CN106886630B - Pump jet propeller hydraulic model with shunting short blades and design method - Google Patents

Pump jet propeller hydraulic model with shunting short blades and design method Download PDF

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CN106886630B
CN106886630B CN201710030057.XA CN201710030057A CN106886630B CN 106886630 B CN106886630 B CN 106886630B CN 201710030057 A CN201710030057 A CN 201710030057A CN 106886630 B CN106886630 B CN 106886630B
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杨琼方
王永生
刘彦森
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Naval University of Engineering PLA
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Abstract

The invention discloses a pump-jet propeller hydraulic model with short shunting blades and a design method. The thrust load proportion between the main blade and the short shunting blade of the impeller is 3: 2. the number of the short shunting blades is the same as that of the main blades, a single short blade is circumferentially positioned in the middle of two adjacent main blades, the axial position of the trailing edge of the short shunting blade is the same as that of the main blades, and the ratio of the average diameter of the leading edge to the diameter of the pump spray inlet is 0.63. The main blade and the short shunting blade of the impeller have large side inclination characteristics. The invention can delay the generation of cavitation bubbles, improve the anti-cavitation performance, reduce the radiation noise, and adapt to the working characteristics of small feed rate coefficient and easy generation of cavitation bubbles when the pump jet is used for an auxiliary propeller. The technical measure is also suitable for the design of a hydraulic model when the shaftless drive type integrated motor pump spray is used as an auxiliary propeller.

Description

Pump jet propeller hydraulic model with shunting short blades and design method
Technical Field
The invention belongs to the technical field of ship propellers, and particularly relates to a pump jet propeller hydraulic model with a shunting short blade and a design method.
Background
Pump jet propellers (Pumpjet for short) are widely applied to low-noise submarine main propellers such as 'marine wolf-level' submarines and 'virginia-level' submarines due to the remarkable characteristics of low radiation noise and high critical navigational speed. The pump jet propulsion technology is applied to the main propulsion of the submarine in the United states, British, France and Russia in the world at present, and the main reason that the service of the pump jet propulsion submarine is not seen in China is the lack of an excellent pump jet hydraulic model. Excellent specific meanings are: low radiation noise, high critical navigational speed (namely strong anti-cavitation capability) and moderate propulsion efficiency. In order to achieve the independent design target, a design method suitable for both shaftless drive type integrated motor pump spraying and a conventional shafted mechanical pump spraying hydraulic model is set forth in a design method (CN 10446265A,2015-03-25) of a shaftless drive type integrated motor pump spraying propeller hydraulic model, a pump spraying propeller hydraulic model with a preposed stator arranged in a circumferential asymmetric manner and a design method (CN 105117564A, 2015-12-02) of the pump spraying propeller hydraulic model, and the pump spraying hydraulic model meeting propulsion and noise performance requirements at the same time can be designed. In the pump water-jet model, there are three common points: firstly, the impeller blades are all single-row cascade main blades, and the number of the impeller blades is 9 at most in consideration of the processing difficulty and the weight of the blades. Secondly, the pump jet is used as a main propeller, takes 16 sections of rated navigational speed as design working points, and has the physical characteristics of large diameter (generally more than 2 meters) and low rotating speed (less than 200 revolutions per minute); thirdly, the pump open water efficiency is more than 0.58, the design point forward speed coefficient is large, the section attack angle of the impeller blade is small, the critical primary cavitation index of the blade tip is small (usually less than 1.2), and the design requirement that no cavitation bubbles are generated when the submergence depth is more than 30 meters is relatively easily met.
When the pump jet is used as an auxiliary propeller of a submersible vehicle, the rotating speed of the auxiliary propulsion motor is obviously higher than that of a main propulsion motor (higher than 300 revolutions per minute) and the ship speed of a ship body is very low (less than 4 sections), so that the advancing speed coefficient is obviously reduced (usually less than 0.4), the section attack angle of a blade is increased, the critical primary cavitation index of a blade tip is increased (even can be more than 4), the probability of generating cavitation bubbles of an impeller blade is obviously improved, and the anti-cavitation performance is reduced (D. Ross, the underwater noise principle, the translation and the translation of the underwater noise principle, Beijing: ocean publishing Co., 1983), and the design difficulty of the blade is also obviously increased.
In the field of impeller machinery, in order to improve the anti-cavitation performance of impeller blades, under the condition that the radial size of an impeller, the power of a main engine and the rotating speed are limited, the following technical measures are typically adopted: increasing the number of blades to reduce the thrust load of unit blades; secondly, an inducer is added to improve the inlet pressure of the impeller blade; and thirdly, the hydrodynamic design of the impeller blade is optimized, and the blade tip section thrust load of the impeller blade is directly reduced. In the above measures, in the scheme, the weight of the impeller is directly increased by increasing the number of the blades, the friction loss of the fluid channel of the blades is also increased, and under the condition of the limitation of the density of the blade cascade, in order to avoid the overlarge twisting degree of the blades, the number of the blades sprayed by a large-scale pump (the diameter is more than 1 meter) is generally not more than 13 blades. In the second scheme, the inducer increases the axial length of pump spraying, so that the longitudinal bending moment of the stern is increased, and the counterweight is not favorable. And the efficiency is sacrificed to improve the anti-cavitation performance in a small amount by adjusting the radial distribution rule of the blade load of the impeller, and the optimization space of an impeller hydraulic model designed by a parameterized ternary reverse design method is small. Therefore, in order to solve the problems that cavitation performance is obviously reduced and the design difficulty of the blades is obviously increased when the pump jet is used as an auxiliary propeller of a submersible, on one hand, the improvement idea can be referred to, on the other hand, a new method can be developed, and the aim of improving the anti-cavitation performance is achieved by greatly reducing the thrust load of the impeller blades.
In the aspect of impeller design with short shunting blades, relevant literature reports published in China at present mainly focus on a centrifugal impeller and an axial flow fan, and the impeller is mainly used for reducing loss, improving efficiency and reducing noise.
From the research background and the application current situation, aiming at the cascade channel with the typical axial flow characteristic, such as a pump impeller, the anti-cavitation performance is improved by adopting the short shunting blades, so that the method is completely feasible in theory, and a new way for designing the blades of the high-performance ship pump propeller is opened in technical application. The technical measure can effectively solve the problem that the cavitation performance is difficult to meet the requirement due to the small working point advance speed coefficient when the pump jet is used as an underwater auxiliary propeller, is suitable for the design of a conventional mechanical type pump jet hydraulic model with a shaft and also suitable for the design of a novel integrated motor type pump jet hydraulic model without shaft driving, can effectively fill the defect of the application field in China, and can effectively promote the independent research, development and popularization and application of the pump jet for auxiliary propulsion with excellent cavitation resistance of the submersible vehicle in China.
The invention content is as follows:
in order to overcome the defects of the background technology, the invention provides a hydraulic model of a pump jet propeller with a shunting short blade and a design method.
In order to solve the technical problems, the invention adopts the technical scheme that:
a pump spray propeller hydraulic model with short shunting blades comprises a guide pipe, wherein a front impeller and a rear stator are coaxially arranged in the guide pipe, the impeller comprises an impeller hub, and an impeller main blade and a short shunting blade which are uniformly arranged along the circumferential direction of the impeller hub, and the impeller main blade and the short shunting blade are provided with side oblique angles; the stator comprises a stator hub and stator blades, wherein the stator hub is coaxial with the impeller hub, the stator blades are uniformly arranged along the circumferential direction of the stator hub, and blade tips of the stator blades are connected with the inner wall surface of the guide pipe.
Preferably, the ratio of the average diameter of the guide edge of the short shunting blade to the diameter of the inlet of the pump-jet propeller is more than 0.5, and the axial positions of the trailing edge of the short shunting blade and the trailing edge of the main blade of the impeller are the same; the degree of lateral inclination of the lateral inclination angle is not less than 50%.
Preferably, the blade tip section of the impeller main blade and the blade tip section of the short shunting blade and the inner wall surface of the guide pipe have the same blade tip clearance, and the blade tip clearance is 2-5 per mill of the diameter of the impeller.
Preferably, the side bevel angle of the main blade of the impeller is the same as the side bevel angle of each short shunting blade; the side oblique angle of the main impeller blade is larger than half of the included angle between the adjacent main impeller blades, and the side oblique angle of the short shunting blade is larger than half of the included angle between the adjacent short shunting blades; the side bevel angle of the impeller main blade and the side bevel angle of the short shunting blade are increased from the blade root to the blade tip section according to a linear rule.
Preferably, the duct comprises a zero thrust and a low thrust duct, the cross-sectional profile of the inner and outer wall surfaces of the duct forming a fat-type duct.
Preferably, the blade numbers of the main blades of the impeller and the short shunting blades are the same, and the blade numbers of the main blades of the impeller and the short shunting blades are both more than 5; the number of main blades of the impeller and the number of stator blades are prime to each other.
A design method of the hydraulic model of the pump-jet propeller with the short shunting blades comprises the following steps:
step 1, carrying out model selection design on hydraulic parameters of a pump fluid channel according to design requirements;
step 2, determining two-dimensional axial plane projection geometry of the pump spraying front impeller, the rear stator and the inner and outer wall surfaces of the guide pipe;
step 3, determining the three-dimensional geometric shapes of the impeller and the stator by adopting a parameterized ternary reverse design method according to the results obtained in the step 1 and the step 2; rotating the two-dimensional axial plane projection geometry of the catheter along the circumferential direction according to the results obtained in the step 1 and the step 2 to obtain the three-dimensional geometry of the catheter;
step 4, enabling the main impeller blade and the short shunting blade to have side oblique angles, wherein the side oblique angles of the main impeller blade and the short shunting blade are the same;
step 5, calculating the hydrodynamic performance under the set condition of the model obtained in the step 4, judging whether the design is met, and if so, entering the step 6; if not, returning to the step 2 to modify the two-dimensional axial plane projection geometry, adjusting the blade surface load distribution rules of the main blades and the stator blades of the impeller in the ternary reverse design process in the step 3 along the radial direction and the axial direction, and redesigning the three-dimensional geometric shapes of the impeller and the stator;
step 6, calculating the cavitation performance of the pump jet of the model obtained in the step 5 under the conditions of given submergence depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, and judging whether the pump jet blade is in a non-cavitation state or a cavitation state: if the device is in a non-cavitation state, entering a step 7; if the blade is in the cavitation initial state, returning to the step 3 to adjust the blade surface load distribution rule of the main blade and the shunting short blade of the impeller in the ternary reverse design process along the axial direction; if the rotor is in a severe cavitation state, returning to the step 2 to modify the corresponding two-dimensional axial plane projection geometry, adjusting the radial distribution rule of the annular quantity of the trailing edge of the main blade and the leading edge of the stator blade of the impeller in the step 3, and redesigning the three-dimensional geometric shapes of the impeller and the stator;
and 7, calculating the unsteady propulsion performance of the pump jet of the model obtained in the step 6 under the conditions of given depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, solving the pulsating thrust coefficient of the pump jet with the shunt short blades, calculating line spectrum noise by a theoretical formula, and judging whether the line spectrum noise of the pump jet meets the design requirement or not: if yes, entering step 8; if not, returning to the step 2 to increase the axial distance between the main blade and the stator blade of the impeller;
and 8, determining a hydraulic model of the pump jet propeller with the shunting short blades.
Preferably, the axial distance between the main blades and the stator blades of the impeller in step 2 is greater than 0.5 times the chord length of the main blades.
Preferably, the main blades, the splitter blades and the stator blades of the impeller in the step 3 adopt NACA16 airfoil thickness distribution.
Preferably, in step 4, the side bevel angle of the main blade of the impeller is larger than half of the included angle between the adjacent main blades of the impeller, and the side bevel angle of the short shunting blade is larger than half of the included angle between the adjacent short shunting blades, so that the side bevel angles of the main blade of the impeller and the short shunting blades are increased from the blade root to the blade tip section according to a linear rule.
Preferably, the modifying the two-dimensional axial plane projection geometry in step 5 comprises: and modifying the diameter and the axial length of the main blade of the impeller in the two-dimensional axial plane projection geometry.
Preferably, the modifying the two-dimensional axial plane projection geometry in step 6 comprises: and modifying the axial position of the guide edge of the main blade of the impeller and the section chord length of the blade tip in the two-dimensional axial plane projection geometry.
The invention has the beneficial effects that: on the basis of a conventional mechanical pump jet hydraulic model, the rear stator pump jet propeller hydraulic model with the short shunting blades is obtained by introducing the short shunting blades, and the rear stator pump jet propeller hydraulic model is suitable for the characteristics of small working point speed coefficient and high cavitation resistance requirement when the pump jet is used as an auxiliary propeller. The number of blades of a main impeller blade and a short shunting blade in a designed pump spraying hydraulic model is 7, the number of stator blades is 9, and a guide pipe is a low-thrust fat-thick guide pipe. The main blade, the short splitter blade and the stator blade of the impeller all adopt the NACA16 airfoil thickness distribution characteristic. The main blade and the short shunting blade of the impeller have large side inclination characteristics, and the side inclination angles are the same. The pump jet is designed to be at a rated navigational speed of 4 sections and a rated rotational speed of 300rpm, the open water efficiency is 0.28, the axial thrust generated under the inflow condition of the ship tail boundary layer is greater than 37kN, the consumed power is less than 250kW, no cavitation is generated when the water depth is greater than 10 m, and the spectral noise of the pump jet at the first-order blade frequency corresponding to the axial pulsation thrust coefficient is lower than 125 dB. The technical measures adopted in the design scheme are also suitable for the design of the hydraulic model when the shaftless drive type integrated motor pump spray is used as an auxiliary propeller, and the popularization and the application of the pump spray auxiliary propulsion technology can be quickly promoted after the technical measures are popularized and applied.
Drawings
FIG. 1 is a three-dimensional geometric shape of a post-stator pump hydraulic power spraying model with a shunting short blade according to an embodiment of the invention;
FIG. 2 is a two-dimensional axial plane projection geometry of a post-stator pump hydraulic power spraying model with a shunting short blade according to an embodiment of the invention;
FIG. 3 is a flow chart of the design of a post-stator pump water-spraying power model with a shunting short blade according to the embodiment of the invention.
Detailed Description
The invention is further described below with reference to the accompanying drawings and examples.
A pump-jet propeller hydraulic model with short shunting blades 2 comprises a guide pipe 6 as shown in figure 1, wherein a front impeller and a rear stator are coaxially arranged in the guide pipe 6, the impeller comprises an impeller hub 3, and an impeller main blade 1 and a short shunting blade 2 which are uniformly arranged along the circumferential direction of the impeller hub 3, the impeller main blade 1 and the short shunting blade 2 have side oblique angles, and the side oblique degree of the side oblique angles is 50%; the stator comprises a stator hub 5 coaxially arranged with the impeller hub 3, and stator blades 4 uniformly arranged along the circumferential direction of the stator hub 5, and the blade tips of the stator blades 4 are connected with the inner wall surface 14 of the guide pipe 6. The main impeller blades 1, the short splitter blades 2 and the stator blades 4 are all distributed in the thickness of an NACA16 airfoil.
The duct 6 is a zero thrust duct 6 or a small thrust duct 6, and the cross-sectional profiles of the inner wall surface 14 and the outer wall surface 15 form a fat-thickness duct 6. The duct 6 in this embodiment is a low thrust duct 6.
The ratio of the average diameter of the leading edge 8 of the splitter stub blade 2 to the diameter of the pump jet inlet is greater than 0.5, preferably 0.63 in this embodiment. The axial positions of the trailing edge 9 of the short shunting blade 2 and the trailing edge 9 of the main blade 1 of the impeller are the same.
The blade tip section of the impeller main blade 1 and the blade tip section of the short shunting blade 2 have the same blade tip gap with the inner wall surface 14 of the guide pipe 6, and the blade tip gap is 2-5 per mill of the diameter of the impeller.
The side bevel angle of the main impeller blade 1 is the same as that of the short shunting blade 2; the side oblique angle of the impeller main blade 1 is larger than half of the included angle between the adjacent impeller main blades 1, and the side oblique angle of the short shunting blade 2 is larger than half of the included angle between the adjacent short shunting blades 2; the side bevel angle of the impeller main blade 1 and the side bevel angle of the shunting short blade 2 increase from the blade root to the blade tip section according to a linear rule.
The blade numbers of the impeller main blades 1 and the shunting short blades 2 are the same, and the blade numbers of the impeller main blades 1 and the shunting short blades 2 are both more than 5; the number of blades of the impeller main blades 1 and the number of blades of the stator blades 4 are relatively prime. In this embodiment, the number of the main blades 1 and the number of the short splitter blades 2 of the impeller are both 7, and the number of the stator blades 4 is 9.
A design method of the hydraulic model of the pump-jet propeller with the short shunting blades 2 comprises the following steps:
step 1, carrying out model selection design on hydraulic parameters of a pump fluid channel according to design requirements; during model selection design, 5 parameters of the pump spray blade grid channel, such as lift, flow, outlet area, specific rotating speed and suction inlet specific rotating speed, are determined according to the ship water jet propulsion theory and the rapidity requirement.
Step 2, determining two-dimensional axial plane projection geometry of the pump spraying front impeller, the rear stator, the inner wall surface 14 and the outer wall surface 15 of the guide pipe 6; the section profiles of the inner wall surface 14 and the outer wall surface 15 of the conduit 6 in the post-stator pump spraying hydraulic model with the shunting short blades 2 form a fat-thick conduit 6, which means that: the ratio of the radial thickness of the conduit 6 in the axial direction to the maximum thickness is greater than 0.8 and the ratio of the axial length of the conduit 6 to the total axial length is greater than 0.5.
As shown in fig. 2, the two-dimensional axial projection geometry includes axial projections of the main blade leading edge 7, the splitter short blade leading edge 8, the main blade trailing edge 9, the impeller hub 10, the stator blade leading edges 11 and trailing edges 12, the stator hub 13, the inner wall surface 14 and the outer wall surface 15 of the duct 6. The trailing edge of the short shunting blade 2 coincides with the axial plane projection of the trailing edge 9 of the main blade. Blade tip sections of the impeller main blade 1 and the flow dividing short blade 2 are provided with blade tip gaps from the inner wall surface 14 of the guide pipe 6, and the gap distances are equal. The ratio of the average diameter of the guide edge of the short splitter blade 2 to the diameter of the pump spray inlet is 0.63. The ratio of the axial distance from the leading edge of the stator blade 4 to the trailing edge 9 of the main blade 1 of the impeller to the chord length of the main blade is 0.75.
Step 3, determining the three-dimensional geometric shapes of the impeller and the stator by adopting a parameterized ternary reverse design method according to the results obtained in the step 1 and the step 2; rotating the two-dimensional axial plane projection geometry of the catheter 6 along the circumferential direction according to the results obtained in the step 1 and the step 2 to obtain the three-dimensional geometry of the catheter 6;
the three-dimensional geometrical shapes of the blades (the impeller main blade 1, the shunting short blade 2 and the stator blade 4) are jointly determined by hydraulic parameters (the load proportion of the main blade and the shunting short blade 2 and the distribution rule of the blade load along the radial direction and the axial direction) and geometrical parameters (the axial plane geometry, the blade section thickness distribution and the stacking angle). The load ratio of the main blade and the shunting short blade 2 determines the contribution of the main blade to the total thrust load; the distribution rule of the blade load along the axial direction determines the distribution of the pressure coefficient of the blade section along the chord length direction, and further directly determines the work capacity and the anti-cavitation performance of the blade; the blade load is distributed along the radial direction and is used for controlling the work capacity of the impeller main blade 1 and the shunting short blade 2 along the span direction and the secondary flow in the blade grid channel, so that the efficiency is improved. The blade thrust load (pressure difference between the pressure and suction faces of the blade face) is closely related to the derivative of the circumferentially averaged ring volume rVt in the axial streamlines direction, mathematically modeled as,
Figure GDA0001287652250000101
where ρ is the density of seawater; r is any section radius on the impeller blade; vmThe axial surface speed is averaged along the circumferential direction and is equal to the ratio of the flow to the area corresponding to the diameter in the axial surface projection drawing; vtIs the tangential velocity component averaged in the circumferential direction, equal to the ring vector rVtRatio of value to radius in axial projection view, ring quantity rVtThe value is determined by the head and the rotational speed,
Figure GDA0001287652250000102
ηhfor hydraulic efficiency, the initial value is 0.88 during design; p is a radical of+、p-The static pressures of the pressure surface and the suction surface of the blade are respectively, and the difference value of the static pressures is equal to the thrust generated by the blade; b is the number of blades, given empirically, such as main blade 1 and splitter stubThe blades 2 are 7 blades and 9 stator blades; and m is the length of a flow line of a non-dimensional axial surface, is a geometric parameter of different spans of the blade, and takes a value from 0 to 1 from the inlet to the outlet of the blade.
When the three-dimensional geometric shapes of the impeller main blade 1, the shunting short blade 2 and the stator blade 4 are designed: the following edge 9 of the impeller main blade 1 adopts incremental type circular distribution, the following edge 9 of the impeller shunt short blade 2 adopts incremental type circular distribution, and the guide edge of the stator blade 4 adopts quadratic circular distribution; the blade root sections of the main blade 1 and the stator blade 4 of the impeller adopt middle-load type load distribution, and the blade tip sections adopt rear-load type load distribution; the leading edge of the blade root section of the main blade 1 of the impeller adopts a small positive attack angle, and the trailing edge 12 of the blade tip section of the stator blade 4 adopts a small negative attack angle.
The ratio between the thrust loads of the main blades 1 and the short splitter blades 2 of the impeller in the embodiment is preferably 3: 2.
step 4, enabling the main impeller blade 1 and the short shunting blade 2 to have side oblique angles, namely enabling the main impeller blade 1 and the short shunting blade 2 to have a large side oblique characteristic, wherein the side oblique angles of the main impeller blade 1 and the short shunting blade 2 are the same, and the side oblique degree is 50%;
in the step, the side oblique angle of the impeller main blade 1 is larger than half of the included angle between the adjacent impeller main blades 1, and the side oblique angle of the short shunting blade 2 is larger than half of the included angle between the adjacent short shunting blades 2, so that the side oblique angle of the impeller main blade 1 and the short shunting blade 2 is increased from the blade root to the blade tip section according to a linear rule.
Step 5, calculating the hydrodynamic performance under the set condition of the model obtained in the step 4, judging whether the design is met, and if so, entering the step 6; if not, returning to the step 2 to modify the two-dimensional axial plane projection geometry, adjusting the blade surface load distribution rules of the main blades 1 and the stator blades 4 of the impeller in the ternary reverse design process in the step 3 along the radial direction and the axial direction, and redesigning the three-dimensional geometric shapes of the impeller and the stator; modifying the two-dimensional axial plane projection geometry in this step includes: the diameter and the axial length of the impeller main blade 1 in the two-dimensional axial plane projection geometry are modified.
Step 6, calculating the cavitation performance of the pump jet of the model obtained in the step 5 under the conditions of given submergence depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, and judging whether the pump jet blade is in a non-cavitation state or a cavitation state: if the device is in a non-cavitation state, entering a step 7; if the blade is in the cavitation initial state, returning to the step 3 to adjust the blade surface load distribution rule of the main blade 1 and the shunting short blade 2 of the impeller in the ternary reverse design process along the axial direction; if the rotor is in a severe cavitation state, returning to the step 2 to modify the corresponding two-dimensional axial plane projection geometry, adjusting the ring volume radial distribution rule of the trailing edge 9 of the main blade 1 and the leading edge 11 of the stator blade 4 of the impeller in the step 3, and redesigning the three-dimensional geometric shapes of the impeller and the stator; the step of modifying the two-dimensional axial plane projection geometry comprises the following steps: and modifying the axial position of the leading edge 7 of the main blade 1 of the impeller and the section chord length of the blade tip in the two-dimensional axial plane projection geometry.
When the pump jet cavitation performance is calculated, the cavitation model preferentially adopts an improved Sauer cavitation model provided by the inventor:
Figure GDA0001287652250000121
wherein the content of the first and second substances,
Figure GDA0001287652250000122
and
Figure GDA0001287652250000123
respectively representing the processes of water vapor evaporation (bubble growth) and condensation (bubble collapse), and respectively taking the evaporation coefficient and the condensation coefficient as Cprod50 and Cdest0.01, average initial radius of bubble RB＝1.5μm，αvAnd ρvRespectively representing the water vapour volume fraction and density, plDenotes the density of water, p denotes the fluid pressure, pvThe phase change critical pressure is expressed, and the value is as the formula (2) during calculation:
Figure GDA0001287652250000124
wherein p issatRepresenting the vaporization pressure constant, k representing the fluid turbulence energy, pmThe density of the mixed fluid is expressed, and the value is as the formula (3) during calculation:
ρm＝(αvρv+(1-αv-αg)ρl)/(1-fg) (3)，
wherein, αgAnd fgRespectively representing the volume fraction and the mass fraction of the non-condensable gas core NCG, and the value is αg＝7.8×10-4And fg＝1.0×10-6. For a three-phase mixed fluid composed of water, water vapor and NCG, the volume fraction and mass fraction of each phase satisfy the relation
Figure GDA0001287652250000131
In addition, when the pump jet cavitation performance is calculated, the Zwart model of the formula (4) can be used as the cavitation model
Figure GDA0001287652250000132
Wherein the content of the first and second substances,rnucis the volume fraction of the gas core,RBis the gas core radius, and the parameter value is rnuc＝5.0×10-4,RB＝2.0×10-6，Fe＝50，Fc＝0.01。
Mixed density ρ αvρv+(1-αv)ρl。
The cavitation performance calculation may also be performed using a Sauer model as in equation (5):
Figure GDA0001287652250000133
wherein the content of the first and second substances,
Figure GDA0001287652250000141
n0is a constant
And 7, calculating the unsteady propulsion performance of the pump jet of the model obtained in the step 6 under the conditions of given depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, solving the pulsating thrust coefficient of the pump jet with the shunting short blade 2, calculating line spectrum noise by a theoretical formula, and judging whether the line spectrum noise of the pump jet meets the design requirement or not: if yes, entering step 8; if not, returning to the step 2 to increase the axial distance between the main blade 1 and the stator blade 4 of the impeller; and calculating the pump jet pulsation thrust coefficient and evaluating line spectrum noise by adopting a scale adaptation simulation method SAS combined with a pulsation force radiation noise theoretical formula.
When the unsteady propulsion performance is calculated, an unsteady transient CFD calculation method is adopted, such as a scale adaptive simulation method SAS or a separation vortex simulation method DES or a macrovortex simulation method LES. SAS simulation is preferentially adopted, and the research and development period can be effectively shortened under the condition of improving the calculation accuracy of the pump jet pulsation thrust coefficient.
When calculating the noise of the pump spray line spectrum, the theoretical model as the formula (6) is adopted
Figure GDA0001287652250000142
Wherein p is sound pressure, t' is lag time, F is pulsating thrust, r is the distance from the pulse power source to a measuring point, theta is an included angle between vectors of F and r, and a cos theta term is used for representing the dipole sound field directivity of the pulse power source. Once the pulsating thrust magnitude is determined, the line spectrum noise spectrum source level is determined.
And 8, determining a hydraulic model of the pump jet propeller with the shunting short blades 2.
It will be understood that modifications and variations can be made by persons skilled in the art in light of the above teachings and all such modifications and variations are intended to be included within the scope of the invention as defined in the appended claims.

Claims (10)

1. The utility model provides a pump spray propeller hydraulic model of short blade of area reposition of redundant personnel, includes the pipe, be equipped with leading impeller and rearmounted stator in the pipe, its characterized in that: the impeller comprises an impeller hub, and impeller main blades and short shunting blades which are uniformly distributed along the circumferential direction of the impeller hub, wherein the impeller main blades and the short shunting blades have side oblique angles; the stator comprises a stator hub and stator blades, wherein the stator hub is coaxial with the impeller hub, the stator blades are uniformly distributed along the circumferential direction of the stator hub, and blade tips of the stator blades are connected with the inner wall surface of the guide pipe; the ratio of the average diameter of the guide edge of the short shunting blade to the diameter of the inlet of the pump-jet propeller is larger than 0.5, and blade tip sections of the main blade of the impeller and the short shunting blade have the same blade tip clearance with the inner wall surface of the guide pipe.
2. The hydraulic model of the pump jet propeller with the shunt short blades as claimed in claim 1, wherein: the trailing edge of the short shunting blade is the same as the axial position of the trailing edge of the main blade of the impeller.
3. The hydraulic model of the pump jet propeller with the shunt short blades as claimed in claim 1, wherein: the blade top gap is 2-5 per mill of the diameter of the impeller.
4. The hydraulic model of the pump jet propeller with the shunt short blades as claimed in claim 1, wherein: the side bevel angle of the main blade of the impeller is the same as that of the short shunting blade; the side oblique angle of the impeller main blade is larger than half of the included angle between the adjacent impeller main blades, and the side oblique angle of the short shunting blade is larger than half of the included angle between the adjacent short shunting blades; and the side bevel angle of the main blade of the impeller and the side bevel angle of the short shunting blade increase from the blade root to the blade tip section according to a linear rule.
5. The hydraulic model of the pump jet propeller with the shunt short blades as claimed in claim 1, wherein: the guide pipe comprises a zero-thrust guide pipe and a small-thrust guide pipe, and the cross section profiles of the inner wall surface and the outer wall surface of the guide pipe form a fat-thick guide pipe.
6. The hydraulic model of the pump jet propeller with the shunt short blades as claimed in claim 1, wherein: the blade numbers of the main impeller blades and the short shunting blades are the same, and the blade numbers of the main impeller blades and the short shunting blades are both more than 5; the number of the main blades of the impeller and the number of the stator blades are prime to each other.
7. A design method of a hydraulic model of a pump jet propeller with short shunting blades as claimed in any one of claims 1-5, which comprises the following steps:
step 1, carrying out model selection design on hydraulic parameters of a pump fluid channel according to design requirements;
step 2, determining two-dimensional axial plane projection geometry of the pump spraying front impeller, the rear stator and the inner and outer wall surfaces of the guide pipe;
step 3, determining the three-dimensional geometric shapes of the impeller and the stator by adopting a parameterized ternary reverse design method according to the results obtained in the step 1 and the step 2; rotating the two-dimensional axial plane projection geometry of the catheter along the circumferential direction according to the results obtained in the step 1 and the step 2 to obtain the three-dimensional geometry of the catheter;
step 4, enabling the main impeller blade and the short shunting blade to have side oblique angles, wherein the side oblique angles of the main impeller blade and the short shunting blade are the same;
step 5, calculating the model set navigational speed, the rotating speed and the hydrodynamic performance under the wake flow condition obtained in the step 4, judging whether the model set navigational speed, the rotating speed and the hydrodynamic performance meet the design requirements, and if so, entering the step 6; if not, returning to the step 2 to modify the two-dimensional axial plane projection geometry, adjusting the blade surface load distribution rules of the main blade and the stator blade of the impeller in the ternary reverse design process in the step 3 along the radial direction and the axial direction, and redesigning the three-dimensional geometric shapes of the impeller and the stator;
step 6, calculating the cavitation performance of the pump jet of the model obtained in the step 5 under the conditions of given submergence depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, and judging whether the pump jet blade is in a non-cavitation state or a cavitation state: if the device is in a non-cavitation state, entering a step 7; if the blade is in the cavitation initial state, returning to the step 3 to adjust the blade surface load distribution rule of the main blade and the shunting short blade of the impeller in the ternary reverse design process along the axial direction; if the rotor is in a severe cavitation state, returning to the step 2 to modify the corresponding two-dimensional axial plane projection geometry, adjusting the radial distribution rule of the annular quantity of the trailing edge of the main blade and the leading edge of the stator blade of the impeller in the step 3, and redesigning the three-dimensional geometric shapes of the impeller and the stator;
and 7, calculating the unsteady propulsion performance of the pump jet of the model obtained in the step 6 under the conditions of given depth, designed navigational speed, rotating speed and wake current by adopting a computational fluid mechanics method, solving the pulsating thrust coefficient of the pump jet with the shunt short blades, calculating line spectrum noise by a theoretical formula, and judging whether the line spectrum noise of the pump jet meets the design requirement or not: if yes, entering step 8; if not, returning to the step 2 to increase the axial distance between the main blade and the stator blade of the impeller;
and 8, determining a hydraulic model of the pump jet propeller with the shunting short blades.
8. The design method of the hydraulic model of the pump jet propeller with the shunting short blades as claimed in claim 7 is characterized in that: the rule of distribution of the surface load of the adjusting blade in the step 5 along the radial direction and the axial direction comprises the following steps: the load is distributed along the radial increasing type annular quantity and the quadratic annular quantity, the load is distributed along the axial middle load type and the axial rear load type,
and 4, enabling the side bevel angle of the impeller main blade to be larger than half of the included angle between the adjacent impeller main blades, and enabling the side bevel angle of the short shunting blade to be larger than half of the included angle between the adjacent short shunting blades, so that the side bevel angles of the impeller main blade and the short shunting blade are increased from the blade root to the blade tip section according to a linear rule.
9. The design method of hydraulic model of pump jet propeller with short shunting blades as claimed in claim 7, wherein said modifying the two-dimensional axial plane projection geometry in step 5 comprises: modifying the diameter and axial length of the main blade of the impeller in a two-dimensional axial plane projection geometry.
10. The design method of hydraulic model of pump jet propeller with short shunting blades as claimed in claim 7, wherein said modifying the two-dimensional axial plane projection geometry in step 6 comprises: and modifying the axial position of the guide edge of the main blade of the impeller and the section chord length of the blade tip in the two-dimensional axial plane projection geometry.
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