CN108443218B - Pump impeller with secondary splitter blade - Google Patents

Pump impeller with secondary splitter blade Download PDF

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CN108443218B
CN108443218B CN201810530207.8A CN201810530207A CN108443218B CN 108443218 B CN108443218 B CN 108443218B CN 201810530207 A CN201810530207 A CN 201810530207A CN 108443218 B CN108443218 B CN 108443218B
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blade
inlet
theta
outlet
splitter blade
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CN108443218A (en
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王凯
芦鑫
刘厚林
谈明高
王勇
董亮
李钰
张子旭
景玉成
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Jiangsu University
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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

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  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention belongs to the field of design of a vane pump, and particularly discloses a pump impeller with secondary splitter vanesThe long blade, the primary splitter blade, the secondary splitter blade I and the secondary splitter blade II; the blades are twisted blades, and the number of the blades is 3; the diameter of an inlet of the primary splitter blade is 0.42-0.46D2The inlet and the outlet of each blade are respectively offset by 0.4-0.5 theta and 0.4-0.5 theta along the rotation direction of the impeller, and theta is an included angle between two adjacent long blades; the diameter of an inlet of the first secondary splitter blade is 0.61-0.64D2The inlet and the outlet of the blade are respectively offset by 0.2-0.25 theta and 0.2-0.25 theta along the rotation direction of the impeller; the diameter of the inlet of the second splitter blade is 0.65-0.75D2The inlet and the outlet of the blade are respectively offset by 0.65-0.75 theta and 0.7-0.8 theta along the rotation direction of the impeller; the thickness of the second secondary splitter blade is additionally thickened towards the suction surface of the adjacent blade at the outlet, and the maximum thickness of the blade is 1.3-1.6 times that of the long blade. The invention can inhibit or reduce the phenomena of internal flow separation, jet flow-wake and the like of the pump impeller and improve the operation efficiency of the pump under the working condition of small flow.

Description

Pump impeller with secondary splitter blade
Technical Field
The invention belongs to the field of design of vane pumps, and particularly relates to a pump impeller with secondary splitter vanes.
Background
With the rapid development of the fields of petroleum, chemical industry, aerospace, metallurgy, light industry and the like, the performance of the pump develops towards high speed, high pressure, high efficiency and high power, and the low specific speed pump has the characteristics of small flow and high lift, and is widely applied to the industries.
At present, a low specific speed pump is mostly a centrifugal pump composite impeller as described in chinese patent documents (application number: 201520005753.1, respectively; publication number: CN204419688U ] primary splitter vane wheel has the advantages that the number of vanes is increased while no displacement is generated at the inlet of the vane wheel, but the primary splitter vane wheel still has the condition of insufficient vane density, when the primary splitter vane wheel operates under a low flow working condition, the vanes are insufficient in fluid restraint at the outlet, and the outlet of the vane wheel is prone to generate phenomena such as jet flow-wake, secondary flow, etc., resulting in great hydraulic loss, thereby resulting in low operating efficiency of the pump.
On the basis of this, a secondary splitter vane type centrifugal impeller described in chinese patent document [ application No.: 200910023223.9, respectively; publication number: CN101598138A discloses a secondary splitter impeller applied to a centrifugal compressor, a high-speed compound centrifugal pump [ application number: 96203683.8, respectively; publication number: CN2265446Y discloses a long, medium and short composite impeller, wherein a secondary flow dividing technology is applied to a low specific speed pump, but the above documents only increase the number of blades, and do not deeply explain the influence of reasonable combination between the blades on the pump performance, and do not consider the interaction between the volute and the impeller and the condition that the flows of the flow channels inside the impeller are different, and the same short blades are used in different flow channels for flow dividing, so that the flow rates in the adjacent flow channels of the flow dividing blades are different, the flow rate flowing into the pump body is not uniform, and the hydraulic losses in the impeller and outside the outlet of the impeller are increased. Secondly, the above documents do not consider the influence of the inlet diameter of the splitter blade in the low specific speed centrifugal pump on the flow in the flow passage, so that when the impeller related to the documents operates under the working condition of low flow, the suction surface of the inlet of the splitter blade may generate flow separation, the flow inside the impeller is disturbed, and the hydraulic loss inside the impeller is increased.
Disclosure of Invention
The invention aims to provide a pump impeller with secondary splitter blades, which adopts different short blades aiming at different flow channels, so that the internal flow of adjacent flow channels of the splitter blades is equal, and the hydraulic loss inside the impeller and outside the outlet edge of the impeller is effectively reduced.
In order to achieve the purpose, the following technical scheme is adopted:
a pump impeller with secondary splitter blades comprises a front cover plate, a rear cover plate, long blades, primary splitter blades, a primary splitter blade and a secondary splitter blade.
The long blades, the primary splitter blade and the secondary splitter blade are twisted blades, and the number of the blades is 3.
The long blades are uniformly distributed in the circumferential direction of the impeller; the first splitter blade is positioned in a flow channel formed by two adjacent long blades, the first secondary splitter blade is positioned in the flow channel between the suction surface of the long blade and the pressure surface of the first splitter blade, and the second secondary splitter blade is positioned in the flow channel between the suction surface of the first splitter blade and the pressure surface of the adjacent long blade.
Inlet diameter D of primary splitter bladesi2＝0.42～0.46D2The blade offset direction is along the rotation direction of the impeller, and the inlet offset degree thetasi20.4-0.5 theta, outlet offset thetaso20.4-0.5 theta, and an inlet angle β1215-25 DEG and an outlet placing angle
Figure BDA0001677018540000021
Wherein a is2Is the absolute value of the difference value of the inlet and outlet offset degrees of the primary splitter blade,
Figure BDA0001677018540000023
is the wrap angle of the primary splitter blade2Is the blade cascade distance between two adjacent long blades on the diameter of the inlet of the primary splitter blade2＝2πDsi2/3，β12Is the inlet setting angle R of the primary splitter blade2Is the radius of curvature of the primary splitter blade.
Inlet diameter D of first secondary splitter bladesi3＝0.61～0.64D2The blade offset direction is along the rotation direction of the impeller, and the inlet offset degree thetasi3＝0.2～0.25θ、Degree of outlet offset thetaso30.2-0.25 theta, inlet mounting angle β1325-35 DEG and an outlet placing angle
Figure BDA0001677018540000024
Figure BDA0001677018540000025
Wherein a is3Is the absolute value of the difference value of the inlet and outlet offset degrees of the first secondary splitter blade,
Figure BDA0001677018540000026
is the wrap angle of the first secondary splitter blade3The cascade pitch, l, between two adjacent long blades on the diameter of one inlet of the secondary splitter blade3＝2πDsi3/3，β13The inlet placing angle R of the first secondary splitter blade3The radius of curvature of the first secondary splitter blade.
Inlet diameter D of secondary splitter blade IIsi4＝0.65～0.75D2Degree of inlet offset thetasi40.7-0.8 theta, outlet offset thetaso40.7-0.85 theta, the blade offset direction along the impeller rotation direction, and the inlet placement angle β1425-35 DEG and an outlet placing angle
Figure BDA0001677018540000027
Figure BDA0001677018540000028
Wherein a is4Is the absolute value of the difference value of the inlet and outlet offset degrees of the second-order splitter blade II,
Figure BDA0001677018540000029
is the wrap angle of the second splitter blade II4The cascade distance between two adjacent long blades on the diameter of the second inlet of the secondary splitter blade is l4＝2πDsi4/3，β14The inlet setting angle R of the second splitter blade II4The radius of curvature of the second splitter blade II is shown;
wherein D is2Is the diameter of the impeller outlet, theta is the phaseAngle between two adjacent long blades, β2An angle is set for the outlet of the long blade.
Wrap angle of long blade
Figure BDA00016770185400000210
Outlet placement angle β2The angle of the blade is 35-45 degrees, the blade is gradually thickened from the inlet edge to the outlet edge, and the maximum thickness delta t of the blade is1＝3～5mm。
The second blade of the secondary splitter blade is gradually thickened from the inlet edge to the outlet edge, the outlet of the blade is additionally thickened towards the suction surface of the adjacent blade, and the maximum thickness delta t of the blade4＝1.3～1.6Δt1Wrap angle
Figure BDA00016770185400000211
Outlet placement angle β24＝45～50°。
The invention has the advantages that:
(1) the invention adopts a secondary flow dividing mode, ensures that the impeller inlet is extruded, increases the number of blades, and reduces the occurrence of flow separation in the impeller by reasonable blade collocation, thereby improving the lift coefficient of the pump.
(2) The invention adopts different forms of short blades to divide the flow in different flow passages, so that the fluid in different flow passages is sufficiently restricted, and the phenomena of internal flow separation, jet flow-wake and the like in the impeller of the pump can be inhibited or reduced, thereby improving the operating efficiency of the pump under the working condition of low flow.
Drawings
FIG. 1 is a schematic structural view of a pump impeller with secondary splitter vanes according to the present invention;
FIG. 2 is a graph comparing the external characteristics of a pump impeller designed according to an embodiment of the present invention and a conventional splitter vane approach;
in the figure: the novel wind turbine blade comprises a front cover plate 1, a rear cover plate 2, a long blade 3, a primary splitter blade 4, a secondary splitter blade 5 and a secondary splitter blade 6.
Detailed Description
The invention will be further described with reference to the following figures and specific examples, but the scope of the invention is not limited thereto.
Example (b):
a centrifugal pump with a specific speed of 48 has the design parameters that: design flow Qd＝16m3H, the lift H is 35m, and the rotating speed n is 2860 r/min. The main geometric parameters of the impeller are: impeller exit diameter D2220mm, impeller inlet diameter D150mm, impeller exit width b2＝6mm。
As shown in fig. 1, a pump impeller with secondary splitter blades comprises a front cover plate, a rear cover plate, long blades, primary splitter blades, a first secondary splitter blade and a second secondary splitter blade, wherein all the blades are twisted blades, and the number of the blades is 3.
As shown in fig. 1, the long blades are uniformly distributed in the circumferential direction of the impeller; the primary splitter blade is positioned in a flow channel formed by two adjacent long blades; the first secondary splitter blade is positioned in a flow channel between the suction surface of the long blade and the pressure surface of the first splitter blade; and the secondary splitter blade is positioned in a flow channel between the suction surface of the primary splitter blade and the pressure surface of the adjacent long blade. The included angle theta between the adjacent long blades is 60 degrees.
As shown in FIG. 1, the inlet diameter D of the primary splitter bladesi297.5mm inlet offset thetasi20.45 theta 27 DEG, outlet offset thetaso2＝0.45θ＝27°、R274mm blade wrap angle
Figure BDA0001677018540000031
Inlet placement angle β12The blade grid distance l between two adjacent long blades on the diameter of the inlet of the primary splitter blade is 16 degrees2204.2mm long blade exit setting angle β242 ° blade offset direction along impeller rotation direction, exit placement angle β22＝42°。
As shown in the attached figure 1, the inlet diameter D of the first secondary splitter bladesi3137mm, inlet offset thetasi30.225 theta 13.5 DEG outlet offset thetaso30.245 theta 14.7 DEG, blade wrap angle
Figure BDA0001677018540000032
R3125mm, inlet angle β 1330 DEG, the cascade distance l between two adjacent long blades on the diameter of one inlet of the secondary splitter blade3286.9mm, blade offset direction along impeller rotation direction, outlet setting angle β23＝46°。
As shown in figure 1, the long blade adopts wrap angleOutlet placement angle β242 DEG, the maximum thickness of the blade is delta t1＝4mm。
As shown in the attached figure 1, the inlet diameter D of the second splitter blade IIsi4152mm, inlet offset thetasi40.725 theta 43.5 DEG, outlet offset thetaso40.775 theta 46.5 DEG, blade offset direction along impeller rotation direction, blade maximum thickness delta t46mm blade wrap angle
Figure BDA0001677018540000041
R480mm, inlet angle β14The cascade distance l between two adjacent blades on the diameter of the second inlet of the secondary splitter blade is 25 degrees4318.3mm, blade offset direction along impeller rotation direction, outlet setting angle β24＝48°。
In order to verify the effectiveness of the pump impeller with the secondary splitter blade, CFD numerical calculation is respectively carried out on the pump designed by the traditional splitter blade method and the pump designed by the invention, the external characteristic calculation result is shown in figure 2, Q is actual flow, H is lift, and η is pump efficiency.
The present invention is not limited to the above-described embodiments, and any obvious improvements, substitutions or modifications can be made by those skilled in the art without departing from the spirit of the present invention.

Claims (3)

1. A pump impeller with secondary splitter blades is characterized by comprising a front cover plate, a rear cover plate, long blades, primary splitter blades, a primary splitter blade and a secondary splitter blade;
the long blades, the primary splitter blade, the first secondary splitter blade and the second secondary splitter blade are all twisted blades, and the number of the blades is 3;
the long blades are uniformly distributed in the circumferential direction of the impeller, the primary splitter blade is positioned in a flow channel formed by two adjacent long blades, the primary splitter blade is positioned in the flow channel between the suction surface of the long blade and the pressure surface of the primary splitter blade, and the secondary splitter blade is positioned in the flow channel between the suction surface of the primary splitter blade and the pressure surface of the adjacent long blade;
the inlet diameter D of the primary splitter bladesi2＝0.42～0.46D2The blade offset direction is along the rotation direction of the impeller, and the inlet offset degree thetasi20.4-0.5 theta, outlet offset thetaso20.4-0.5 theta, inlet placement angle β12＝15-25 DEG and an outlet placing angle
Figure FDA0002048789620000011
Figure FDA0002048789620000012
Wherein a is2The absolute value of the difference value of the inlet and outlet offset degrees of the primary splitter blade,
Figure FDA0002048789620000013
is the wrap angle of the primary splitter blade,/2The blade row distance between two adjacent long blades on the diameter of the inlet of the primary splitter blade is l2＝2πDsi2/3，β12For the inlet setting angle, R, of the primary splitter vane2The radius of curvature of the primary splitter blade;
the diameter D of the inlet of the first secondary splitter bladesi3＝0.61～0.64D2The blade offset direction is along the rotation direction of the impeller, and the inletDegree of offset thetasi30.2-0.25 theta, outlet offset thetaso30.2-0.25 theta, inlet mounting angle β13＝25-35 DEG and an outlet placing angle
Figure FDA0002048789620000014
Wherein a is3The absolute value of the difference value of the inlet and outlet offset degrees of the first secondary splitter blade,
Figure FDA0002048789620000016
is the wrap angle of the first secondary splitter blade3The cascade pitch, l, between two adjacent long blades on the diameter of one inlet of the secondary splitter blade3＝2πDsi3/3，β13Is the inlet placing angle R of the first secondary splitter blade3The radius of curvature of the first secondary splitter blade;
the diameter D of the inlet of the second splitter bladesi4＝0.65～0.75D2The blade offset direction is along the rotation direction of the impeller, and the inlet offset degree thetasi40.7-0.8 theta, outlet offset thetaso40.7-0.85 theta, inlet mounting angle β14＝25-35 DEG and an outlet placing angle
Figure FDA0002048789620000017
Wherein a is4The absolute value of the difference value of the inlet and outlet offset degrees of the second secondary splitter blade II,is the wrap angle of the second secondary splitter blade II4The cascade distance between two adjacent long blades on the diameter of the second inlet of the secondary splitter blade is l4＝2πDsi4/3，β14Is the second splitter bladeInlet angle of (R)4The radius of curvature of the second secondary splitter blade II is defined as the radius of curvature of the second secondary splitter blade II;
wherein D is2Theta is the angle between two adjacent long blades, β, and is the diameter of the outlet of the impeller2An angle is set for the outlet of the long blade.
2. A pump impeller with secondary splitter vanes according to claim 1, wherein the wrap angle of the long vanes
Figure FDA00020487896200000110
Outlet placement angle β2The angle of the blade is 35-45 degrees, the blade is gradually thickened from the inlet edge to the outlet edge, and the maximum thickness delta t of the blade is1＝3～5mm。
3. The impeller according to claim 2, wherein the second splitter blade has a blade exit setting angle β24The angle of the blade is 45-50 degrees, the blade is gradually thickened from the inlet edge to the outlet edge, the blade outlet is additionally thickened to the suction surface of the adjacent blade, and the maximum thickness delta t of the blade is4＝1.3～1.6Δt1Wrap angle
Figure FDA0002048789620000021
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109882446B (en) * 2019-01-09 2020-11-03 江苏大学 Design method of low specific speed centrifugal pump impeller splitter blade
CN109989943B (en) * 2019-04-18 2021-06-22 江苏大学 Design method of multi-stage pump reverse guide vane splitter blade

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0205001A1 (en) * 1985-05-24 1986-12-17 A. S. Kongsberg Väpenfabrikk Splitter blade arrangement for centrifugal compressors
JPH0318697A (en) * 1989-06-15 1991-01-28 Matsushita Electric Ind Co Ltd Electro-motive air blower
CN2426027Y (en) * 1999-03-13 2001-04-04 格伦德福什联合股份有限公司 Radial structure type impeller for centrifugal pump
CN101598138A (en) * 2009-07-07 2009-12-09 西安交通大学 Secondary splitter blade type centrifugal impeller
JP2011094544A (en) * 2009-10-30 2011-05-12 Panasonic Corp Electric blower and electric vacuum cleaner using the same

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0205001A1 (en) * 1985-05-24 1986-12-17 A. S. Kongsberg Väpenfabrikk Splitter blade arrangement for centrifugal compressors
JPH0318697A (en) * 1989-06-15 1991-01-28 Matsushita Electric Ind Co Ltd Electro-motive air blower
CN2426027Y (en) * 1999-03-13 2001-04-04 格伦德福什联合股份有限公司 Radial structure type impeller for centrifugal pump
CN101598138A (en) * 2009-07-07 2009-12-09 西安交通大学 Secondary splitter blade type centrifugal impeller
JP2011094544A (en) * 2009-10-30 2011-05-12 Panasonic Corp Electric blower and electric vacuum cleaner using the same

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