CN1185418C - Propeller with ultra-thick blades for centrifugal impurities pump - Google Patents
Propeller with ultra-thick blades for centrifugal impurities pump Download PDFInfo
- Publication number
- CN1185418C CN1185418C CN 01138011 CN01138011A CN1185418C CN 1185418 C CN1185418 C CN 1185418C CN 01138011 CN01138011 CN 01138011 CN 01138011 A CN01138011 A CN 01138011A CN 1185418 C CN1185418 C CN 1185418C
- Authority
- CN
- China
- Prior art keywords
- impeller
- present
- runner
- blades
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to an impeller for pumps, particularly to an impeller of centrifugal impurity pumps, namely centrifugal solid-liquid two-phase flowing pumps. The present invention adopts an impeller with the gradually increased blade thickness from an inlet to an outlet, a flow passage between the two blades uniformly shrinks in two directions, and the total area of the flow passage between the blades is gradually reduced from the inlet to the outlet. The present invention solves the disadvantages of low pump efficiency, shaft power is increased with the increase of flow quantity and damages a prime mover, etc. Therefore, the present invention obtains sudden decrease characteristic curves and saturated power characteristics, suppresses separation phenomenon in the flow passage between the blades and increases hydraulic efficiency and cavitation performance, and the present invention has the advantages of simple structure, convenient processing, convenient use and good economic performance.
Description
Technical field
The present invention relates to a kind of impeller of pump, particularly a kind of centrifugal impurities pump, the i.e. impeller of centrifugal two-phase pump.
Background technique
For the centrifugal impurities pump that low-specific-speed is low-flow high-lift, there are two significant problems to limit it and use, the efficient of this pump of the first is lower; It two is that the air horsepower of this pump increases along with the increase of flow, and prime mover (under the situation that lift reduces) causes damage easily.Just need to strengthen match power for fear of damaging prime mover, make cost increase, volume strengthens, and has reduced the Economy of complete machine.
Before the present invention made, the inventor noticed the improvement of prior art to the above-mentioned defective of this type of pump.Successively propose for pump and compressor as U.S. Pat 4235789 or China Patent No. 86102777, for waiting axial plane thickness impeller, runner between leaf is made into contraction on planimetric map, but its contraction is not uniform, therefore runner between the leaf of appearance contraction-diffusion-contraction is unfavorable for increasing work efficiency most probably; And for example CN2054100U makes involute with the plane molded lines of blade, makes like this that width of flow path remains unchanged between the leaf on the planimetric map, controls the area change of runner between leaf again by axial plane figure; Chinese patent CN2086336U is with the axial plane of runner and the size on the planimetric map between several equation control leaves for another example, reaches the purpose of control peak output; CN1022584C adopts thick blade to make on planimetric map, and the inlet part of runner is non-diffusion between leaf, and exit portion then has diffusion slightly, and the distribution of vane thickness is with stopping up functions control, and the number of blade＞2 are more.
The common ground of above several method and structure all is the shapes (axial plane or plane) of a direction of runner between the control leaf of ining all sorts of ways, and is and shrinks shape, and the gross area of runner is a slight spread between leaf, and the number of blade is more.Though solved two above-mentioned defectives to a certain extent, these all propose at the monophasic fluid medium, and runner is always smaller at the size degree of some directions in certain this place between designed leaf.For the transh pump of the conveying solidliquid mixture that solves for needs, satisfy the requirement of passing capacity, just must make runner between leaf all be not less than the value of regulation in the smallest dimension of any section, virtually any size, above-mentioned these method and structures are just all inapplicable.
The inventor also notices CN1022584C, makes the impeller outlet area be equal to or slightly greater than inlet-duct area by the method for controlling flow channel of axial plane.But it is little that this method exists the passing capacity of pump, lacks promptly very high dead point, the pass lift of characteristic curve that falls very suddenly, and saturated power characteristic and high defectives such as level of efficiency.
Summary of the invention
Purpose of the present invention will overcome above-mentioned defective exactly, designs a kind of centrifugal impurities pump impeller.
Technological scheme of the present invention is that major technique is characterised in that the vane thickness on the impeller increases gradually from import to outlet, and runner is evenly to shrink between two interlobate leaves, and the gross area of runner reduces gradually from import to outlet between leaf.
Its further technology is characterized in that being that runner evenly shrinks between two interlobate leaves on both direction.
Its further again technical characteristics is to be that the discharge area of runner between leaf and the ratio range of inlet-duct area are between 0.2≤K＜1.0.
Advantage of the present invention and effect be as shown in Figure 3, because the impeller outlet area is controlled at very little numerical value, guaranteed that pump has the characteristic curve that falls suddenly and saturated power characteristic; Flow-the head curve 6 (Q-H) of tradition low specific-speed centrifugal pump is more flat, and lift slowly reduces with the increase of flow, and (Q-P) is steeper for flow-power curve 8, and power increases rapidly with the increase of flow, and does not have extreme point; Flow-head curve of the present invention 7 is steeper, lift reduces rapidly with the increase of flow, and flow-power curve 9 is more flat, and has the power extreme point, improved the operational reliability of low specific-speed pump, made that pump is can normally move under any operating mode of zero to lift from closing the dead point.Flowmeter is shown Q, and lift is expressed as H, and wattmeter is shown P.
Because runner is evenly to shrink between leaf, or even strong contraction, therefore effectively suppressed the appearance of segregation phenomenon in the runner between leaf, improved the hydraulic efficiency of impeller.
Owing to enlarged the inlet channel area as much as possible, reduced the flow velocity of import, therefore improved its cavitation performance.
In addition, edge, blade import position is circular arc, has suppressed off-design behaviour preferably down because the flow separation that the import impact causes, though make pump when the off-design operating mode decrease in efficiency seldom, thereby efficacious workaround with comparison broadness.
And simple in structure, processing, use are all convenient, good economy performance.
Description of drawings
The axis projection of Fig. 1-impeller of the present invention.
The plane figure of Fig. 2-impeller of the present invention.
Fig. 3-performance chart.
Embodiment
As shown in Figure 1, can know from the axis projection of impeller that its exit width 1 is greater than the solid particle diameter that passes through, and from being exported to import, the axial plane width of runner increases to entrance width 2 gradually; As shown in Figure 2, can know from the plane figure of impeller that the outlet port 3 of runner equally also should be greater than the diameter of solid particle between leaf, the width of runner 3 evenly increases to inlet 4 gradually from the outlet port equally between leaf.Like this, runner evenly shrinks on both direction between two interlobate leaves, and the gross area of runner between leaf is reduced to outlet gradually from import, and its ratio range is between 0.2≤K＜1.0, and K is a discharge area and the ratio of inlet-duct area, and K is 0.2 in this example; The inlet radius of front and rear cover plate place blade is unequal, and the two sides of blade is that the working surface and the back side all are distorted shape in inlet 4, and edge, blade import position is circular arc 5.The blade surface molded lines is not the shape need according to blade, but determine according to the requirement that Flow area changes.
For the characteristic curve that obtains to fall suddenly and saturated power characteristic, solve the bigger problem of outlet total area ratio because of formed by the solid particle diameter restrictions of runner between leaf, adopt the method control outlet gross area that reduces the runner number, adopt two blades in this example.When guaranteeing certain passing capacity, controlled peak output effectively, greatly improved the safety reliability of water pump.
Claims (4)
1. the centrifugal impurities pump impeller that has ultra-thick blades is characterized in that the vane thickness of impeller increases gradually from import to outlet, and runner is evenly to shrink between two interlobate leaves, and the gross area of runner reduces gradually from import to outlet between leaf.
2. the centrifugal impurities pump impeller with ultra-thick blades according to claim 1 is characterized in that the discharge area of runner between leaf and the ratio of inlet-duct area are 0.2≤k＜1.0.
3. the centrifugal impurities pump impeller with ultra-thick blades according to claim 1 is characterized in that edge, blade import position is circular arc.
4. the centrifugal impurities pump impeller with ultra-thick blades according to claim 1 is characterized in that the number of blade is provided with 1～3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01138011 CN1185418C (en) | 2001-12-21 | 2001-12-21 | Propeller with ultra-thick blades for centrifugal impurities pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01138011 CN1185418C (en) | 2001-12-21 | 2001-12-21 | Propeller with ultra-thick blades for centrifugal impurities pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1356478A CN1356478A (en) | 2002-07-03 |
| CN1185418C true CN1185418C (en) | 2005-01-19 |
Family
ID=4674306
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01138011 Expired - Fee Related CN1185418C (en) | 2001-12-21 | 2001-12-21 | Propeller with ultra-thick blades for centrifugal impurities pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1185418C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103899573B (en) * | 2014-03-17 | 2016-06-15 | 安徽华瑞塑业有限公司 | A kind of centrifugal pump impeller |
| NL2013367B1 (en) * | 2014-08-26 | 2016-09-26 | Ihc Holland Ie Bv | Impeller blade with asymmetric thickness. |
| CN105673556A (en) * | 2016-04-08 | 2016-06-15 | 梁平 | Impeller |
| CN107061348B (en) * | 2017-02-24 | 2023-03-28 | 西华大学 | Low specific speed centrifugal pump impeller |
-
2001
- 2001-12-21 CN CN 01138011 patent/CN1185418C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1356478A (en) | 2002-07-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1265099C (en) | Method for designing low-rate revolution centrifugal pump impeller | |
| US3522997A (en) | Inducer | |
| US6149385A (en) | Multiphase fluid pumping or compression device with blades of tandem design | |
| EP0886069A2 (en) | Turbomachinery with variable angle fluid guiding devices | |
| WO1994015102A1 (en) | Pump impeller and centrifugal slurry pump incorporating same | |
| CN110762051A (en) | Surging prevention structure of magnetic suspension air compressor | |
| CN1185418C (en) | Propeller with ultra-thick blades for centrifugal impurities pump | |
| CN101042144A (en) | Centrifugal type turbo machine | |
| CN2528981Y (en) | Impeller with super-thick vane of centrifugal trash pump | |
| US5141390A (en) | Vertical axis centilevered pump provided with a stabilizing by-pass flow | |
| CN100398840C (en) | Wedge blade for diffuser of compressor mechanical blade | |
| CN202326441U (en) | Wedge-shaped blade for blade diffuser of centrifugal compressor | |
| CN2086336U (en) | No-overload low-unit speed centrifugal pump centrifugal impeller | |
| CN2165276Y (en) | High-efficiency vane wheel | |
| CN206972617U (en) | A kind of guide vane of water pump cell structure | |
| CN2265446Y (en) | High-speed composite impeller centrifugal pump | |
| KR101315358B1 (en) | Pump with multiple stage of impeller | |
| CN206054372U (en) | A kind of high-efficiency overload-free submersible sewage impeller of pump suitable for sewage disposal | |
| US5252025A (en) | Drainage pump | |
| CN2224942Y (en) | Centrifugal impeller of fluid energy converting mechanism | |
| CN2054100U (en) | Involute impeller for rotary fluid machines | |
| CN2320827Y (en) | High-efficiency centrifugal water pump vane | |
| CN200958478Y (en) | Split centrifugal pump | |
| CN110319053A (en) | Unshrouded impeller and the low-flow high-lift centrifugal pump of single stage type for using unshrouded impeller | |
| CN2303952Y (en) | Gas-liquid two-phase centrifugal pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: LANSHEN GROUP CO., LTD. Free format text: FORMER NAME: LANSHEN PUMP GROUP CO LTD, NANJING |
|
| CP03 | Change of name, title or address |
Address after: 211500 Nanjing Province, Liuhe District, East Road, No. Patentee after: Lanshen Group Co., Ltd. Patentee after: Huazhong University of Science and Technology Address before: 211500, No. 31 East Road, Liuhe, Jiangsu, Nanjing Patentee before: Lanshen Pump Group Co., Ltd., Nanjing Patentee before: Huazhong University of Science and Technology |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20050119 Termination date: 20171221 |