CN105179307B - A kind of wear-resistant centrifugal type slurry pump impeller Hydraulic Design Method - Google Patents

Abstract

The present invention relates to a kind of slurry pump impeller Hydraulic Design Method, more particularly to a kind of wear-resistant centrifugal type slurry pump impeller Hydraulic Design Method.The present invention determines impeller inlet diameter D by formula₀, impeller outlet diameter D₂, vane inlet width b₁, blade exit width b₂, vane inlet laying angle β₁, blade exit laying angle β₂, the impeller such as subtended angle of blade φ important design parameter.Through practice test, present invention greatly enhances the wear resistence and design level of Pulp pump, the Pulp pump according to present invention design production has good performance and economic benefit higher.

Description

A kind of wear-resistant centrifugal type slurry pump impeller Hydraulic Design Method

Technical field

The present invention relates to a kind of screenings impeller of pump Hydraulic Design Method, more particularly to a kind of wear-resistant centrifugal type slurry pump leaf Wheel Hydraulic Design Method.

Background technology

The pump containing suspended solids suitable for conveying liquid (water) is typically referred to as Pulp pump.It is currently ore dressing, choosing One of indispensable equipment in each technological process in coal works.Pulp pump is by the effect by centrifugal force (rotation of the impeller of pump) Make a kind of increased machinery of solid, liquid blending agent energy.Be widely used in mine, chemical industry, coal, food, metallurgy, building materials and The industry fields such as oil.Pulp pump can be divided into single-stage/multistage, single suction/double suction, cantilever, horizontal/vertical and pump by distinct principle / vertical the pattern such as combine is opened in shell level.With the fast development of industry-by-industry.Under the prior art, the water of slurry pump impeller Hydraulic design method depends on the experience of designer, and such method for designing has many relations with the experience of designer, not really Qualitative factor is a lot, and design cost is higher, it is impossible to meet requirement of the current market to Pulp pump.Therefore, it is necessary to Pulp pump The Hydraulic Design Method of impeller is done further perfect.

Mainly have following through retrieving slurry pump impeller Hydraulic Design Method：" the one of Patent No. ZL03213328.6 Kind of Assembled slag pulp pump impeller " utility model patent, in that patent designer employ fabricated structure so that blade, leaf The easily fabricated processing of structure of piece main body and apron plate；" slurry pump impeller " of Patent No. ZL201020293027.1 is practical new Type patent, in that patent designer blade wheel structure is improved, reduce the gap of impeller oversheath and primary blades, make Pressure increase between both parts, reduces the vibration of Pulp pump.

Goal of the invention

Existing centrifugal type slurry pump impeller Hydraulic Design Method is simultaneously incomplete, even the slurry pump impeller of individual species Hydraulic Design Method also has many places to have pending improvement.It is an object of the present invention to provide a kind of science, it is efficient from Core type slurry pump impeller Hydraulic Design Method, improves the flow regime inside Pulp pump, improves Pulp pump abrasion resistance, and extension makes Use the life-span.

The content of the invention

The present invention has taken into full account the worked environment of Pulp pump, it is contemplated that influence of the granular size to pump operation situation, The method for designing of slurry pump impeller design parameter is improved, to ensure the stabilization, functions reliably and efficiently of slurry pump work.

The technical scheme that purpose is used is：

(1) Pulp pump performance parameter P, Q, H, β₂It is adapted to following relation:

In formula：

The flow of Q-design conditions, rice³/ the second；

The lift of H-design conditions, rice；

The shaft power of P-design conditions, kilowatt；

G-acceleration of gravity, meter per second²；

σ-Douglas slip coefficient；

u₂- blade exit peripheral speed, meter per second；

β₂- blade exit laying angle, degree；

K_u- velocity coeffficient；

ρ-fluid density, kg/m³；

S₂- outlet area of passage, square metre；

(2) velocity coeffficient K_u, design formula is as follows：

In formula：

n_s- specific revolution；

(3) impeller inlet diameter D₀, design formula is as follows：

In formula：

D₀- impeller inlet diameter, rice；

n_s- specific revolution；

The flow of Q-design conditions, rice³/ the second；

(4) impeller outlet diameter D₂, design formula is as follows：

In formula：

D₂- impeller outlet diameter, rice；

n_s- specific revolution；

The flow of Q-design conditions, rice³/ the second；

K₂- impeller outlet diameter quotient；

The lift of H-design conditions, rice；

(5) impeller outlet diameter quotient K₂, design formula is as follows：

K₂=8.615n_s ^0.01898

In formula：

K₂- impeller outlet diameter quotient；

n_s- specific revolution；

(6) vane inlet width b₁, design formula is as follows：

In formula：

b₁- vane inlet width, rice；

n_s- specific revolution；

D₂- impeller outlet diameter, rice；

(7) blade exit width b₂, design formula is as follows：

In formula：

b₂- blade exit width, rice；

n_s- specific revolution；

K_b- impeller outlet diameter quotient；

The flow of Q-design conditions, rice³/ the second；

(8) impeller outlet diameter 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 diameter quotient；

n_s- specific revolution；

(9) vane inlet laying angle β₁, design formula is as follows：

In formula：

β₁- vane inlet laying angle, degree；

n_s- specific revolution；

(10) blade exit laying angle β₂, design formula is as follows：

In formula：

β₂- blade exit laying angle, degree；

n_s- specific revolution；

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

φ=- 0.0003546n_s ²+0.3478n_s+77.35

In formula：

φ-subtended angle of blade, degree；

n_s- specific revolution；

According to above step, a kind of science, system, accurate impeller major parameter method for designing can be obtained. The main geometric parameters of impeller, including impeller inlet diameter D can be determined by above-mentioned computational methods₀, impeller outlet diameter D₂、 Vane inlet width b₁, blade exit width b₂, vane inlet laying angle β₁, blade exit laying angle β₂, subtended angle of blade φ etc.. The slurry pump impeller designed by above step more conforms to the flow behavior of its pumped (conveying) medium, enhances the wear-resistant of Pulp pump Performance, it is ensured that the fluency of flow of fluid in pump so that the performance of Pulp pump becomes more stable reliability, and wear resistance is more Height, effective run time is longer.

Brief description of the drawings

The present invention is further described with reference to the accompanying drawings and detailed description.

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

Fig. 2 is the plan of slurry pump impeller.

In Fig. 1：D₀- impeller inlet diameter；D₂- impeller outlet diameter；b₁- vane inlet width；b₂- blade exit Width；D_iThe distance of-blade passage center line distance axis line；R_DS- front shroud of impeller arc radius；R_TS- back shroud of impeller circular arc Radius.

In Fig. 2：β₁- vane inlet laying angle；β₂- blade exit laying angle；φ-subtended angle of blade.

Specific embodiment

The present invention determines to include 1 impeller inlet diameter D by following formula₀, 2 impeller outlet diameter D₂, 3 blades Entrance width b₁, 4 blade exit width b₂, 5 vane inlet laying angle β₁, 6 blade exit laying angle β₂, the slag such as 7 subtended angle of blade φ The important design parameter of stock pump impeller.

The embodiment is the meter on the premise of given design conditions flow Q, design conditions lift H, design conditions rotating speed n Calculate impeller parameters：

K₂=8.615n_s ^0.01898

K_b=(0.06288n_s ²+16.16n_s+0.0002576)/(n_s+0.000163)

φ=- 0.0003546n_s ²+0.3478n_s+77.35

Present invention is generally applicable to the Impeller Design of low-specific-speed centrifugal type slurry pump high, above design formula is comprehensively examined The flow behavior in Pulp pump is considered.

Checked through production practices, present invention greatly enhances the design efficiency and design level of Pulp pump, reduce and set Meter cost and risk, the Pulp pump according to present invention design production has good performance and economic benefit higher.

Above for patent of the present invention with reference to illustrating that embodiment is made, but the present invention is not limited to above-mentioned implementation Example, also comprising the other embodiment or variation in the range of present inventive concept.

Claims (5)

1. a kind of wear-resistant centrifugal type slurry pump impeller Hydraulic Design Method, there is provided the main geometric parameters of Impeller Design, including Impeller inlet diameter D₀, impeller outlet diameter D₂, vane inlet width b₁, blade exit width b₂, vane inlet laying angle β₁, leaf Piece outlet laying angle β₂, subtended angle of blade φ, it is characterised in that Pulp pump performance parameter P, Q, H, β₂It is adapted 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, rice³/ the second；

The lift of H-design conditions, rice；

The shaft power of P-design conditions, kilowatt；

G-acceleration of gravity, meter per second²；

σ-Douglas slip coefficient；

u₂- blade exit peripheral speed, meter per second；

β₂- blade exit laying angle, degree；

K_u- velocity coeffficient；

ρ-fluid density, kg/m³；

S₂- outlet area of passage, square metre.

2. wear-resistant centrifugal type slurry pump Hydraulic Design Method according to claim 1, impeller inlet diameter D₀, impeller goes out Mouth diameter D₂, vane inlet width b₁, blade exit width b₂, design formula is as follows：

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

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

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

In formula：

D₀- impeller inlet diameter, rice；

D₂- impeller outlet diameter, rice；

n_s- specific revolution；

K₂- impeller outlet diameter quotient；

K_b- blade exit spread factor；

b₁- vane inlet width, rice；

b₂- blade exit width, rice.

3. wear-resistant centrifugal type slurry pump Hydraulic Design Method according to claim 1, vane inlet laying angle β₁, blade Outlet laying angle β₂, subtended angle of blade φ, design formula is as follows：

φ=- 0.0003546n_s ²+0.3478n_s+77.35

In formula：

n_s- specific revolution；

β₁- vane inlet laying angle, degree；

β₂- blade exit laying angle, degree；

φ-subtended angle of blade, degree.

4. wear-resistant centrifugal type slurry pump Hydraulic Design Method according to claim 1, velocity coeffficient K_u, design formula is such as Under：

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

In formula：

n_s- specific revolution.

5. wear-resistant centrifugal type slurry pump Hydraulic Design Method according to claim 2, impeller outlet diameter quotient K₂, leaf Piece exit width COEFFICIENT K_b, design formula is as follows：

K₂=8.615n_s ^0.01898

K_b=(0.06288n_s ²+16.16n_s+0.0002576)/(n_s+0.000163)。