CN111043073B - Ultrahigh-speed high-efficiency complex curved surface centrifugal impeller - Google Patents
Ultrahigh-speed high-efficiency complex curved surface centrifugal impeller Download PDFInfo
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- CN111043073B CN111043073B CN201911372026.8A CN201911372026A CN111043073B CN 111043073 B CN111043073 B CN 111043073B CN 201911372026 A CN201911372026 A CN 201911372026A CN 111043073 B CN111043073 B CN 111043073B
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
Abstract
The invention discloses an ultra-high-speed high-efficiency complex curved surface centrifugal impeller, which comprises a wheel disc and blades, wherein the wrap angle of the blades is controlled to be 45-62 degrees, the forward rake angle of the blade outlet is controlled to be 25-32 degrees, the installation angle of the blade inlet is controlled to be 32-40 degrees, and the installation angle of the blade outlet is controlled to be 28-60 degrees.
Description
Technical Field
The invention relates to the field of fan impellers, in particular to an ultrahigh-speed high-efficiency complex curved surface centrifugal impeller.
Background
The centrifugal impeller is a wind wheel which supplies air in the axial direction and discharges air in the radial direction, and applies work by utilizing centrifugal force (depending on the rotating speed and the outer diameter) to improve the pressure of the air.
The performance of the centrifugal impeller directly determines the performance of fan equipment, and along with the development of turbine rotating machinery towards high speed, high efficiency and high reliability, the design requirement on the centrifugal impeller is higher and higher. At present, the design of the centrifugal impeller mainly bases on a three-dimensional flow design theory, carries out computational fluid dynamics analysis on a flow passage, and has important engineering significance for the design of medium and low speed centrifugal impellers. However, in the case of the ultra-high speed centrifugal blower, the linear velocity at the maximum diameter of the centrifugal impeller exceeds the sonic velocity, and the high efficiency and high speed stability of the centrifugal impeller cannot be ensured by applying the existing design scheme.
However, in the existing scheme of designing the centrifugal impeller, on one hand, the outlet flow and the outlet pressure cannot be effectively improved after the rotating speed is increased, and the impeller efficiency tends to be reduced, and on the other hand, the rotating speed of the centrifugal impeller needs to cross the critical rotating speed, the requirement on the dynamic performance is higher and higher, and the existing scheme cannot meet the design requirement of ultra high speed.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides the ultrahigh-speed high-efficiency complex curved surface centrifugal impeller, and the impeller efficiency of the impeller is improved by 3-5% compared with the efficiency of the original impeller design scheme.
The technical scheme adopted by the invention for solving the technical problems is as follows:
the invention relates to an ultra-high-speed high-efficiency complex curved surface centrifugal impeller, which comprises a wheel disc and blades 1, wherein the installation angle of the inlet of the blade 1 of the impeller is 32-40 degrees;
the mounting angle of the outlet of the blade is controlled to be 28-60 degrees;
the wrap angle of the blade is designed to be 45-62 degrees.
The impeller can also be provided with a splitter blade 2, the splitter blade 2 and a main blade 3 jointly form a blade, and the ratio of the rim curve of the splitter blade to the rim curve of the main blade is less than or equal to 0.7 and is greater than or equal to 0.4;
the ratio of the hub curve of the splitter blade to the hub curve of the main blade is less than or equal to 0.7 and greater than or equal to 0.4.
The ratio of the rim curve of the splitter blade on the meridian plane to the hub curve of the splitter blade is less than or equal to 0.6 and more than or equal to 0.3;
the front rake angle of the blade outlet of the impeller is 25-32 degrees;
the hub curve on the meridian plane can be a Bezier curve, and the rim curve can also be a Bezier curve;
the peak value of a curve of the ratio of the curvature radius of each point on the hub curve of the blade to the arc length of the point and the peak value of a curve of the ratio of the curvature radius of each point on the rim curve to the arc length of the noon surface of the point are different by 1/5-1/3 phase angles, preferably 1/4 phase angles.
The invention has the beneficial effects that:
aiming at the design requirement of the ultra-high speed centrifugal impeller, a fluid dynamics calculation analysis method is adopted, and repeated iterative calculation is carried out through impeller flow channel optimization, outlet angle preference, blade forward inclination angle preference and splitter blade size design, so that the flow rate and pressure ratio of the impeller are improved, and the working efficiency of the impeller is increased.
1. When the ultra-high-speed high-efficiency complex curved surface centrifugal impeller designed by the invention keeps the size unchanged or does not change greatly (the size change is less than or equal to 5 percent), the pressure ratio can be improved by more than 20 percent when the original flow rate is kept unchanged;
2. the designed impeller can keep the size unchanged or not change greatly (the size change is less than or equal to 5 percent), and when the original pressure ratio is kept unchanged, the flow can be increased by more than 15 percent;
3. the efficiency of the designed impeller is improved by 3 to 5 percent compared with the efficiency of the original impeller design scheme.
Drawings
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention.
FIG. 1 is a schematic view of a centrifugal impeller blade installation;
FIG. 2 is a schematic view of the overall structure of the centrifugal impeller;
FIG. 3 is a meridian plane structure diagram of a centrifugal impeller blade;
FIG. 4 is a front view of the centrifugal impeller in an upright position;
FIG. 5 is a graph of the ratio of the radius of curvature of each point on the hub curve of the blade to the arc length at that point and the ratio of the radius of curvature of each point on the rim curve to the arc length at the noon surface at that point.
1-a blade; 2-splitter blades; 3-a main blade; 4-anteversion angle.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
Referring to the attached drawing 2, the ultra-high-speed high-efficiency complex curved surface centrifugal impeller comprises a wheel disc and blades 1, in order to reduce pneumatic impact loss, reduce noise at an inlet and improve the work capacity of the blades of the impeller, the installation angle of the inlet of the blade 1 of the impeller is 32-40 degrees, and the angle B1 shown in the attached drawing 1 is referred to;
the outlet installation angle of the impeller blade 1 has an influence on the efficiency of the impeller and plays a certain role in the outlet pressure of the impeller, the larger the outlet installation angle of the blade is, the stronger the working capacity of the blade is, and the outlet pressure is also increased, so that the outlet installation angle of the blade is effectively controlled to be between 28 and 60 degrees, see < B2 shown in figure 1;
if the wrap angle is too large, the blades are correspondingly longer, the friction area between gas and the blades is increased, the work efficiency of the impeller is reduced, and if the wrap angle is too small, the control capability of the blades on the airflow and the stability of the airflow in a flow passage are reduced, so that the wrap angle of the blades is designed to be 45-62 degrees, and see the angle A shown in the attached figure 1.
The impeller may further have splitter blades 2, the splitter blades 2 and the main blades 3 together form a blade, see fig. 2, the splitter blades function to reduce blade loading at the outlet region of the impeller, and the ratio of the rim curve (ratio of the CB section to the AB section) to the rim curve of the main blades (BAA 'B' profile) is 0.7 or less and 0.4 or more, see BCC 'B' contour in fig. 3 for the splitter blades in the meridian plane.
The ratio of the hub curve of the splitter blade (BCC 'B' profile) to the hub curve of the main blade (BAA 'B' profile) (the ratio of the section C 'B' to the section A 'B') in the meridian plane is not more than 0.7 and not more than 0.4.
The ratio of the rim curve of the meridian plane splitter blade (BCC 'B' outline) to the hub curve (the ratio of the CB section to the C 'B' section) is less than or equal to 0.6 and is more than or equal to 0.3;
the impeller outlet forward-inclination angle can reduce the load at the impeller outlet rim and effectively reduce the pressure of the airflow outlet, so that the blades of the impeller have a certain outlet forward-inclination angle 4, see angle AOB shown in figure 4, and the outlet forward-inclination angle is 25-32 degrees;
the hub curve on the meridian plane can be a Bezier curve, and the rim curve can also be a Bezier curve;
referring to fig. 5, two curves are a curve of the ratio of the curvature radius of each point on the hub curve of the blade to the arc length of the point and a curve of the ratio of the curvature radius of each point on the rim curve to the arc length of the noon surface of the point, and the maximum value, namely the peak value, of the two curves is separated, that is, the curve of the ratio of the curvature radius of each point on the hub of the blade to the arc length of the point and the curve of the ratio of the curvature radius of each point on the rim to the arc length of the point, the peak values of the two curves have phase angles of 1/5-1/3, the phase difference is 1/4 phase differences, and aerodynamic noise is reduced.
The designed ultra-high-speed high-efficiency complex curved surface centrifugal impeller greatly improves the flow of the centrifugal impeller and reduces the outlet pressure of the impeller on the premise of not changing the overall size of the impeller. The flow loss is small, the working efficiency is higher, and the dynamic characteristic is better.
Claims (9)
1. The utility model provides a high-efficient complicated curved surface centrifugal impeller of hypervelocity, includes rim plate and blade, its characterized in that: the blades comprise splitter blades and main blades, the ratio of the arc length of the rim curve of the splitter blades to the arc length of the rim curve of the main blades is less than or equal to 0.7 and more than or equal to 0.4, and/or the ratio of the arc length of the hub curve of the splitter blades to the arc length of the hub curve of the main blades is less than or equal to 0.7 and more than or equal to 0.4, and the wrap angle of the blades is 45-62 degrees.
2. The centrifugal impeller of claim 1, wherein: the blade inlet installation angle is 32-40 degrees.
3. The centrifugal impeller of claim 1, wherein: the blade outlet installation angle is 28-60 degrees.
4. The centrifugal impeller of claim 1, wherein: the curve of the hub on the meridian plane is a Bezier curve.
5. The centrifugal impeller of claim 1, wherein: the ratio of the rim curve of the splitter blade on the meridian plane to the hub curve of the splitter blade is less than or equal to 0.6 and more than or equal to 0.3.
6. The centrifugal impeller of claim 1, wherein: the front inclination angle of the blade outlet of the impeller is 25-32 degrees.
7. The centrifugal impeller of claim 5, wherein: the rim curve is also a bezier curve.
8. The centrifugal impeller of claim 1, wherein: the peak value of a curve of the ratio of the curvature radius of each point on the hub curve of the blade to the arc length of the point and the peak value of a curve of the ratio of the curvature radius of each point on the rim curve to the arc length of the noon surface of the point have a phase angle of 1/5-1/3.
9. The centrifugal impeller of claim 1, wherein: the difference between the curve of the ratio of the curvature radius of each point on the hub curve of the blade to the arc length of the point and the peak value of the curve of the ratio of the curvature radius of each point on the rim curve to the arc length of the noon surface of the point is 1/4 phase angles.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911372026.8A CN111043073B (en) | 2019-12-27 | 2019-12-27 | Ultrahigh-speed high-efficiency complex curved surface centrifugal impeller |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911372026.8A CN111043073B (en) | 2019-12-27 | 2019-12-27 | Ultrahigh-speed high-efficiency complex curved surface centrifugal impeller |
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| Publication Number | Publication Date |
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| CN111043073A CN111043073A (en) | 2020-04-21 |
| CN111043073B true CN111043073B (en) | 2021-06-15 |
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| CN201911372026.8A Active CN111043073B (en) | 2019-12-27 | 2019-12-27 | Ultrahigh-speed high-efficiency complex curved surface centrifugal impeller |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111894872A (en) * | 2020-07-10 | 2020-11-06 | 绍兴智新机电科技有限公司 | Two-stage booster-type low noise fan |
| CN111894873B (en) * | 2020-08-08 | 2021-08-31 | 绍兴智新机电科技有限公司 | Two-stage mixed-flow low-noise fan |
| CN112377457B (en) * | 2020-10-13 | 2021-12-17 | 宁波方太厨具有限公司 | Impeller, centrifugal fan applying same and range hood |
| 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 |
Citations (4)
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|---|---|---|---|---|
| JP2015190382A (en) * | 2014-03-28 | 2015-11-02 | 株式会社Ihi | compressor impeller, centrifugal compressor, and supercharger |
| CN106402020A (en) * | 2016-10-31 | 2017-02-15 | 广东威灵电机制造有限公司 | Impeller and fan having same |
| CN206221359U (en) * | 2016-11-23 | 2017-06-06 | 广东威灵电机制造有限公司 | Impeller for blower fan and the blower fan with it |
| CN108361205A (en) * | 2017-07-17 | 2018-08-03 | 华中科技大学 | A kind of centrifugal pump impeller and the LNG immersed pumps comprising the centrifugal pump impeller |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017193982A (en) * | 2016-04-19 | 2017-10-26 | 本田技研工業株式会社 | compressor |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015190382A (en) * | 2014-03-28 | 2015-11-02 | 株式会社Ihi | compressor impeller, centrifugal compressor, and supercharger |
| CN106402020A (en) * | 2016-10-31 | 2017-02-15 | 广东威灵电机制造有限公司 | Impeller and fan having same |
| CN206221359U (en) * | 2016-11-23 | 2017-06-06 | 广东威灵电机制造有限公司 | Impeller for blower fan and the blower fan with it |
| CN108361205A (en) * | 2017-07-17 | 2018-08-03 | 华中科技大学 | A kind of centrifugal pump impeller and the LNG immersed pumps comprising the centrifugal pump impeller |
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| CN111043073A (en) | 2020-04-21 |
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