CN110259720B - Gap drainage impeller for centrifugal pump and centrifugal pump with same - Google Patents

Gap drainage impeller for centrifugal pump and centrifugal pump with same Download PDF

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Publication number
CN110259720B
CN110259720B CN201910499236.7A CN201910499236A CN110259720B CN 110259720 B CN110259720 B CN 110259720B CN 201910499236 A CN201910499236 A CN 201910499236A CN 110259720 B CN110259720 B CN 110259720B
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gap
cover plate
blade
centrifugal pump
width
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CN110259720A (en
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董亮
郭瑾楠
张子龙
代翠
刘厚林
朱建成
张立新
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Jiangsu University
Zhenjiang Fluid Engineering Equipment Technology Research Institute of Jiangsu University
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Jiangsu University
Zhenjiang Fluid Engineering Equipment Technology Research Institute of 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
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
    • 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

Abstract

The invention relates to a gap drainage impeller for a centrifugal pump, which comprises a front cover plate, a rear cover plate, a hub and blades, wherein the blades comprise a front section blade and a rear section blade; a gap for drainage is arranged between the front section blade and the rear section blade; wherein the width of the gap at the front cover plate is recorded as L1The width of the gap at the rear cover plate is marked as L2，L1>L2. The invention has low cavitation degree in the gap drainage impeller and improves the hydraulic performance of the centrifugal pump in a certain working condition range.

Description

Gap drainage impeller for centrifugal pump and centrifugal pump with same
Technical Field
The invention relates to the technical field of centrifugal pumps, in particular to a gap drainage impeller for a centrifugal pump and the centrifugal pump with the gap drainage impeller.
Background
The centrifugal pump is used as a general machine, plays a vital role in both the traditional field and the special field, and puts forward higher requirements on the running stability of the centrifugal pump along with the continuous development and progress of science and technology in each field. In actual operation, centrifugal pumps can cavitate for a variety of reasons. The occurrence of cavitation tends to affect the normal flow of fluid within the pump, causing the pump to degrade in performance. When the cavitation is serious, the whole system can not normally operate, and even the whole system is damaged. Therefore, the hydraulic performance of the centrifugal pump is improved, and the centrifugal pump also has better cavitation performance, which is very important for ensuring the safe, stable and efficient operation of the unit.
The traditional centrifugal pump impeller has a complex internal flow field structure and poor cavitation resistance. The invention provides a gap drainage centrifugal pump impeller aiming at the prior art.
Disclosure of Invention
In order to solve at least one technical problem, in a first aspect, the present invention provides a gap-inducing impeller for a centrifugal pump, including a front cover plate, a rear cover plate, a hub and blades, wherein the blades include a front blade and a rear blade; a gap for drainage is arranged between the front section blade and the rear section blade;
wherein the width of the gap at the front cover plate is recorded as L1The width of the gap at the rear cover plate is marked as L2，L1>L2。
Optionally, a width L of the gap at the front cover plate1The following conditions are satisfied:
Figure BDA0002089631750000011
Figure BDA0002089631750000021
wherein:
delta-the true thickness of the blade, m;
ns-specific speed;
n-rotation speed, r/min;
q-flow, m3/h；
H-the pump head, m.
Optionally, a width L of the gap at the back cover plate2The following conditions are satisfied:
Figure BDA0002089631750000022
wherein:
L1-the width of the gap at the front cover plate, m;
ns-specific speed.
Optionally, the aft section blade fillet radius R1The following conditions are satisfied:
R1＝9L1
wherein L is1The width of the gap at the front cover plate, m.
Optionally, the front blade fillet radius is set to R2The following conditions are satisfied:
R2＝3L1
wherein L is1The width of the gap at the front cover plate, m.
Optionally, the slotting position angle is set to β3The following conditions are satisfied:
Figure BDA0002089631750000023
wherein: beta is a4-blade wrap angle, °;
D2-impeller exit diameter, m;
n-rotation speed, r/min;
z is the number of leaves.
Optionally, the grooving direction angle is set to β2The following conditions are satisfied:
Figure BDA0002089631750000031
wherein:
β1-blade setting angle, °;
β3-slot position angle, °;
β4-blade wrap angle, °.
In a second aspect, the present invention provides a centrifugal pump having the above-described gap-inducing impeller.
The gap drainage impeller has the beneficial effects that:
the gap drainage impeller provided by the invention has the advantages that the gap width is different at the front cover plate and the rear cover plate, the cavitation degree difference of the front cover plate and the rear cover plate is considered, and the gap drainage impeller is more practical.
Furthermore, the radius of the fillet of the rear-section blade of the gap-drainage impeller is as large as possible, so that the vortex can be effectively prevented from being generated at the rear-section blade, and the loss is reduced.
Furthermore, the invention provides the main geometric parameters of the blade, including the design of the position of the gap, the width of the gap, the radius of the rounded angle of the blade and the like, compared with the traditional impeller centrifugal pump, the degree of hollowing in the impeller of the centrifugal pump is obviously reduced, and the hydraulic performance of the centrifugal pump is improved in a certain working condition range.
Drawings
Fig. 1 is a half sectional view of a centrifugal pump impeller according to the present invention.
Fig. 2 is a schematic view of a gap guide vane according to the present invention.
Fig. 3(a) is a pressure cloud before optimization according to the present invention.
Fig. 3(b) is a pressure cloud before optimization according to the present invention.
In the figure: 1-front cover plate, 2-rear cover plate, 3-hub, 4-blade, 5-gap, a-front blade and b-rear blade.
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.
As shown in fig. 1 and 2, a gap-inducing impeller for a centrifugal pump includes a front shroud 1, a rear shroud 2, a hub 3 and blades 4;
the blades 4 comprise a front blade a and a rear blade b, and the blades 4 are provided with gaps 5 with a drainage function.
In order to reduce the losses after the fluid has flowed out of the gap 5 and to avoid vortices at the inlet of the rear blade b, the latter blade b is rounded off with a radius R1Should be as large as possible.
Since the cavitation condition near the front cover plate 1 is more severe than that of the rear cover plate 2, the width of the gap 5 is not uniform. The width L of the gap 5 at the front cover plate 11Is larger than the rear cover plate 2Width L of2。
In some embodiments, the width of the gap 5 at the front cover plate 1 is set to L1The following conditions are satisfied:
Figure BDA0002089631750000041
Figure BDA0002089631750000042
wherein:
L1-the width of the gap at the front cover plate, m;
ns-specific speed;
delta-the true thickness of the blade, m;
n-rotation speed, r/min;
q-flow, m3/s；
H-the pump head, m.
In some embodiments, the width of the gap 5 at the back cover plate 2 is set to L2Satisfy the following
Conditions are as follows:
Figure BDA0002089631750000051
wherein:
L1-the width of the gap at the back cover plate, m;
L1-the width of the gap at the front cover plate, m;
ns-specific speed.
In some embodiments, to reduce losses after the fluid exits the gap 5 and avoid vortices at the inlet of the rear blade b, the rear blade b is rounded with a radius R1Should be as large as possible, satisfying the following conditions:
R19L formula (4)
Wherein L is1The width of the gap at the front cover plate, m.
In some embodiments, the leading blade a fillet radius is set to R2The following conditions are satisfied:
R2＝3L1formula (5)
Wherein L is1The width of the gap at the front cover plate, m.
In some embodiments, the slot position angle is set to β3The following conditions are satisfied:
Figure BDA0002089631750000052
wherein:
β4-blade wrap angle, °;
D2-impeller exit diameter, m;
n-rotation speed, r/min;
z is the number of leaves.
In some embodiments, the grooving direction angle is set to β2The following conditions are satisfied:
Figure BDA0002089631750000061
wherein:
β1-blade setting angle, °;
β3-slot position angle, °;
β4-blade wrap angle, °.
According to the gap-drainage centrifugal pump impeller, when fluid passes through the gap, the fluid on the high-pressure surface is introduced into the low-pressure surface due to the flow guiding effect of the front-section blades and the existence of the gap, so that the pressure of the low-pressure surface is compensated, and the gap-drainage centrifugal pump impeller has a better anti-cavitation characteristic than a traditional centrifugal pump impeller.
Specifically, taking a centrifugal pump impeller of a certain factory as an example, the impeller blade placement angle β120 DEG, blade wrap angle beta4120 degrees, blade thickness delta 0.004m, blade number z 5, and pump flow rate Q0.049m3(s), pump head H is 50m, rotating speed n is 2950r/min, and diameter D of outlet of impeller20.29m, calculated according to the above formula (1) and formula (2), ns＝126.8，L1＝0.0085m。
Mixing L with1Substituting 0.0085m into formula (3) to obtain L2＝0.0051m。
Mixing L with1Substituting 0.0085m into formula (4) to obtain R1＝0.0765m。
Mixing L with1Substituting 0.0085m into formula (5) to obtain R2＝0.0255m。
According to the blade angle of wrap beta4120 degrees, number of blades z 5, diameter of impeller outlet D2When the rotating speed n is 2950r/min and the m is 0.29m, the beta is calculated3＝45°。
According to beta3Calculated by substituting 45 ° into equation (7), β2＝80°。
In this embodiment, as shown in fig. 3, a pressure cloud before blade optimization of the conventional method is given, as shown in fig. 3(a) in particular, and a pressure cloud after blade optimization by gap drainage, as shown in fig. 3(b) in particular. As can be seen from FIG. 3, the pressure difference between the working surface and the suction surface of the optimized front blade is large, the pressure of the suction surface is low, and cavitation is easy to occur. After optimization, due to the diversion effect of the front-section blades and the existence of the gaps, fluid on the working surface is introduced into the suction surface, the pressure of the suction surface is compensated, so that the pressure difference between the front-section blades and the suction surface is small, and cavitation is not easy to occur.
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 (6)

1. A gap drainage impeller for a centrifugal pump is characterized by comprising a front cover plate, a rear cover plate, a hub and blades, wherein the blades comprise a front section of blade and a rear section of blade; a gap for drainage is arranged between the front section blade and the rear section blade;
wherein the width of the gap at the front cover plate is recorded as L1The width of the gap at the rear cover plate is marked as L2，L1>L2；
The width L of the gap at the front cover plate1And a width L at the rear cover plate2The following conditions are satisfied:
Figure FDA0003216564990000011
Figure FDA0003216564990000012
Figure FDA0003216564990000013
wherein, delta is the real thickness of the blade, m; n issIs the specific rotating speed; n is the rotating speed, r/min; q is the flow, m3H; h is the pump head, m.
2. A gap-inducing impeller for a centrifugal pump according to claim 1, wherein the aft-stage blade fillet radius R1The following conditions are satisfied:
R1＝9L1
wherein L is1Is the gap width m at the front cover plate.
3. A gap-inducing impeller for a centrifugal pump according to claim 1, wherein the leading blade fillet radius is set to R2The following conditions are satisfied:
R2＝3L1
wherein L is1Is the gap width m at the front cover plate.
4. According to the rightThe gap-inducing impeller for centrifugal pumps of claim 1 wherein the notch position angle is set to β3The following conditions are satisfied:
Figure FDA0003216564990000021
wherein, beta4Is the leaf wrap angle, °; d2Is the diameter of the impeller outlet, m; n is the rotating speed, r/min; z is the number of leaves.
5. A gap-inducing impeller for a centrifugal pump according to claim 1, wherein the grooving direction angle is set to β2The following conditions are satisfied:
Figure FDA0003216564990000022
wherein, beta1Setting the angle of the leaves; beta is a3Is the slot position angle, °; beta is a4Is the leaf wrap angle.
6. A centrifugal pump, characterized by a gap-inducing impeller according to any one of claims 1-5.
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Publication number Priority date Publication date Assignee Title
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CN104613003A (en) * 2014-11-26 2015-05-13 江苏大学 Hydraulic design method for low-specific-speed overload-free centrifugal pump impeller
CN208294826U (en) * 2018-05-18 2018-12-28 浙江青霄科技股份有限公司 Centrifugal pump impeller

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FR2743113B1 (en) * 1995-12-28 1998-01-23 Inst Francais Du Petrole DEVICE FOR PUMPING OR COMPRESSING A TANDEM BLADED POLYPHASTIC FLUID
CN108425704B (en) * 2013-01-23 2020-05-22 概创机械设计有限责任公司 Turbine comprising a flow guiding structure
CN105257557A (en) * 2015-11-25 2016-01-20 湘潭金阳电机泵业有限公司 Efficient low-lift submersible sewage pump
CN105626575B (en) * 2015-12-29 2019-05-24 西安航天动力研究所 Multistage blade centrifugal wheel
CN105604977A (en) * 2016-01-25 2016-05-25 江苏大学 Single channel pump impeller provided with single slotted envelope blade
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Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN204099272U (en) * 2014-09-24 2015-01-14 浙江理工大学 A kind of low specific-speed centrifugal pump impeller
CN104613003A (en) * 2014-11-26 2015-05-13 江苏大学 Hydraulic design method for low-specific-speed overload-free centrifugal pump impeller
CN208294826U (en) * 2018-05-18 2018-12-28 浙江青霄科技股份有限公司 Centrifugal pump impeller

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