CN107100888B - Twisted blade type impeller of large-pass spherical-diameter efficient double-shell mud pump - Google Patents
Twisted blade type impeller of large-pass spherical-diameter efficient double-shell mud pump Download PDFInfo
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- CN107100888B CN107100888B CN201710366776.9A CN201710366776A CN107100888B CN 107100888 B CN107100888 B CN 107100888B CN 201710366776 A CN201710366776 A CN 201710366776A CN 107100888 B CN107100888 B CN 107100888B
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- impeller
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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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
- F04D29/245—Geometry, shape for special effects
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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
- F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
- F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to the technical field of hydraulic design of mud pumps, and discloses a twisted blade type impeller of a large-pass spherical-diameter efficient double-shell mud pump, wherein the maximum diameter of a passing sphere of the impeller is 60% of the diameter of a suction port of the impeller, and the blades are three-dimensional twisted blades. The impeller blade of the dredge pump is designed into a twisted blade, the blade profile improves the passing capacity of an impeller runner, the novel dredge pump impeller can solve the problem that a dredge pump is easy to block when conveying massive rock, hydraulic loss is reduced, and dredge pump efficiency is improved.
Description
Technical Field
The invention relates to a large-pass spherical diameter high-efficiency industrial pump which is used for conveying large rocks and minerals in the fields of dredging and mining, and mainly relates to a mud pump with the passing capacity of 60% of the diameter of a suction port of the mud pump and capable of effectively preventing the blockage of the large rocks.
Background
The dredger is a key device of the dredger, when the dredger is used for dredging weathered rocks, coral reefs or sandy soil containing larger stones, the situation that the stones are blocked at the inlet of the dredger impeller can occur, the construction is not interrupted, a short pipe at the inlet of the dredger is removed, the stones at the inlet of the impeller are cleaned out, the dredger is frequently blocked, the continuity of the construction cannot be ensured, and the soil quality of the dredger is seriously reducedAnd the construction efficiency of working conditions. At the existing 3500m 3 The mud pump applied to the cutter suction dredger is taken as an example, whether the mud pump is a common mud pump with five-blade impellers or a high-efficiency mud pump with three-blade impellers, the particle size is 35-40% of the diameter of a suction port of the mud pump, when the diameter of the suction port of the mud pump is 850mm, namely the diameter of a maximum passing sphere of the mud pump is 340mm, and when the size of a stone is greater than 340mm, the stone is easily blocked at the pumping position. The relatively small passing sphere diameter of the mud pump impeller is a main reason for frequent blockage of the mud pump when conveying rock masses. Aiming at special soil such as massive rock, the key overflow part of the dredge pump not only requires that the flow channel of the key overflow part conforms to the running track of the dredge, but also has large overflow channel, thus reducing the blockage of the dredge pump.
Disclosure of Invention
Aiming at the problem that the existing dredge pump is easy to block when rock is conveyed, the invention aims to provide the pump impeller with larger outer diameter through objects, the maximum passing sphere diameter of the dredge pump designed by adopting the impeller can reach 60% of the diameter of the dredge pump suction opening, when the diameter of the dredge pump suction opening is 850mm, namely the maximum passing sphere diameter of the dredge pump is 510mm, the conveying capacity of the large rock is enhanced, the dredge pump is effectively prevented from being blocked, meanwhile, the pump impeller has higher efficiency under various working conditions, and the construction efficiency of a dredge boat is improved.
The technical scheme to be protected of the invention is as follows:
the utility model provides a high-efficient double-shell mud pump's of big through sphere diameter distortion blade formula impeller, this impeller's overflow part is enclosed by impeller front shroud, impeller back shroud, water conservancy diversion cap, blade, wheel hub 5 (this part structure relates to component parts, positional relationship, and the relation of connection all belongs to prior art). The innovation point of the invention is characterized in that:
the blades 3 are twisted blades, the number of the blades is three, the adjacent blades are 120-degree intervals, the width of the blade outlet is 60% of the diameter of the impeller suction opening, the diameter of the impeller runner passing through the maximum sphere is 60% of the diameter of the impeller suction opening, the blades are uniformly thickened from the inlet to the outlet, the thickness of the blades is 80-120 mm, and the wrap angle of the blades is 120-150 degrees. The blade profile equation consists of two parts, namely a blade and front cover plate intersection equation and a blade and rear cover plate intersection equation:
the blade and front cover plate intersection equation:
the blade and back cover plate intersection equation:
wherein r is 1 The unit mm is the radius of the suction port of the impeller; θ is the angle of the blade in the circumferential direction, the blade inlet is at the initial 0 °, and the blade outlet is at the end point
For the blade wrap angle, 135℃in FIG. 1, r s (θ) and r h And (theta) is the distance from any point on the intersecting line of the front cover plate and the intersecting line of the rear cover plate to the center of the impeller in mm. After the blade is lofted by the intersecting line of the front cover plate and the intersecting line of the rear cover plate, the blade is thickened towards the outer edge direction of the impeller to obtain a set thickness range.
Based on the technical scheme, the high-efficiency dredge pump with large drift diameter for conveying rocks can be designed, and the inner cavity consists of the cantilever closed centrifugal impeller and the single-flow-channel volute, wherein the inner impeller and the outer volute are cast by high-chromium cast iron.
The flow passing part of the impeller is enclosed by an impeller front cover plate, an impeller rear cover plate, a diversion cap, blades and a hub 5. The pump shaft is connected with the impeller hub through threads, an anti-abrasion ring is arranged at the impeller suction port, an anti-abrasion lining is arranged at the suction port, and an anti-abrasion lining plate is arranged between the impeller and the pump cover. The blades are twisted blades, the number of the blades is three, and the diameter of the impeller runner passing through the maximum sphere is 60% of the diameter of the impeller suction port.
The volute is supported and fixed by the lining plate and the pump cover, the section of the volute flow passage is in a round corner rectangle, the width value of the volute flow passage is the sum of the thickness value of the impeller flow passage and the front and rear cover plates of the impeller and the clearance value of the impeller cover plates and the wear-resistant lining plate, the thickness value of the front and rear cover plates of the impeller is 50-60mm, the clearance value of the impeller cover plates and the wear-resistant lining plate is 3-5mm, and the inner edge and the outer edge of the volute are in spiral line shapes.
The impeller blade of the dredge pump is designed into a twisted blade, the blade profile improves the passing capacity of an impeller runner, the problem that the dredge pump is easy to block when conveying massive rock can be solved, hydraulic loss is reduced, and dredge pump efficiency is improved.
The mud pump has large passing sphere diameter and high efficiency, the passing sphere diameter is improved by 50% compared with that of the existing mud pump products in the market, the blocking probability of dredging massive rock is effectively reduced, the clear water efficiency of the mud pump can reach 85%, the construction continuity and economy are ensured, and obvious benefit improvement is brought to enterprises.
Drawings
Fig. 1 is a perspective view of an impeller axial surface and a vane pattern diagram.
FIG. 2 is a three-dimensional view of the impeller water flow path and through-sphere diameter.
FIG. 3 is a three-dimensional impeller part diagram, 1-front shroud, 2-deflector cap, 3-blade, 4-rear shroud, 5-hub.
FIG. 4 is a three-dimensional assembly view of a double-shell mud pump, 6-volute (liner), 7-wear-resistant liner, 8-large cover, 9-front pump cover, 10-impeller, 11-impeller suction inlet wear-resistant ring, 12-housing, 13-bearing cartridge assembly, 14-pump shaft, 15-bearing cartridge bracket.
FIG. 5 is a graph of the clear water performance of a mud pump employing the impeller design of the present invention.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
as shown in FIG. 1, the axial projection of the impeller flow channel and the profile of the blades, the number of the blades is 3, and the outer diameter D of the impeller 2 2040mm, 850mm in impeller suction opening diameter, and the impeller runner outlet width B2 is the impeller suction opening diameter D 1 60% of the impeller flow passage outlet width B 2 The blade wrap angle is 135 degrees and is calculated according to the equation (1) and the equation (2) to obtain the blade profile coordinates as shown in the following table. The blade is obtained by thickening 80mm towards the outer edge of the impeller after lofting by the intersecting line of the front cover plate and the intersecting line of the rear cover plate.
| θ(°) | 0 | 10 | 20 | 30 | 40 | 50 | 60 | 70 | 80 | 90 | 100 | 110 | 120 | 130 | 135 |
| r s (θ)(mm) | 231 | 277 | 323 | 382 | 433 | 490 | 541 | 600 | 654 | 708 | 755 | 805 | 857 | 912 | 1020 |
| r h (θ)(mm) | 429 | 448 | 474 | 498 | 529 | 556 | 591 | 626 | 669 | 708 | 755 | 805 | 857 | 912 | 1020 |
The maximum through-sphere diameter of the impeller of the present invention shown in fig. 2 is 60% of the impeller suction opening diameter D1 of fig. 1, i.e., 510mm.
As shown in fig. 3, the over-current part of the impeller is surrounded by the impeller front cover plate 1, the flow guiding cap 2, the blades 3, the impeller rear cover plate 4 and the hub 5, and the five parts are cast integrally. The blades 3 are twisted blades, the number of the blades is three, and the diameter of the impeller runner passing through the maximum sphere is 60% of the diameter of the impeller suction port.
As shown in fig. 4, the pump shaft 14 is connected with the impeller 10 through threads, the impeller 10 is connected with the impeller suction port anti-wear ring 11 through bolts, the impeller 10 is positioned in a cavity formed by the volute (inner liner) 6 and the wear-resistant lining plate 7, the volute (inner liner) 6 is fixed on the shell 12 through bolts, the cavity between the volute (inner liner) 6 and the shell 12 is filled with high-pressure water to balance the pressure in the mud pump flow passage, the wear-resistant lining plate 7 is arranged between the impeller 10 and the front pump cover 9 and the shell 12, the wear-resistant lining plate 7 is connected with the front pump cover 9 and the shell 12 through bolts, the front pump cover 9 is connected on the large cover 8 through bolts, the large cover 8 is connected on the shell 12 through bolts, the pump shaft 14 is positioned in the bearing cylinder 13, the bearing cylinder 13 is fixed on the bearing cylinder bracket 15, the bearing cylinder bracket 15 is connected with the shell 7 through bolts, and the bearing cylinder bracket 15 and the shell 12 are fixed on the hull deck through bolts.
The width value of the volute (liner) runner takes the sum of the thickness value of the impeller runner and the front and rear cover plates of the impeller and the clearance value of the impeller cover plates and the wear-resistant lining plate, the thickness value of the front and rear cover plates of the impeller takes 60mm, the clearance value of the impeller cover plates and the wear-resistant lining plate takes 4mm, namely the width value of the volute (liner) runner takes 578mm.
FIG. 5 shows that the performance curve of the mud pump of the invention is obtained through numerical simulation, and the flow is 12000-14000m 3 And/h, the hydraulic efficiency can reach 83% -85%, and the hydraulic performance is excellent. Through production practice inspection, the impeller designed according to the invention enhances the conveying capacity of massive rocks, effectively prevents the dredge pump from being blocked, improves the construction continuity of the dredge, further improves the construction efficiency of the dredge, and has higher economic benefit. The dredger can greatly reduce the blocking probability of a dredger pump under severe soil, reduce maintenance time, improve ship construction continuity, increase effective construction time of the dredger, and improve daily output, thereby saving cost and improving benefit.
The present invention is specifically described above, but the present invention is not limited to the above-described embodiments, and other embodiments and modifications within the scope of the present invention are also included.
Claims (1)
1. The twisted vane impeller of the large-pass spherical high-efficiency double-shell mud pump is characterized in that the overflow part of the impeller is surrounded by an impeller front cover plate (1), an impeller rear cover plate (4), a diversion cap (2), vanes (3) and a hub (5),
the number of the blades (3) is three, the adjacent blades are 120-degree intervals, the width of the blade outlet is 60% of the diameter of the impeller suction opening, the maximum sphere diameter of the impeller flow passage is 60% of the diameter of the impeller suction opening, and the blades are uniformly thickened from the inlet to the outlet;
the blade profile equation consists of two parts, namely a blade and front cover plate intersection equation and a blade and rear cover plate intersection equation:
blade and front shroud intersection equation:
blade and back cover plate intersection equation:
wherein r is 1 The unit mm is the radius of the suction port of the impeller; θ is the angle of the blade in the circumferential direction, the blade inlet is at the initial 0 °, and the blade outlet is at the end point
For the blade wrap angle, the blade wrap angle is 135 degrees, r s (θ) and r h (theta) is the distance from any point on the intersecting line of the front cover plate and the intersecting line of the rear cover plate to the center of the impeller, and the unit is mm; the blades (3) are obtained by thickening 80mm towards the outer edge of the impeller after lofting through intersecting lines of the front cover plate and the rear cover plate;
the impeller outer diameter D2 is 2040mm, the impeller suction opening diameter D1 is 850mm, and the impeller runner outlet width B2 is 510mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710366776.9A CN107100888B (en) | 2017-05-23 | 2017-05-23 | Twisted blade type impeller of large-pass spherical-diameter efficient double-shell mud pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710366776.9A CN107100888B (en) | 2017-05-23 | 2017-05-23 | Twisted blade type impeller of large-pass spherical-diameter efficient double-shell mud pump |
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| Publication Number | Publication Date |
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| CN107100888A CN107100888A (en) | 2017-08-29 |
| CN107100888B true CN107100888B (en) | 2023-06-16 |
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| CN201710366776.9A Active CN107100888B (en) | 2017-05-23 | 2017-05-23 | Twisted blade type impeller of large-pass spherical-diameter efficient double-shell mud pump |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108150448B (en) * | 2017-10-19 | 2023-09-29 | 浙江理工大学 | Impeller design method of unequal-spacing runner pump |
| CN109404332A (en) * | 2018-12-13 | 2019-03-01 | 湖南万通科技股份有限公司 | A kind of impeller and coke delivery pump |
| CN110454433B (en) * | 2019-08-27 | 2024-04-05 | 陕西科技大学 | Impeller structure for submersible pump |
| CN113719469B (en) * | 2021-09-03 | 2023-11-17 | 中交疏浚技术装备国家工程研究中心有限公司 | Design method for impeller blades of short-row-distance mud pump |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4406338A1 (en) * | 1994-02-26 | 1995-09-07 | Fink Gerhard | Double curved impeller blade |
| US6220819B1 (en) * | 2000-01-12 | 2001-04-24 | Industrial Technology Research Institute | Centrifugal pump impeller |
| CN103438022A (en) * | 2013-09-16 | 2013-12-11 | 江苏大学 | Centrifugal pump with greatly distorted blades |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2003903024A0 (en) * | 2003-06-16 | 2003-07-03 | Weir Warman Ltd | Improved pump impeller |
| JP2006291917A (en) * | 2005-04-14 | 2006-10-26 | Shin Meiwa Ind Co Ltd | Impeller for centrifugal pump and centrifugal pump having the same |
| CN101368574A (en) * | 2008-10-15 | 2009-02-18 | 许洪元 | Design method of two phase flow pump impeller |
| KR100950454B1 (en) * | 2009-12-23 | 2010-04-02 | (주)제일파워펌프 | Solids self priming pumps |
| CN103994077A (en) * | 2014-05-29 | 2014-08-20 | 戴年歌 | Vertical type slime pump |
| CN105240310B (en) * | 2015-12-03 | 2017-09-26 | 浙江工业大学之江学院 | A kind of twayblade is without blocking centrifugal impeller Hydraulic Design Method |
| CN207064319U (en) * | 2017-05-23 | 2018-03-02 | 中交疏浚技术装备国家工程研究中心有限公司 | It is a kind of to pass through the twisted blade type impeller of the efficient double wall dredge pump of sphere diameter greatly |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4406338A1 (en) * | 1994-02-26 | 1995-09-07 | Fink Gerhard | Double curved impeller blade |
| US6220819B1 (en) * | 2000-01-12 | 2001-04-24 | Industrial Technology Research Institute | Centrifugal pump impeller |
| CN103438022A (en) * | 2013-09-16 | 2013-12-11 | 江苏大学 | Centrifugal pump with greatly distorted blades |
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