CN112648230B - High-efficiency cavitation-resistant centrifugal pump impeller - Google Patents
High-efficiency cavitation-resistant centrifugal pump impeller Download PDFInfo
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- CN112648230B CN112648230B CN202011192285.5A CN202011192285A CN112648230B CN 112648230 B CN112648230 B CN 112648230B CN 202011192285 A CN202011192285 A CN 202011192285A CN 112648230 B CN112648230 B CN 112648230B
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- impeller
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2238—Special flow patterns
- F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
- F04D29/2233—Construction and assembly entirely open or stamped from one sheet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2294—Rotors specially for centrifugal pumps with special measures for protection, e.g. against abrasion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/22—Fuel supply systems
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to the technical fields of centrifugal pumps, impellers and the like, in particular to an efficient cavitation-resistant centrifugal pump impeller. At least one through hole is formed in the blade of the impeller; the through holes penetrate from the blade working surface to the back surface of the blade. According to the invention, through holes are formed in the impeller blades, the high pressure of the impeller outlet is led to the back surface area of the inlet edge of the impeller blades by means of the through holes, so that the pressure of a low pressure area in the impeller is improved, the area of the low pressure area is reduced, the cavitation volume generated by cavitation in the impeller of the centrifugal pump is greatly inhibited, and the cavitation resistance of the impeller is improved. The anti-cavitation performance of the impeller is improved on the premise of not sacrificing the impeller efficiency, the solidified external dimension and interface of the impeller are not changed, the weight of the impeller can be slightly reduced to meet the light weight requirement, the processing technology is simple, the popularization is easy, and the use value is high.
Description
Technical Field
The invention relates to the technical fields of centrifugal pumps, impellers and the like, in particular to an efficient cavitation-resistant centrifugal pump impeller.
Background
Cavitation is generated when the fuel centrifugal pump of the engine rotates at a high speed, so that cavitation volume on the surface of the impeller and uneven pressure distribution degree on the surface of the blade are enhanced, energy conversion is restrained, performance of the fuel pump is reduced, and cavitation is further developed to form cavitation. Meanwhile, cavitation can cause the low-pressure area in the impeller to expand rapidly from the impeller inlet to the impeller outlet, so that cavitation generation and cavitation volume expansion in the impeller can be further promoted, and the energy conversion of the fuel pump is more seriously inhibited. In addition, damage to the flow-through components of the fuel centrifugal pump caused by cavitation is a key factor affecting the running safety and reliability of the engine. Therefore, improvement of efficiency and cavitation resistance of the fuel centrifugal pump of the engine is a core problem to be solved in order to improve the performance of the fuel centrifugal pump.
There are many methods for improving cavitation resistance of centrifugal pumps, such as: the open impeller is provided with an inducer, the inlet structure of the shell is changed, the surface of the flow passing component is provided with a coating, the oil supply pressure is improved, and the like. Although the existing method for improving cavitation resistance of the impeller can achieve the aim of improving cavitation resistance, the efficiency of the centrifugal pump is reduced or the solidified structure of the centrifugal pump is required to be changed, and the development process of the fuel centrifugal pump product of the engine is often limited by installation space, weight index, interface size and production period, so that the feasibility of improving the cavitation resistance by changing the structure of the fuel centrifugal pump product of the engine is reduced.
Disclosure of Invention
The invention solves the technical problems that: in order to ensure that the anti-cavitation performance of the centrifugal pump impeller is improved without sacrificing the efficiency, the solidified external dimension and interface of the centrifugal pump impeller are not changed, and the weight index requirement and the processing operability are met, the invention provides the efficient anti-cavitation centrifugal pump impeller.
The technical scheme of the invention is as follows: an anti-cavitation centrifugal pump impeller, wherein at least one through hole is formed in a blade of the impeller;
the through holes penetrate from the blade working surface to the back surface of the blade. According to the invention, through holes are formed in the impeller blades, the high pressure of the impeller outlet is led to the back surface area of the inlet edge of the impeller blades by means of the through holes, so that the pressure of a low pressure area in the impeller is improved, the area of the low pressure area is reduced, the cavitation volume generated by cavitation in the impeller of the centrifugal pump is greatly inhibited, and the cavitation resistance of the impeller is improved. The anti-cavitation performance of the impeller is improved on the premise of not sacrificing the impeller efficiency, the solidified external dimension and interface of the impeller are not changed, the weight of the impeller can be slightly reduced to meet the light weight requirement, the processing technology is simple, the popularization is easy, and the use value is high.
Preferably, the medium inlets and outlets of the through holes are positioned on different circumferential surfaces.
Preferably, the radial position R of the center of the medium inlet of the through hole L ＝K RL * R, radial direction of center of medium outletR is set S ＝K Rs *R；
Wherein R is the outer diameter of the impeller, K RL For the length coefficient of the inlet of the through hole, K Rs For the length coefficient of the outlet of the through hole, K RL Taking 0.75 to 0.85, K Rs Taking 0.55 to 0.65. The invention specifically discloses a radial position calculation formula of the center of the through hole medium inlet and outlet, and provides corresponding optimal parameters through simulation test, thereby improving the feasibility of the rectification scheme and ensuring the technical effect.
Preferably, the medium inlet angle of the through hole is 10 degrees < beta RL The medium outlet angle is less than 60 degrees and is less than or equal to 0 degrees and less than or equal to beta Rs ≤15°；
Wherein the inlet angle beta RL The outlet angle beta is the included angle between the axis of the through hole and the tangent line of the blade bone line at the position Rs Is the included angle between the axis of the through hole and the tangent line of the blade bone line at the position. The invention further defines the inlet angle and the outlet angle of the through hole medium, and gives out corresponding optimal parameters through a large number of simulation tests, thereby being convenient for processing and positioning on one hand and ensuring that the invention achieves optimal technical effect on the other hand.
Preferably, the maximum diameter of the through hole is smaller than the thickness of the blade, and the minimum diameter of the through hole is larger than 1/10 of the width of the impeller outlet; and the total flow of the medium of the through holes is less than 1% of the flow of the pump. On the premise of ensuring that the technical effect can be achieved, the influence on the strength of the blade and the efficiency of the centrifugal pump is comprehensively considered.
Preferably, the medium inlet and outlet of the through hole are positioned on the middle flow surface of the impeller flow channel. The technical scheme particularly discloses the position of the through hole medium inlet and outlet, and the medium flow at the position is stable, so that the realization of the technical effect can be ensured.
Preferably, all blades of the impeller are provided with the through holes. The technical scheme provides an orderly implementation mode, and the implementation mode can ensure that the technical scheme realizes the optimal effect.
Preferably, the through holes may be in the form of a convergent-divergent, divergent or constant diameter, depending on the direction of flow of the medium. The invention particularly discloses a form of the through hole flow channel, and provides various selection schemes, so that flexible treatment is facilitated according to specific conditions.
Preferably, the through hole axis may be a straight line, a curved line or a smooth transition line formed by the straight line and the curved line. The invention particularly discloses a form of the through hole flow channel, and provides various selection schemes, so that flexible treatment is facilitated according to specific conditions.
Drawings
Fig. 1 is a schematic view of the meridian plane structure of the impeller according to embodiment 1;
FIG. 2 is a front view of the impeller 1 according to the embodiment;
FIG. 3 is a sectional view B-B;
FIG. 4 is an isometric view of a position of an impeller blade according to example 1;
FIG. 5 is an isometric view of a position of the impeller of example 1;
FIG. 6 is an isometric view of an alternative position of the impeller of example 1;
FIG. 7 is a pressure contour plot comparison of example 1 with an axially intermediate section of a prior art impeller;
FIG. 8 is a graph comparing pressure contours of an axial intermediate section of example 1 and a prior art impeller design;
FIG. 9 is a graph of cavitation volume contrast in the impeller flowpath for example 1 versus prior art impeller design conditions;
FIG. 10 is a graph comparing flow-efficiency curves for example 1 and prior art impeller design speeds.
FIG. 11 is a graph of flow-boost versus speed for example 2 and a prior art impeller design speed
FIG. 12 is a graph comparing flow versus efficiency curves for example 2 and prior art impeller designs.
FIG. 13 is a graph comparing flow rate versus boost pressure for example 3 and prior art impeller design speeds
FIG. 14 is a graph comparing flow versus efficiency curves for example 3 and prior art impeller designs.
The symbols in the drawings are as follows: 1-hub, 2-front cover plate, 3-middle streamline, 4-rear cover plate, 5-through hole, 6-short blade and 7-long blade; 51-through hole inlet,52-through hole outlet 511-through hole inlet radial position line R L 521 radial position line R of through hole outlet S 512-through-hole entrance angle beta RL 522-through-hole exit angle beta Rs 601 short blade face, 602 short blade back, 701 long blade face, and 702 long blade back.
Detailed Description
According to the high-efficiency cavitation-resistant centrifugal pump impeller, through the arrangement of the through holes on the impeller blades, the high pressure of the impeller outlet is led to the back surface area of the inlet edge of the impeller blades by means of the through holes, so that the pressure of a low pressure area in the impeller is improved, the area of the low pressure area is reduced, the cavitation volume generated by cavitation in the centrifugal pump impeller can be greatly restrained, and the cavitation resistance of the impeller is improved.
The long blades and the short blades are uniformly staggered along the circumferential direction of the hub. The through hole 5 penetrates through the blade from the long blade working surface (surface 701 and surface 601) to the blade back surface (surface 702 and surface 602) near the blade outlet near the blade inlet from the long blade working surface and the short blade working surface, namely, the contour line of the through hole is completely overlapped with the projection of the blade in the axial direction, and the inlet and outlet positions and the wall surface of the blade are in smooth transition.
The inlet and outlet of the through hole 5 are positioned on the middle flow surface of the impeller flow channel,
inlet radial position (line 511) R L ＝K RL * R (wherein R is the impeller outer diameter, K) RL Taking (0.75-0.85) as the length coefficient of the inlet of the through hole; outlet radial position (line 521) R S ＝K Rs * R (wherein R is the impeller outer diameter, K) Rs Taking the length coefficient of the outlet of the through hole as 0.55-0.65.
Defining the via entrance angle beta RL (angle 512) is the angle (acute angle) between the axis of the through hole and the tangent line of the blade line at the place, and the outlet angle beta Rs The angle 522 is the angle (acute angle) between the axis of the through hole and the tangent of the blade bone line at this point.
The maximum diameter of the through hole is smaller than the thickness of the blade, and the minimum diameter is larger than 1/10 of the width of the impeller outlet. The total jet flow of the through holes should be less than 1% of the pump flow.
The radial projection length of the through hole is smaller than the radial projection length of the blade.
Each blade is provided with a corresponding through hole which is symmetrical relative to the rotation center of the impeller; the same blade can be provided with 2 groups of through holes, and the distance between the two through holes cannot be too close, otherwise, the strength of the impeller is affected.
The through holes may be convergent-divergent, divergent or of constant diameter. Preferably, through holes of constant diameter are used.
The inlet angle of the through hole is less than 10 degrees and less than beta RL The angle of the outlet is less than 60 degrees, and the angle of the outlet is less than or equal to 0 degree and less than or equal to beta Rs The through hole axis can be a straight line, a curve or a smooth transition line formed by the straight line and the curve, and the straight line is preferably selected.
Example 1
As shown in fig. 1-4, a high efficiency cavitation resistant impeller, the impeller comprising: the hub 1, the front cover plate 2, the middle streamline 3, the rear cover plate 4, the through holes 5, the short blades 6 and the long blades 7, and the long blades 7 and the short blades 6 are uniformly arranged along the circumferential direction of the hub. Through-hole inlet 51, through-hole outlet 52, through-hole inlet radial position line R L 511. Radial position line R of through hole outlet S 521. Entrance angle beta of through hole RL 512. Outlet angle beta of through hole Rs 522. Short blade face 601, short blade back 602, long blade face 701, and long blade back 702.
The through holes penetrate through the blades from the long blade working surface to the short blade working surface near the impeller outlet to the position of the back surface of the blade near the impeller inlet, and the inlet and outlet positions and the impeller wall surface are in smooth transition. The inlet and the outlet of the through hole 5 are positioned on the middle flow surface of the impeller flow passage, and the radial position R of the inlet is the radial position R L ＝K RL * r=0.85R; outlet radial position R S ＝K Rs * r=0.62R. The total jet flow of the through holes is 0.95% of the pump flow.
The contour line of the through hole is completely coincident with the projection of the blade in the axial direction.
The radial projection length of the through hole is smaller than the radial projection length of the blade.
Each blade is provided with corresponding through holes, the number of the through holes is 8, and the through holes are symmetrical about the rotation center of the impeller.
The diameter of the through hole is unchanged, the diameter is 1.8mm, and the thickness of the blade is 2mm.
The inlet angle beta of the through hole RL Outlet angle beta =25° Rs =12°, the axis being a straight line.
FIG. 7 is a pressure contour plot comparison of axial intermediate sections of a prior art impeller and an impeller of the present invention in cavitation conditions. It can be seen that the pressure in the indicated area increases and the area of the low pressure area decreases, and that the minimum pressure increase in the impeller flow passage is 6.5% consistent with the results described above.
FIG. 8 is a graph comparing cavitation distribution of a prior art impeller and an impeller of the present invention under design conditions, wherein the marked area is an area with a cavitation volume fraction greater than 90%, and it can be seen that the volume fraction of bubbles in the low pressure area of the impeller after the through holes are opened is significantly reduced, and the bubble aggregation area is significantly reduced, and the cavitation volume in the impeller is reduced by 20%. Namely, the existence of the through holes effectively inhibits cavitation, and improves cavitation resistance of the impeller.
Fig. 9 and 10 are flow-boost and flow-efficiency curves for the prior art impeller and the impeller of the present invention, respectively, at the design speeds for the design conditions. As can be seen from the graph, the simulation efficiency of the impeller in the prior art under the rated working condition and the impeller in the invention is 82%, the supercharging value and the efficiency of the impeller under the same rotating speed and different flow rates are not obviously changed, namely the impeller in the invention has no influence on the supercharging value and the efficiency.
Example two
A high efficiency anti-cavitation semi-open impeller, the impeller comprising: the hub 1, the back cover plate 4, the middle streamline 3, the through holes 5, the short blades 6 and the long blades 7, and the long blades 7 and the short blades 6 are uniformly arranged along the circumferential direction of the hub. Through-hole inlet 51, through-hole outlet 52, through-hole inlet radial position line R L 511. Radial position line R of through hole outlet S 521. Entrance angle beta of through hole RL 512. Outlet angle beta of through hole Rs 522. Short blade face 601, short blade back 602, long blade face 701, and long blade back 702.
The through holes penetrate through the blades from the long blade working surface to the short blade working surface near the impeller outlet to the position of the back surface of the blade near the impeller inlet, and the inlet and outlet positions and the impeller wall surface are in smooth transition. The inlet and the outlet of the through hole 5 are positioned on the middle flow surface of the impeller flow passage, and the inlet diameter is the same as the inlet diameterTo position R L ＝K RL * R=0.75r; outlet radial position R S ＝K Rs * R=0.65r. The total jet flow of the through holes is 0.5% of the pump flow.
Each blade is provided with corresponding through holes, the number of the through holes is 8, and the through holes are symmetrical about the rotation center of the impeller.
The through holes are gradually-enlarged holes, the diameter of the inlet is 1.5mm, the diameter of the outlet is 2.4mm, and the thickness of the blade is 2.5mm.
The inlet angle beta of the through hole RL Outlet angle beta =55° Rs =5°, the axis being a straight line.
FIG. 11 is a graph of flow versus boost for a prior art impeller and an inventive impeller at a design speed, and FIG. 12 is a graph of flow versus efficiency for a prior art impeller and an inventive impeller at a design speed. As can be seen from the graph, the simulation efficiency of the impeller in the prior art under the rated working condition and the impeller in the invention is 75%, the supercharging value and the efficiency of the impeller under the same rotating speed and different flow rates are not obviously changed, namely the impeller in the invention has no influence on the supercharging value and the efficiency.
Example III
A high efficiency cavitation resistant open impeller, the impeller comprising: the hub 1, the middle streamline 3, the through holes 5 and the long blades 7, and the long blades 7 are uniformly arranged along the circumferential direction of the hub. Through-hole inlet 51, through-hole outlet 52, through-hole inlet radial position line R L 511. Radial position line R of through hole outlet S 521. Entrance angle beta of through hole RL 512. Outlet angle beta of through hole Rs 522. A long blade working face 701 and a long blade back face 702.
The through holes penetrate through the blades from the long blade working surface to the back of the blade near the inlet of the blade near the outlet of the blade, and the positions of the inlet and the outlet are in smooth transition with the wall surface of the blade. The inlet and the outlet of the through hole 5 are positioned on the middle flow surface of the impeller flow passage, and the radial position R of the inlet is the radial position R L ＝K RL * r=0.85R; outlet radial position R S ＝K Rs * R=0.6r. The total jet flow of the through holes is 1% of the pump flow.
Each long blade is provided with corresponding through holes, the number of the through holes is equal to the number of the blades and is 6, and the through holes are symmetrical about the rotation center of the impeller.
The through hole is a shrinkage-reaming hole, the diameter of an inlet is 1.8mm, the diameter of a throat is 1mm, the diameter of an outlet is 2.2mm, the throat is positioned at 1/2 of the axial length of the hole, and the thickness of a blade is 2.3mm.
The inlet angle beta of the through hole RL Outlet angle beta =15° Rs =10°, the axis being a straight line.
FIG. 13 is a graph of flow versus boost for a prior art impeller and an inventive impeller at a design speed, and FIG. 14 is a graph of flow versus efficiency for a prior art impeller and an inventive impeller at a design speed. As can be seen from the graph, the efficiency of the impeller in the prior art under the rated working condition and the impeller in the invention is 1 to 1.5 percent of the difference between the design working condition point and the high-flow work condition point; the impeller has no obvious change in the supercharging value and efficiency under the same rotating speed and different flow rates, i.e. the impeller has little influence on the supercharging value and efficiency.
Claims (8)
1. An anti-cavitation centrifugal pump impeller is characterized in that at least one through hole is formed in a blade of the impeller; the through hole penetrates from the working surface of the blade to the back surface of the blade; leading the high pressure of the impeller outlet to the back surface area of the inlet edge of the impeller blade by virtue of the through hole;
the medium inlet and outlet of the through hole is positioned on the middle flow surface of the impeller flow channel;
the medium inlet angle of the through hole is 10 degrees less than beta RL Less than 60 DEG, inlet angle beta RL An included angle between the axis of the through hole and the tangent line of the blade bone line at the position;
the maximum diameter of the through hole is smaller than the thickness of the blade.
2. A cavitation-resistant centrifugal pump impeller according to claim 1, wherein the medium inlets and outlets of the through holes are located on different circumferential surfaces.
3. A cavitation resistant centrifugal pump impeller according to claim 2 wherein the center of the media inlet of the through bore is radialPosition R L ＝K RL * R, radial position R of center of medium outlet S ＝K Rs *R；
Wherein R is the outer diameter of the impeller, K RL K is the jet hole inlet length coefficient Rs K is the length coefficient of the jet hole outlet RL Taking 0.75 to 0.85, K Rs Taking 0.55 to 0.65.
4. The impeller of a cavitation resistant centrifugal pump of claim 1 wherein the medium outlet angle is 0 ° - β Rs ≤15°；
Wherein the outlet angle beta Rs Is the included angle between the axis of the through hole and the tangent line of the blade bone line at the position.
5. A cavitation resistant centrifugal pump impeller according to claim 1 wherein the smallest diameter of the through bore is greater than 1/10 of the width of the impeller outlet; and the total flow of the medium of the through holes is less than 1% of the flow of the pump.
6. An impeller according to any one of claims 1 to 5, wherein all blades of the impeller are provided with said through holes.
7. A cavitation-resistant centrifugal pump impeller according to any of claims 1-5, wherein said through holes may be of the convergent-divergent, divergent or constant diameter type, depending on the direction of flow of the medium.
8. A cavitation-resistant centrifugal pump impeller according to any of claims 1-5, wherein the through-hole axis may be straight, curved or a smooth transition line formed by straight and curved lines.
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| CN114109891A (en) * | 2021-11-05 | 2022-03-01 | 中国航发西安动力控制科技有限公司 | Cavitation-resistant booster pump impeller |
| CN114396383A (en) * | 2022-01-10 | 2022-04-26 | 成都凯天电子股份有限公司 | Oil-gas mixed transportation system |
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| US5480284A (en) * | 1993-12-20 | 1996-01-02 | General Electric Company | Self bleeding rotor blade |
| EP0807760B1 (en) * | 1996-05-17 | 2003-09-17 | Calsonic Kansei Corporation | Centrifugal multiblade fan |
| CN105650025A (en) * | 2016-01-08 | 2016-06-08 | 兰州理工大学 | Centrifugal pump impeller |
| CN207049062U (en) * | 2016-12-01 | 2018-02-27 | 江苏国泉泵业制造有限公司 | A kind of new drop cavitation impeller |
| CN207879523U (en) * | 2017-12-19 | 2018-09-18 | 新疆金风科技股份有限公司 | Wind speed round measurement structure, system and wind power generating set |
| CN109209987B (en) * | 2018-11-13 | 2019-06-25 | 兰州理工大学 | A kind of anti-cavitation centrifugal pump impeller and centrifugal pump |
| CN110118152B (en) * | 2019-06-14 | 2020-07-28 | 三一重能有限公司 | Pneumatic balance monitoring and adjusting system and method for blades of wind generating set |
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| Title |
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| 基于平衡孔偏移的离心泵空化性能改善研究;王东伟;刘在伦;赵伟国;;农业机械学报(第05期) * |
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