CN105221487A - The radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field - Google Patents

Abstract

The present invention relates to a kind of radial stator Hydraulic Design Method, particularly the radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field.The present invention determines stator base circle diameter (BCD) D by formula ₃, stator throat axial plane width b ₃, vane inlet angle α ₃, stator number of blade z, stator throat plane width a ₃, stator outlet diameter D ₄, stator blade inlet thickness δ, stator diffuser length L, vane inlet axial width a ₃, stator angle of flare deng the important design parameter of stator.The object of the invention is to, for centrifugal tundish stator provides a kind of science, system, more complete design method, widen the high efficiency range of water injection pump, increase the service life.

Description

The radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field

Technical field

The present invention relates to a kind of radial stator Hydraulic Design Method, particularly the radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field.

Background technique

Water-flooding pump for oil field is used for the water injection work in oil field development, and the effect of water filling is effectively to supplement stratum energy, makes oil recovery efficiency higher, ensures ability and the stability of oil field produce oil.Flood pattern is of crucial importance and power consumption is very huge to oilfield exploitation, can account for more than three one-tenth of oil recovery factory's electricity consumption.So the performance requirement for flood pattern critical component water injection pump is very high, improves existing water injection pump efficiency, reliability and stability are significant for reduction cost of production.

In the middle and later periods of oilfield exploitation, the water injection rate that oil-producing region needs is different for early stage from exploitation, and need use pump valve adjust flux, at this moment the running operating point of pump can depart from the efficient district of pump, will consume more electric energy.In addition, the water quality of oilfield injection water is poor, has corrosivity, also there is scale formation, significantly affects the working life of water injection pump, and this is also the place that the design of current water injection pump must be considered.

In centrifugal water-flooding pump for oil field, stator is most important flow passage components except impeller, its role is to the kinetic transformation of fluid to become pressure energy, eliminates flowing circular rector simultaneously.The stator properties directly affecting water injection pump whether reasonable in design.To widen the efficient region of water injection pump, increasing the service life, certainly will will be optimized existing stator Hydraulic Design Method.The present inventor proposes the radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field at this, not only perfect improvement is carried out to existing parameter designing formula, and incorporate more in the middle of production practices effective empirical correlation, to expand water injection pump efficient district, to increase the service life have positive role.

Goal of the invention

The design method of current centrifugal water-flooding pump for oil field is perfect still not, and indivedual experience class formula has also used not to be revised along with continuous production practices grow with each passing hour for many years.The object of the invention is to, for centrifugal tundish stator provides a kind of science, system, more complete design method, widen the high efficiency range of water injection pump, increase the service life.

Summary of the invention

The present invention has taken into full account the performance requirement of water-flooding pump for oil field and the particularity of working environment, improve the design method of relevant parameter, especially innovative design has been done to the defining method of the number of blade, to ensure to use the stator of the method design to have more excellent performance in production reality.

The technological scheme that object adopts is:

(1). with stator diffuser discharge area F ₄for starting point designs, progressively each relevant parameter is determined

In formula

F ₄---stator diffuser discharge area, m ²;

D ₃---stator base circle diameter (BCD), m;

---stator angle of flare, radian;

F ₃---stator throat opening area, m ².

(2). stator throat plane width a ₃

a ₃＝(-0.001437z ³+0.04615z ²-0.4314z+1.944)b ₃(4)

In formula

A ₃---stator throat plane width, m;

Z---the stator number of blade, individual;

B ₃---stator throat axial plane width, m.

(3). stator number of blade z

$Z=\frac{Q}{b_3^{2}11.58n_s^{-1.013}+0.2823\sqrt{2gH}}---\left(5\right)$

In formula

Q---flow, m ³/ h;

N _s---specific speed;

G---gravity accleration, m/s ²;

H---lift, m.

(4). vane inlet width b ₃

$\left\{\begin{array}{cc}{b}_3=b_2+3.204\×{10}^{-7}{R}_s^3-8.489\×{10}^{-5}{n}_s^2+0.007579n_s+1.854,n_s\∈(1,100)& \left(6\right)\\ b_3=b_2+3.487-1.535cos\left(0.01941n_s\right)+0.3561sin\left(0.01941n_s\right),n_s\∈(100,200)& \left(7\right)\\ b_3=b_2+\frac{-0.2412n_s^2+76.01n_s}{n_s+1.578},n_s\∈(200,300)& \left(8\right)\end{array}\right.$

In formula

B ₂---impeller blade exit width, m.

(5). stator base circle diameter (BCD) D ₃

$\left\{\begin{array}{cc}{D}_3=D_2+4.224e^{\frac{-{(n_s-224.8)}^2}{{47.62}^2}}+6.667e^{\frac{-{(n_s-157.4)}^2}{{129.3}^2}},n_s\∈(1,150)& \left(9\right)\\ D_3=D_2+6.371-3.447\cos \left(0.02882n_s\right)-1.427sin\left(0.02882n_s\right),n_s\∈(150,250)& \left(10\right)\\ D_3=D_2+0.001476n_s^2+0.02713n_s+1.528,n_s\∈(250,300)& \left(11\right)\end{array}\right.$

In formula

D ₂---impeller outlet diameter, m.

(6). stator angle of flare usually the some values between 5 ° to 9 ° are got.

(7). stator diffuser length L

$L=(-1.287+0.04596{\mathrm{\α}}_3+1.034-0.005772{\mathrm{\α}}_3{D}_3-0.05D_3^2)a_3---\left(12\right)$

In formula

L---stator diffuser length, m;

α ₃---vane inlet angle, radian.

(8). vane inlet angle α ₃

${\mathrm{tan\α}}_3=\frac{0.007775{\mathrm{\α}}_2^{\′3}-0.06727{\mathrm{\α}}_2^{\′2}-83.3{\mathrm{\α}}_2^{\′}+4665}{{\mathrm{\α}}_2^{\′2}-118.8{\mathrm{\α}}_2^{\′}+4486}{\mathrm{tan\α}}_2^{\′}---\left(13\right)$

In formula

α ₂'---the absolute flow angle of impeller outlet, radian.

(9). stator outlet diameter D ₄

In formula

D ₄---stator outlet diameter, m

δ---stator blade inlet thickness, mm.

According to above-mentioned steps, can obtain a kind of science, system, the design method of accurate stator major parameter.The main geometric parameters of stator can be determined by above-mentioned calculating, comprise stator base circle diameter (BCD), stator throat axial plane width, vane inlet angle, the stator number of blade, stator throat plane width, stator outlet diameter, stator blade inlet thickness, stator diffuser length, vane inlet axial width, stator angle of flare etc.The centrifugal water-flooding pump for oil field stator designed by said method can reduce the energy ezpenditure amplification regulating pump valve to cause, and also effectively can extend the time limit of water injection pump.

Accompanying drawing explanation

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

Fig. 1 is the planimetric map of water injection pump stator.

Fig. 2 is the axial plane figure of water injection pump stator.

In Fig. 1: 1.a ₃, 2. α ₃, 4.D ₄, 5.D ₃, A-B camber line is stator diffuser length L, 7. stator blade inlet thickness δ.

In Fig. 2: 6.b ₃.

Embodiment

The present invention determines stator base circle diameter (BCD) D by following formula ₃, stator throat axial plane width b ₃, vane inlet angle α ₃, stator number of blade z, stator throat plane width a ₃, stator outlet diameter D ₄, stator blade inlet thickness δ, stator diffuser length L, vane inlet axial width a ₃, stator angle of flare deng the important design parameter of stator.

This embodiment is at given design conditions flow Q scope, design conditions lift, design specific speed n _sdeng prerequisite under, calculate stator parameter:

a ₃＝(-0.001437z ³+0.04615z ²-0.4314z+1.944)b ₃(4)

$Z=\frac{Q}{b_3^{2}11.58n_s^{-1.013}+0.2823\sqrt{2gH}}---\left(5\right)$

$\left\{\begin{array}{cc}{b}_3=b_2+3.204\×{10}^{-7}{n}_s^3-8.489\×{10}^{-5}{n}_s^2+0.007579n_s+1.854,n_s\∈(1,100)& \left(6\right)\\ b_3=b_2+3.487-1.535cos\left(0.01941n_s\right)+0.3561\sin \left(0.01941n_s\right),n_s\∈(100,200)& \left(7\right)\\ b_3=b_2+\frac{-0.2412n_s^2+76.01n_s}{n_s+1.578},n_s\∈(200,300)& \left(8\right)\end{array}\right.$

$\left\{\begin{array}{cc}{D}_3=D_2+4.224e^{\frac{-{(n_s-224.8)}^2}{{47.62}^2}}+6.667e^{\frac{-{(n_s-157.4)}^2}{{129.3}^2}},n_s\∈(1,150)& \left(9\right)\\ D_3=D_2+6.371-3.447cos\left(0.02882n_s\right)-1.427sin\left(0.02882n_s\right),R_s\∈(150,250)& \left(10\right)\\ D_3=D_2+0.001476n_s^2+0.02713n_s+1.528,n_s\∈(250,300)& \left(11\right)\end{array}\right.$

Stator angle of flare usually the some values between 5 ° to 9 ° are got

$L=(-1.287+0.04596{\mathrm{\α}}_3+1.034-0.005772{\mathrm{\α}}_3{D}_3-0.05D_3^2)a_3---\left(12\right)$

${\mathrm{tan\α}}_3=\frac{0.007775{\mathrm{\α}}_2^{\′3}-0.06727{\mathrm{\α}}_2^{\′2}-83.3{\mathrm{\α}}_2^{\′}+4665}{a_2^{\′2}-118.8{\mathrm{\α}}_2^{\′}+4486}{\mathrm{tan\α}}_2^{\′}---\left(13\right)$

The present invention is generally applicable to the stator design of centrifugal water-flooding pump for oil field, gives and sufficient consideration and analysis the working state of water-flooding pump for oil field, proposes the radial stator Hydraulic Design Method of a kind of water-flooding pump for oil field originally.

The present invention greatly improves design efficiency and the design level of the radial stator of centrifugal water-flooding pump for oil field, reduces the cost and risk of design.

The invention is not restricted to above-described embodiment, also comprise other embodiment in concept of the present invention and variation.

Claims (9)

1. the radial stator Hydraulic Design Method of water-flooding pump for oil field, provides the main geometric parameters that stator designs, comprises stator base circle diameter (BCD) D ₃, stator throat axial plane width b ₃, vane inlet angle α ₃, stator number of blade z, stator throat plane width a ₃, stator outlet diameter D ₄, stator diffuser length L, vane inlet axial width a ₃, stator angle of flare deng, it is characterized in that stator geometric parameter and pump operating point for design performance parameter Q, H, n _sbe applicable to following relation:

In formula

F ₄---stator diffuser discharge area, m ²;

D ₃---stator base circle diameter (BCD), m;

---stator angle of flare, radian;

F ₃---stator throat opening area, m ².

2. stator throat plane width a ₃design formula is as follows:

a ₃＝(-0.001437z ³+0.04615z ²-0.4314z+1.944)b ₃(4)

In formula

A ₃---stator throat plane width, m;

Z---the stator number of blade, individual;

B ₃---stator throat axial plane width, m.

3. as claimed in claim 2, stator number of blade z design formula is as follows

$z=\frac{Q}{b_3^{2}11.58n_s^{-1.013}+0.2823\sqrt{2gH}}---\left(5\right)$

In formula

Q---flow, m ³/ h;

N _s---specific speed;

G---gravity accleration, m/s ²;

H---lift, m.

4. vane inlet width b ₃design formula is as follows:

$\left\{\begin{array}{cc}{b}_3=b_2+3.204\×{10}^{-7}{n}_s^3-8.489\×{10}^{-5}{n}_s^2+0.007579n_s+1.854,n_s\∈(1,100)& \left(6\right)\\ b_3=b_2+3.487-1.535cos\left(0.01941n_s\right)+0.3561sin\left(0.01941n_s\right),n_s\∈(100,200)& \left(7\right)\\ b_3=b_2+\frac{-0.2412n_s^2+76.01n_s}{n_s+1.578},n_s\∈(200,300)& \left(8\right)\end{array}\right.$

In formula

B ₂---impeller blade exit width, m.

5. as claimed in claim 1, stator base circle diameter (BCD) D ₃design formula is as follows:

$\left\{\begin{array}{cc}{D}_3=D_2+4.224e^{\frac{-{(n_s-224.8)}^2}{{47.62}^2}}+6.667e^{\frac{-{(n_s-157.4)}^2}{{129.3}^2}},n_s\∈(1,150)& \left(9\right)\\ D_3=D_2+6.371-3.447\cos \left(0.02882n_s\right)-1.427sin\left(0.02882n_s\right),n_s\∈(150,250)& \left(10\right)\\ D_3=D_2+0.001476n_s^2+0.02713n_s+1.528,n_s\∈(250,300)& \left(11\right)\end{array}\right.$

In formula

D ₂---impeller outlet diameter, m.

6. as claimed in claim 1, stator angle of flare usually the some values between 5 ° to 9 ° are got.

7. stator diffuser length L design formula is as follows:

$L=(-1.287+0.04596{\mathrm{\α}}_3+1.034-0.005772{\mathrm{\α}}_3{D}_3-0.05D_3^2)a_3---\left(12\right)$

In formula

L---stator diffuser length, m;

α ₃---vane inlet angle, radian.

8. as claimed in claim 7, vane inlet angle α ₃design formula is as follows:

${\mathrm{tan\α}}_3=\frac{0.007775{\mathrm{\α}}_2^{\′3}-0.06727{\mathrm{\α}}_2^{\′2}-83.3{\mathrm{\α}}_2^{\′}+4665}{{\mathrm{\α}}_2^{\′2}-118.8{\mathrm{\α}}_2^{\′}+4486}{\mathrm{tan\α}}_2^{\′}---\left(13\right)$

In formula

α ₂'---the absolute flow angle of impeller outlet, radian.

9. stator outlet diameter D ₄as follows with stator blade inlet thickness δ design formula:

In formula

D ₄---stator outlet diameter, m;

δ-stator blade inlet thickness, mm.