of variable pitch amount is relevant to the sense of rotation of circumference angle position, blade place and impeller blade.The stator vane angle of pitch is defined as the acute angle formed between stator vane leaf cross section chord length and the square section in direction perpendicular to axial direction.During impeller dextrorotation, the stator vane angle of pitch in right string space reduces relative to the reference vanes angle of pitch, and the stator vane angle of pitch in port space increases relative to the reference vanes angle of pitch; Otherwise stator vane angle of pitch during impeller left string in port space reduces relative to the reference vanes angle of pitch, and the stator vane angle of pitch in starboard space increases relative to the reference vanes angle of pitch.The direct impact of this arrangement is axial pulsating force amplitude when not only can reduce pump spray work, pump is suppressed to spray line spectrum noise peak and weaken the influence degree of vane rotary direction to pump spray sound directive property with this, and additional side can be produced to moment, be of value to the lifting of hull maneuvering performance.
Preferably, the number of sheets of described stator vane is 12 leaves, and the number of sheets of described impeller blade is 9 leaves or 7 leaves.Like this, circumferential angle between adjacent two panels stator vane is 30 degree, sequence numbering be 1 stator vane be positioned at 15 degree of angles, sequence numbering be 12 stator vane be positioned at 345 degree of angles, hull fairwater and upper vertical stabilizer wake flow from sequence numbering be 1 and sequence numbering be 12 stator vane between passage flow through, stator vane sequence numbering increases progressively and completes in the direction of the clock, consistent with impeller clockwise direction.During impeller dextrorotation, expression formula is:
in dextrorotation space, sequence numbering is the angle of pitch reduction of the stator vane of 1 to 6, and in left-handed space, sequence numbering is the angle of pitch increase of the stator vane of 7 to 12; Otherwise when impeller is left-handed, expression formula is
in dextrorotation space, sequence numbering is the angle of pitch increase of the stator vane of 1 to 6, and in left-handed space, sequence numbering is the angle of pitch reduction of the stator vane of 7 to 12.
Preferably, blade tip clearance is provided with between the blade tip cross section of described impeller blade 3 and conduit 5 internal face.In this example, the ratio of described blade tip clearance and impeller diameter is 3 ‰.
Preferably, impeller blade 3 skew angle is greater than the half of angle between adjacent impeller blade 3; Impeller blade 3 is from blade root to blade tip cross section, and different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases.
Preferred further, impeller blade 3 is from blade root to blade tip cross section, and skew angle increases by given rule, and the skew angle mathematic(al) representation of different radii section is:
Wherein, θ
smaxblade tip sectional side oblique angle, for describing the skew angle of impeller blade; r
hbe impeller hub radius, R is impeller radius, and r is arbitrary section radius on impeller blade, θ
sit is the skew angle of radius r section.
Preferably, stator vane and impeller blade all adopt NACA16 profile thickness to distribute.
Preferably, the cross section profile of the inside and outside wall of described conduit 5 is aerofoil profile.
Claims (10)
1. a pump-jet propulsor hydraulic model for stator before rotor circumference asymmetric arrangement, it is characterized in that: comprise conduit, be provided with coaxial impeller and stator in described conduit, described stator is preposition, and described impeller is rearmounted; Described impeller comprises impeller blade and impeller hub, and described impeller blade is axially symmetrically fixed on impeller hub; Described stator comprises stator vane and stator wheel hub, described stator vane is fixed on stator wheel hub and stator vane blade tip is fixed on pipe inner wall face, angle between two adjacent described stator vanes is 360 °/n (n is the quantity of stator vane), and the stator vane angle of pitch adjusts according to the following equation:
In formula: α
0be the angle of pitch of stator vane in benchmark pump spray hydraulic model, determined by the parametrization ternary reverse engineer of stator three-dimensional geometry;
A is amplitude coefficient, gets the integer between 1 to 9, and unit is degree;
N is the sequence numbering of stator vane, and value is the integer between 1 to 12, and blade sequence is numbered to increase progressively and completed in the direction of the clock, consistent with impeller clockwise direction, and N value difference describes the difference of circumference angle position, blade place.
2. the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement according to claim 1, it is characterized in that: the number of sheets of described stator vane is 12 leaves, the number of sheets of described impeller blade is 9 leaves or 7 leaves.
3. the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement according to claim 1, it is characterized in that: be provided with blade tip clearance between the blade tip cross section of described impeller blade and pipe inner wall face, the ratio of described blade tip clearance and impeller diameter is 2 ~ 5 ‰ depending on machining precision value.
4., according to the pump-jet propulsor hydraulic model of described stator before rotor circumference asymmetric arrangement arbitrary in claims 1 to 3, it is characterized in that: impeller blade skew angle is greater than the half of angle between adjacent impeller blade; Impeller blade is from blade root to blade tip cross section, and different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases.
5. the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement according to claim 4, is characterized in that: impeller blade is from blade root to blade tip cross section, and skew angle increases by given rule, and the skew angle mathematic(al) representation of different radii section is:
Wherein, θ
smaxblade tip sectional side oblique angle, for describing the skew angle of impeller blade; r
hbe impeller hub radius, R is impeller radius, and r is arbitrary section radius on impeller blade, θ
sit is the skew angle of radius r section.
6. the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement according to claim 1, is characterized in that: stator vane and impeller blade all adopt NACA16 profile thickness to distribute.
7. the pump-jet propulsor hydraulic model of stator before rotor circumference asymmetric arrangement according to claim 1, is characterized in that: the cross section profile of the inside and outside wall of described conduit is aerofoil profile.
8. the pump-jet propulsor hydraulic model method for designing of stator before rotor circumference asymmetric arrangement, comprises the following steps:
One) Selection and Design of pump fluid passage hydraulic parameters is carried out according to designing requirement;
Two) the two-dimentional axis plane projection geometry of wall inside and outside pump spray stator before rotor, rearmounted impeller and conduit is determined;
Three) by step one) and step 2) acquired results adopts the 3 dimensional coil geometry of parametrization ternary Reverse Design determination stator, rearmounted impeller; By step one) and step 2) the two-dimentional axis plane projection geometry of conduit rotates and obtain conduit 3 dimensional coil geometry by acquired results vertically;
Four) Fluid Mechanics Computation method calculation procedure three is adopted) hydrodynamic performance of gained model pump spray under design speed, rotating speed and wake condition and cavitation performance, judge whether pump spray axial thrust, consumed power, propulsive efficiency and cavitation performance meet design requirement: if so, then carry out next step; If not, then get back to step 2) revise corresponding two-dimentional axis plane projection geometry, and adjust stator and the blade surface load distribution rule of impeller in ternary reverse engineer process, redesign stator and impeller 3 dimensional coil geometry;
Five) the large skew back of impeller blade and laden by the stern feature is introduced: make impeller blade skew angle be greater than the half of angle between adjacent blades, and impeller blade is from blade root to blade tip cross section, different radii section guide margin is to ship tail direction trim, and trim distance linearly rule increases;
Six) Fluid Mechanics Computation method calculation procedure five is adopted) the large skew back pump spray under design speed, rotating speed and wake condition of gained model pulses thrust coefficient obtain line spectrum noise, judge whether pump spray line spectrum noise meets design requirement: if so, then carry out next step; If not, then step 5 is got back to) increase impeller blade skew back and trim degree, increase the axial distance of stator and impeller;
Seven) angle of pitch of stator vane is adjusted according to circumference angle position, stator vane place, impeller rotation direction and amplitude coefficient;
Eight) Fluid Mechanics Computation method calculation procedure seven is adopted) thrust coefficient of gained model under wake condition forecast obtains line spectrum noise;
Nine) the pump-jet propulsor hydraulic model of preposition circumferential asymmetric arrangement is determined.
9. the pump-jet propulsor hydraulic model method for designing of stator before rotor according to claim 8 circumference asymmetric arrangement, is characterized in that: described step 3) in design stator vane and impeller blade 3 dimensional coil geometry time: stator vane lagging edge adopts increment type swirl distribution, impeller blade guide margin to adopt quadratic power swirl distribution; Carry type load distribution during the blade root cross section of stator vane and impeller blade all adopts, blade tip cross section carries type load distribution before all adopting; Guide margin place, stator vane blade root cross section adopts little positive incidence, and lagging edge place, impeller blade blade tip cross section adopts little negative angle of attack.
10. the pump-jet propulsor hydraulic model method for designing of stator before rotor according to claim 8 circumference asymmetric arrangement, is characterized in that: described step 6) in assessment pump spray radiated noise reducing amount time pump can be adopted to spray pulsation axial thrust coefficient parameter.
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