CN105179307A - Wear-resistance centrifugal slurry pump impeller hydraulic design method - Google Patents

Abstract

The invention relates to a slurry pump impeller hydraulic design method, in particular to a wear-resistance centrifugal slurry pump impeller hydraulic design method. The method determines such important design parameters of an impeller as an impeller inlet diameter D0, an impeller outlet diameter D2, an impeller inlet width b1, a blade outlet width b2, a blade inlet placing angle beta 1, a blade outlet placing angle beta 2 and a blade wrap angle phi through formulas. Through practical inspection, the method greatly improves the wear resistance and the design standard of a slurry pump; and the slurry pump, designed and produced by the method, is excellent in use performance and higher in economic benefit.

Description

One is resistance to worn centrifugal type slurry pump impeller Hydraulic Design Method

Technical field

The present invention relates to a kind of screenings pump impeller Hydraulic Design Method, particularly one is resistance to worn centrifugal type slurry pump impeller Hydraulic Design Method.

Background technique

Generally the pump containing suspended solids in liquid (water) is carried to be called Pulp pump by being applicable to.One of indispensable equipment in ore dressing, each technological process of coal preparation plant at present.The one machinery of Pulp pump by making solid, liquid mixed medium energy increase by the effect of centrifugal force (rotation of the impeller of pump).Be widely used in the industry fields such as mine, chemical industry, coal, food, metallurgy, building materials and oil.Pulp pump can be divided in single-stage/multistage, single suction/double suction, cantilever, horizontal/vertical and pump case level by distinct principle opens the/pattern such as vertical combination.Along with the fast development of industry-by-industry.Under the prior art, the Hydraulic Design Method of slurry pump impeller depends on the experience of artificer, and such design method and the experience of artificer have a lot of relation, and uncertain factor is a lot, design cost is higher, can not meet the requirement of current market to Pulp pump.Therefore, be necessary to do the Hydraulic Design Method of slurry pump impeller further perfect.

Mainly contain following through retrieval slurry pump impeller Hydraulic Design Method: the patent No. is " a kind of Assembled slag pulp pump impeller " utility model patent of ZL03213328.6, artificer have employed fabricated structure in that patent, makes the structure of blade, blade body and apron plate be easy to manufacture processing; The patent No. is " slurry pump impeller " utility model patent of ZL201020293027.1, artificer improves blade wheel structure in that patent, reduce the gap of impeller outer sheath and primary blades, make the pressure increase between these two parts, reduce the vibration of Pulp pump.

Goal of the invention

Existing centrifugal type slurry pump impeller Hydraulic Design Method is also incomplete, even the Hydraulic Design Method of the slurry pump impeller of individual species also has a lot of place to have pending improvement.The object of the invention is to, a kind of science, efficient centrifugal type slurry pump impeller Hydraulic Design Method is provided, improves the flowing state of Pulp pump inside, improve Pulp pump antiwear property, increase the service life.

Summary of the invention

The present invention has taken into full account the worked environment of Pulp pump, considers the impact of size of grain on pump operation situation, improves the design method of slurry pump impeller design parameter, to ensure the stable, reliable and efficient of Pulp pump work.

The technological scheme that object adopts is:

(1) Pulp pump performance parameter P, Q, H, β ₂be applicable to following relation:

$P=K_u\mathrm{\ρ}g\sqrt{2gH}\[{\mathrm{\σu}}_2-Q/\left(S_2{\mathrm{tan\β}}_2\right)\]$

In formula:

The flow of Q-design conditions, rice ³/ second;

The lift of H-design conditions, rice;

The air horsepower of P-design conditions, kilowatt;

G-gravity accleration, meter per second ²;

σ-Douglas slip coefficient;

U ₂-blade exit peripheral velocity, meter per second;

β ₂-blade exit laying angle, degree;

K _u-velocity coefficient;

ρ-fluid density, kg/m ³;

S ₂-outlet area of passage, square metre;

(2) velocity coefficient K _u, design formula is as follows:

$K_u=1.936e^{-{\left(\frac{n_s-766.5}{930.1}\right)}^2}$

In formula:

N _s-specific speed;

(3) impeller inlet diameter D ₀, design formula is as follows:

$D_0=3.47e^{\frac{n_s}{1154}}\·\sqrt[3]{Q\·}(0.05596n_s+75.46)/(n_s+318.7)$

In formula:

D ₀-impeller inlet diameter, rice;

N _s-specific speed;

The flow of Q-design conditions, rice ³/ second;

(4) impeller outlet diameter D ₂, design formula is as follows:

In formula:

D ₂-impeller outlet diameter, rice;

N _s-specific speed;

The flow of Q-design conditions, rice ³/ second;

K ₂-impeller outlet diametral quotient;

The lift of H-design conditions, rice;

(5) impeller outlet diametral quotient K ₂, design formula is as follows:

K ₂＝8.615n _s ^0.01898

In formula:

K ₂-impeller outlet diametral quotient;

N _s-specific speed;

(6) vane inlet width b ₁, design formula is as follows:

$b_1=0.1574e^{0.002162n_s}{D}_2$

In formula:

B ₁-vane inlet width, rice;

N _s-specific speed;

D ₂-impeller outlet diameter, rice;

(7) blade exit width b ₂, design formula is as follows:

$b_2=K_b\sqrt[3]{Q}(0.05596n_s+75.46)/(n_s+318.7)$

In formula:

B ₂-blade exit width, rice;

N _s-specific speed;

K _b-impeller outlet diametral quotient;

The flow of Q-design conditions, rice ³/ second;

(8) impeller outlet diametral quotient K _b, design formula is as follows:

K _b＝(0.06288n _s ²+16.16n _s+0.0002576)/(n _s+0.000163)

In formula:

K _b-impeller outlet diametral quotient;

N _s-specific speed;

(9) vane inlet laying angle β ₁, design formula is as follows:

In formula:

β ₁-vane inlet laying angle, degree;

N _s-specific speed;

(10) blade exit laying angle β ₂, design formula is as follows:

In formula:

β ₂-blade exit laying angle, degree;

N _s-specific speed;

(11) subtended angle of blade φ, design formula is as follows:

In formula:

φ-subtended angle of blade, degree;

N _s-specific speed;

According to above step, can obtain a kind of science, system, the design method of accurate impeller major parameter.The main geometric parameters of impeller can be determined by above-mentioned computational methods, comprise impeller inlet diameter D ₀, impeller outlet diameter D ₂, vane inlet width b ₁, blade exit width b ₂, vane inlet laying angle β ₁, blade exit laying angle β ₂, subtended angle of blade φ etc.The slurry pump impeller designed by above step meets the flow characteristic of its fed sheet of a media more, enhance the wear resistance of Pulp pump, ensure that the fluency that pump inner fluid flows, make the performance of Pulp pump become more reliable and more stable, wear resistance is higher, and effective run time is longer.

Accompanying drawing explanation

Below in conjunction with the drawings and specific embodiments, the present invention is further described.

Fig. 1 is the axial plane figure of slurry pump impeller.

Fig. 2 is the planimetric map of slurry pump impeller.

In Fig. 1: D ₀-impeller inlet diameter; D ₂-impeller outlet diameter; b ₁-vane inlet width; b ₂-blade exit width; D _i-blade passage center line distance is from the distance of axis; R _dS-front shroud of impeller radius of arc; R _tS-back shroud of impeller radius of arc.

In Fig. 2: β ₁-vane inlet laying angle; β ₂-blade exit laying angle; φ-subtended angle of blade.

Embodiment

The present invention determines to comprise 1 impeller inlet diameter D by following formula ₀, 2 impeller outlet diameter D ₂, 3 vane inlet width b ₁, 4 blade exit width b ₂, 5 vane inlet laying angle β ₁, 6 blade exit laying angle β ₂, the slurry pump impeller such as 7 subtended angle of blade φ important design parameter.

This embodiment is under the prerequisite of given design conditions flow Q, design conditions lift H, design conditions rotating speed n, calculates impeller parameters:

$P=K_u\mathrm{\ρ}g\sqrt{2gH}\[{\mathrm{\σu}}_2-Q/\left(S_2{\mathrm{tan\β}}_2\right)\]$

$K_u=1.936e^{-{\left(\frac{n_s-766.5}{930.1}\right)}^2}$

$D_0=3.47e^{\frac{n_s}{1154}}\·\sqrt[3]{Q\·}(0.05596n_s+75.46)/(n_s+318.7)$

K ₂＝8.615n _s ^0.01898

$b_1=0.1574e^{0.002162n_s}{D}_2$

$b_2=K_b\sqrt[3]{Q}(0.05596n_s+75.46)/(n_s+318.7)$

K _b＝(0.06288n _s ²+16.16n _s+0.0002576)/(n _s+0.000163)

The present invention is generally applicable to the Impeller Design of high low-specific-speed centrifugal type slurry pump, and above design formula considers the flow characteristic in Pulp pump all sidedly.

Through production practices inspection, present invention greatly enhances design efficiency and the design level of Pulp pump, reduce design cost and risk, the Pulp pump designing production according to the present invention has good usability and higher economic benefit.

That more than makes with reference to embodiment for patent of the present invention illustrates, but the present invention is not limited to above-described embodiment, also comprises other embodiments in concept of the present invention or variation.

Claims (5)

1. to resistance to wear a centrifugal type slurry pump impeller Hydraulic Design Method, the main geometric parameters of Impeller Design is provided, comprises impeller inlet diameter D ₀, impeller outlet diameter D ₂, vane inlet width b ₁, blade exit width b ₂, vane inlet laying angle β ₁, blade exit laying angle β ₂, subtended angle of blade φ etc., it is characterized in that Pulp pump performance parameter P, Q, H, β ₂be applicable to following relation:

In formula:

The flow of Q-design conditions, rice ³/ second;

The lift of H-design conditions, rice;

The air horsepower of P-design conditions, kilowatt;

G-gravity accleration, meter per second ²;

σ-Douglas slip coefficient;

U ₂-blade exit peripheral velocity, meter per second;

β ₂-blade exit laying angle, degree;

K _u-velocity coefficient;

ρ-fluid density, kg/m ³;

S ₂-outlet area of passage, square metre.

2. according to claim (1), impeller inlet diameter D ₀, impeller outlet diameter D ₂, vane inlet width b ₁, blade exit width b ₂, design formula is as follows:

In formula:

D ₀-impeller inlet diameter, rice;

D ₂-impeller outlet diameter, rice;

N _s-specific speed;

K ₂-impeller outlet diametral quotient;

K _b-blade exit spread factor;

B ₁-vane inlet width, rice;

B ₂-blade exit width, rice.

3. according to claim (1), vane inlet laying angle β ₁, blade exit laying angle β ₂, subtended angle of blade φ, design formula is as follows:

In formula:

β ₁-vane inlet laying angle, degree;

β ₂-blade exit laying angle, degree;

φ-subtended angle of blade, degree.

4. according to claim (1), velocity coefficient K _u, design formula is as follows:

。

5. according to claim (2), impeller outlet diametral quotient K ₂, blade exit spread factor K _b, design formula is as follows:

K ₂＝8.615n _s ^0.01898

K _b＝(0.06288n _s ²+16.16n _s+0.0002576)/(n _s+0.000163)。