CN105404749A - Modeling method for no-load running check valve - Google Patents

Modeling method for no-load running check valve Download PDF

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CN105404749A
CN105404749A CN201510873436.6A CN201510873436A CN105404749A CN 105404749 A CN105404749 A CN 105404749A CN 201510873436 A CN201510873436 A CN 201510873436A CN 105404749 A CN105404749 A CN 105404749A
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main flow
flow direction
flap
direction valve
current time
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CN105404749B (en
Inventor
刘现星
陈保同
刘志宏
王长杰
李华峰
刘翠英
范迎九
孔夏明
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719th Research Institute of CSIC
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves

Abstract

The present invention discloses a modeling method for a no-load running check valve. Based on the working principle of the no-load running check valve, starting from a dynamic equation of a valve clack assembly, a set of complete modeling, calculating and simulating processing method for the no-load running check valve is established; and the method can be used for high-accuracy dynamic characteristic analysis of a steam power apparatus water supply system comprising the no-load running check valve, and also can be used for instructing the optimal design of the no-load running check valve.

Description

A kind of modeling method of check valve
Technical field
The invention belongs to Steam Power Equipment water supply system technical field, more specifically, relate to a kind of modeling method of check valve.
Background technology
Steam Power Equipment water supply system is when underrun, required feedwater flow is less, if feed pump works under low discharge, then feed temperature may reach overheated, and the steam of generation makes feed pump generation cavitation, can cause the damage of feed pump, and produce the phenomenons such as various noise and vibrations, on the other hand, the radial force that pump shaft is strengthened, long-play can cause the fatigue breakdown of pump shaft.For avoiding the generation of above-mentioned phenomenon, usually on feed pump export pipeline, check valve is installed, both the refluence of medium can have been prevented, again can according to the delivery rate of feed pump, regulate the empty discharge capacity of feed pump, by the minimum flow of holding pump, ensure that feed pump normally works and the safe operation of water supply system.
In check valve flap assembly difference force, impulsive force, gravity, spring force and damping force before and after flap combined action under move.When the flow flowing through valve reduces, before and after flap, difference force and impulsive force reduce, and flap band ovable valve stem moves to valve seat direction, and when the delivery rate of feed pump is less than the empty discharge capacity of regulation, the flow of holding pump is empty discharge capacity; When the flow flowing through valve increases, before and after flap, difference force and impulsive force increase, and flap band ovable valve stem moves to away from valve seat direction, and when delivery rate is greater than the empty discharge capacity of regulation, empty row's mouth is closed completely, and feedwater flow is pump stream flow.
The design analysis of check valve is calculate based on stable state substantially, when bistable design operating mode is run, check valve can meet feed pump stable operation requirement, but when load variations, will there is larger change in water supply system resistance, feed pump hydrodynamic property.On the one hand, from the angle of security of operation, be necessary very much to carry out the dynamic analysis of water supply system under varying load condition, and the whether accurate precision directly determining water supply system dynamic analysis of check valve computation model; On the other hand, the simulation analysis of water supply system Dynamic High-accuracy characteristic can be verified the requirement that can the design of check valve enough meet system.But, also do not have a kind of effective method to remove the dynamics of accurate simulation check valve at present.
Summary of the invention
For above defect or the Improvement requirement of prior art, the invention provides a kind of modeling method of check valve, comprise the simulation of check valve hydraulic characteristic, flap assembly Gravity calculation, spring force modeling, check valve main flow upstream and downstream difference force calculates, main flow direction valve impulsive force calculates, and damping force calculates, and check valve Dynamic Modeling, its object is to the dynamics of accurate simulation check valve, the optimal design of check valve can also be used to guide.
For achieving the above object, according to one aspect of the present invention, provide a kind of modeling method of check valve, it is characterized in that, comprise the steps:
(1) current time T=1 is made, the main flow direction valve opening v in initialization 0 moment pm0, flap assembly movement velocity V 0with the Lift h of flap assembly 0;
(2) the main flow direction flow G of current time T is obtained mT, main flow direction inlet pressure P iT, main flow direction top hole pressure P moT, main flow direction fluid density ρ mT, empty row direction fluid density ρ kTwith the fluid density ρ in damping hole dT;
(3) the spring force F of current time T is calculated sT=k s(x 0+ h t-1), wherein, k sfor the elastic coefficient, x 0for the initial compression amount of spring during flap complete shut-down, h t-1for the Lift of the flap assembly of previous moment T-1;
(4) the flap upstream and downstream difference force F of current time T is calculated dpT=(P iT-P moT) A 0c dp, wherein, A 0for flap area, for pressure reduction correction factor, G gfor flap assembly gravity, F s0for the initial compression force of spring during flap complete shut-down, Δ P minfor the minimum differntial pressure of flap upper and lower surface when flap is opened;
(5) impulsive force suffered by the main flow direction flap calculating current time T wherein, | G mT| be G mTabsolute value, v pm (T-1)for the main flow direction valve opening of previous moment T-1, f f() is main flow direction valve opening-impulsive force function;
(6) damping force that when calculating the flap component movement of current time T, damping hole produces wherein, V t-1for the movement velocity of the flap assembly of previous moment T-1, | V t-1| be V t-1absolute value, ζ dfor the form drag coefficient of damping hole, λ is the friction factor in damping hole duct, and L is damping hole length, d dfor damping hole diameter, A gfor valve rod sectional area, A dfor damping hole sectional area;
(7) the spring force F of current time T is utilized sT, flap upstream and downstream difference force F dpT, impulsive force F suffered by main flow direction flap fTwith the damping force F that damping hole during flap component movement produces dT, calculate the acceleration of motion of the flap assembly of current time T wherein, m is the gross mass of flap assembly;
(8) according to the acceleration of motion a of the flap assembly of current time T t, calculate the movement velocity V of the flap assembly of current time T t, flap assembly Lift h t, main flow direction valve opening v pmTwith sky row direction valve aperture v pkTbe respectively:
V T＝V T-1+a TΔt，
h T＝h T-1+V TΔt，
v p m T = h T h m a x With
v p k T = 1 - h T h k ,
Wherein, Δ t is time step, h kfor the Lift of flap when empty discharge capacity has been just zero;
(9) according to the main flow direction valve opening v of current time T pmTwith sky row direction valve aperture v pkT, calculate the main flow direction valve admittance a of current time T mTwith sky row direction valve admittance a kTand export;
(10) make T=T+1, return step (2).
Preferably, in described step (5), main flow direction valve opening-impulsive force function f f() obtains in the following way:
According to main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively spring force F swith flap upstream and downstream difference force F dp, and then calculate wherein, h maxfor the maximum Lift of flap, F f=G g+ F s-F dpimpulsive force suffered by main flow direction flap, according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, f f) one group of data, be labeled as (v pm, i, f f,i), i=1,2 ..., I, I are the data count in these group data;
Make f fthe input quantity of () is x, then have:
f f ( x ) = f f , i , x = v p m , i f f , i - 1 ( v p m , i - x v p m , i - v p m , i - 1 ) &times; f f , i ( x - v p m , i - 1 v p m , i - v p m , i - 1 ) , v p m , i - 1 < x < v p m , i .
Preferably, in described step (9), the main flow direction valve admittance a of current time T mT=f m(v pmT), the sky row direction valve admittance a of current time T kT=f k(v pkT), wherein, f m() is main flow direction valve resistance fitting function, f k() is empty row's direction valve resistance fitting function.
Preferably, main flow direction valve resistance fitting function f m() obtains in the following way:
According to main flow direction flow G m, main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively with the admittance of main flow direction valve according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, a m) one group of data, be labeled as (v pm, j, a m,j), j=1,2 ..., J, J are the data count in these group data;
Make f mthe input quantity of () is y, then have:
f m ( y ) = a m , j , y = v p m , j a m , j - 1 ( v p m , j - y v p m , j - v p m , j - 1 ) &times; a m , j ( y - v p m , j - 1 v p m , j - v p m , j - 1 ) , v p m , j - 1 < y < v p m , j .
Preferably, empty row's direction valve resistance fitting function f k() obtains in the following way:
According to sky row directional flow G kp, empty row direction inlet outlet pressure differential Δ P k, empty row direction fluid density ρ kpwith the experimental data of the Lift h of flap assembly, calculate empty row's direction valve aperture respectively with the admittance of sky row direction valve according to sky row direction valve aperture v pkorder from small to large, obtains about (v pk, a k) one group of data, be labeled as (v pk, r, a k,r), r=1,2 ..., R, R are the data count in these group data;
Make f kthe input quantity of () is z, then have:
f k ( z ) = a k , r , z = v p k , r a k , r - 1 ( v p k , r - z v p k , r - v p k , r - 1 ) &times; a k , r ( z - v p k , r - 1 v p k , r - v p k , r - 1 ) , v p k , r - 1 < z < v p k , r .
In general, the above technical scheme conceived by the present invention compared with prior art, there is following beneficial effect: based on the principle of work of check valve, from the kinetics equation of flap assembly, establish the check valve modeling of complete set, Computation and Simulation disposal route, the high-precision dynamic analysis of Steam Power Equipment water supply system containing check valve can be used for, also can be used to guide the optimal design of check valve.
Accompanying drawing explanation
Fig. 1 is the modeling method process flow diagram of the check valve of the embodiment of the present invention.
Embodiment
In order to make object of the present invention, technical scheme and advantage clearly understand, below in conjunction with drawings and Examples, the present invention is further elaborated.Should be appreciated that specific embodiment described herein only in order to explain the present invention, be not intended to limit the present invention.In addition, if below in described each embodiment of the present invention involved technical characteristic do not form conflict each other and just can mutually combine.
As shown in Figure 1, the modeling method of the check valve of the embodiment of the present invention comprises the steps:
(1) current time T=1 is made, the main flow direction valve opening v in initialization 0 moment pm0, flap assembly movement velocity V 0with the Lift h of flap assembly 0;
(2) the main flow direction flow G of current time T is obtained mT, main flow direction inlet pressure P iT, main flow direction top hole pressure P moT, main flow direction fluid density ρ mT, empty row direction fluid density ρ kTwith the fluid density ρ in damping hole dT;
(3) the spring force F of current time T is calculated sT=k s(x 0+ h t-1), wherein, k sfor the elastic coefficient, x 0for the initial compression amount of spring during flap complete shut-down, h t-1for the Lift of the flap assembly of previous moment T-1;
(4) the flap upstream and downstream difference force F of current time T is calculated dpT=(P iT-P moT) A 0c dp, wherein, A 0for flap area, for pressure reduction correction factor, G gfor flap assembly gravity, F s0for the initial compression force of spring during flap complete shut-down, Δ P minfor the minimum differntial pressure of flap upper and lower surface when flap is opened;
(5) impulsive force suffered by the main flow direction flap calculating current time T wherein, | G mT| be G mTabsolute value, v pm (T-1)for the main flow direction valve opening of previous moment T-1, f f() is main flow direction valve opening-impulsive force function;
Particularly, suffered by main flow direction flap, impulsive force is:
F f = C f &CenterDot; G m | G m | G m 2 &CenterDot; A 0 2 A 2 &CenterDot; &rho; m - - - ( 1 )
Wherein, C ffor impulsive force correction factor, G mfor main flow direction flow, | G m| be G mabsolute value, A is the circulation area of fluid, ρ mfor main flow direction fluid density.
When simulation modeling, simulate the hydraulic characteristic in check valve main flow direction and empty row direction with two valves, introduce the concept of admittance in circuit.For check valve main flow direction, have: wherein, a mfor the admittance of main flow direction valve, Δ P mfor main flow direction inlet outlet pressure differential, convolution (1) obtains impulsive force and is: due to main flow direction valve admittance a mwith main flow direction valve opening v pmrelevant, impulsive force correction factor is also relevant to valve opening, by impulsive force F suffered by main flow direction flap fbe expressed as main flow direction valve opening v pmfunction, obtain: F f = G m | G m | &Delta;P m &CenterDot; f f ( v p m ) .
F f() obtains in the following way:
According to main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively (h maxmaximum Lift for flap), spring force F swith flap upstream and downstream difference force F dp, and then calculate wherein, F f=G g+ F s-F dp, according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, f f) one group of data, be labeled as (v pm, i, f f,i), i=1,2 ..., I, I are the data count in these group data;
Make f fthe input quantity of () is x, then have:
f f ( x ) = f f , i , x = v p m , i f f , i - 1 ( v p m , i - x v p m , i - v p m , i - 1 ) &times; f f , i ( x - v p m , i - 1 v p m , i - v p m , i - 1 ) , v p m , i - 1 < x < v p m , i .
Wherein, for f f, i-1's power, for f f,i's power.
(6) damping force that when calculating the flap component movement of current time T, damping hole produces wherein, V t-1for the movement velocity of the flap assembly of previous moment T-1, | V t-1| be V t-1absolute value, ζ dfor the form drag coefficient of damping hole, λ is the friction factor in damping hole duct, and L is damping hole length, d dfor damping hole diameter, A gfor valve rod sectional area, A dfor damping hole sectional area;
(7) the spring force F of current time T is utilized sT, flap upstream and downstream difference force F dpT, impulsive force F suffered by main flow direction flap fTwith the damping force F that damping hole during flap component movement produces dT, calculate the acceleration of motion of the flap assembly of current time T wherein, m is the gross mass of flap assembly;
(8) according to the acceleration of motion a of the flap assembly of current time T t, calculate the movement velocity V of the flap assembly of current time T t, flap assembly Lift h t, main flow direction valve opening v pmTwith sky row direction valve aperture v pkTbe respectively:
V T＝V T-1+a TΔt，
h T＝h T-1+V TΔt，
v p m T = h T h m a x With
v p k T = 1 - h T h k ,
Wherein, Δ t is time step, h kfor the Lift of flap when empty discharge capacity has been just zero;
When carrying out numerical evaluation, to h t, v pmTand v pkTcarry out limit value, limits is 0≤h t≤ h max, 0≤v pmT≤ 1 and 0≤v pkT≤ 1.
(9) according to the main flow direction valve opening v of current time T pmTwith sky row direction valve aperture v pkT, calculate the main flow direction valve admittance a of current time T mTwith sky row direction valve admittance a kTand export;
Particularly, a mT=f m(v pmT), a kT=f k(v pkT), wherein, f m() is main flow direction valve resistance fitting function, f k() is empty row's direction valve resistance fitting function;
F m() obtains in the following way:
According to main flow direction flow G m, main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively with the admittance of main flow direction valve according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, a m) one group of data, be labeled as (v pm, j, a m,j), j=1,2 ..., J, J are the data count in these group data;
Make f mthe input quantity of () is y, then have:
f m ( y ) = a m , j , y = v p m , j a m , j - 1 ( v p m , j - y v p m , j - v p m , j - 1 ) &times; a m , j ( y - v p m , j - 1 v p m , j - v p m , j - 1 ) , v p m , j - 1 < y < v p m , j ,
Wherein, for a m, j-1's power, for a m,j's power.
F k() obtains in the following way:
According to sky row directional flow G kp, empty row direction inlet outlet pressure differential Δ P k, empty row direction fluid density ρ kpwith the experimental data of the Lift h of flap assembly, calculate empty row's direction valve aperture respectively with the admittance of sky row direction valve according to sky row direction valve aperture v pkorder from small to large, obtains about (v pk, a k) one group of data, be labeled as (v pk, r, a k,r), r=1,2 ..., R, R are the data count in these group data;
Make f kthe input quantity of () is z, then have:
f k ( z ) = a k , r , z = v p k , r a k , r - 1 ( v p k , r - z v p k , r - v p k , r - 1 ) &times; a k , r ( z - v p k , r - 1 v p k , r - v p k , r - 1 ) , v p k , r - 1 < z < v p k , r ,
Wherein, for a k, r-1's power, for a k,r's power.
(10) make T=T+1, return step (2).
Those skilled in the art will readily understand; the foregoing is only preferred embodiment of the present invention; not in order to limit the present invention, all any amendments done within the spirit and principles in the present invention, equivalent replacement and improvement etc., all should be included within protection scope of the present invention.

Claims (5)

1. a modeling method for check valve, is characterized in that, comprises the steps:
(1) current time T=1 is made, the main flow direction valve opening v in initialization 0 moment pm0, flap assembly movement velocity V 0with the Lift h of flap assembly 0;
(2) the main flow direction flow G of current time T is obtained mT, main flow direction inlet pressure P iT, main flow direction top hole pressure P moT, main flow direction fluid density ρ mT, empty row direction fluid density ρ kTwith the fluid density ρ in damping hole dT;
(3) the spring force F of current time T is calculated sT=k s(x 0+ h t-1), wherein, k sfor the elastic coefficient, x 0for the initial compression amount of spring during flap complete shut-down, h t-1for the Lift of the flap assembly of previous moment T-1;
(4) the flap upstream and downstream difference force F of current time T is calculated dpT=(P iT-P moT) A 0c dp, wherein, A 0for flap area, for pressure reduction correction factor, G gfor flap assembly gravity, F s0for the initial compression force of spring during flap complete shut-down, Δ P minfor the minimum differntial pressure of flap upper and lower surface when flap is opened;
(5) impulsive force suffered by the main flow direction flap calculating current time T wherein, | G mT| be G mTabsolute value, v pm (T-1)for the main flow direction valve opening of previous moment T-1, f f() is main flow direction valve opening-impulsive force function;
(6) damping force that when calculating the flap component movement of current time T, damping hole produces wherein, V t-1for the movement velocity of the flap assembly of previous moment T-1, | V t-1| be V t-1absolute value, ζ dfor the form drag coefficient of damping hole, λ is the friction factor in damping hole duct, and L is damping hole length, d dfor damping hole diameter, A gfor valve rod sectional area, A dfor damping hole sectional area;
(7) the spring force F of current time T is utilized sT, flap upstream and downstream difference force F dpT, impulsive force F suffered by main flow direction flap fTwith the damping force F that damping hole during flap component movement produces dT, calculate the acceleration of motion of the flap assembly of current time T wherein, m is the gross mass of flap assembly;
(8) according to the acceleration of motion a of the flap assembly of current time T t, calculate the movement velocity V of the flap assembly of current time T t, flap assembly Lift h t, main flow direction valve opening v pmTwith sky row direction valve aperture v pkTbe respectively:
V T＝V T-1+a TΔt，
h T＝h T-1+V TΔt，
v p m T = h T h max With
v p k T = 1 - h T h k ,
Wherein, Δ t is time step, h kfor the Lift of flap when empty discharge capacity has been just zero;
(9) according to the main flow direction valve opening v of current time T pmTwith sky row direction valve aperture v pkT, calculate the main flow direction valve admittance a of current time T mTwith sky row direction valve admittance a kTand export;
(10) make T=T+1, return step (2).
2. the modeling method of check valve as claimed in claim 1, is characterized in that, in described step (5), and main flow direction valve opening-impulsive force function f f() obtains in the following way:
According to main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively spring force F swith flap upstream and downstream difference force F dp, and then calculate wherein, h maxfor the maximum Lift of flap, F f=G g+ F s-F dpimpulsive force suffered by main flow direction flap, according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, f f) one group of data, be labeled as (v pm, i, f f,i), i=1,2 ..., I, I are the data count in these group data;
Make f fthe input quantity of () is x, then have:
f f ( x ) = f f , i , x = v p m , i f f , i - 1 ( v p m , i - x v p m , i - v p m , i - 1 ) &times; f f , i ( x - v p m , i - 1 v p m , i - v p m , i - 1 ) , v p m , i - 1 < x < v p m , i .
3. the modeling method of check valve as claimed in claim 1 or 2, is characterized in that, in described step (9), and the main flow direction valve admittance a of current time T mT=f m(v pmT), the sky row direction valve admittance a of current time T kT=f k(v pkT), wherein, f m() is main flow direction valve resistance fitting function, f k() is empty row's direction valve resistance fitting function.
4. the modeling method of check valve as claimed in claim 3, is characterized in that, main flow direction valve resistance fitting function f m() obtains in the following way:
According to main flow direction flow G m, main flow direction inlet outlet pressure differential Δ P m, main flow direction fluid density ρ mexperimental data with the Lift h of flap assembly, calculates main flow direction valve opening respectively with the admittance of main flow direction valve according to main flow direction valve opening v pmorder from small to large, obtains about (v pm, a m) one group of data, be labeled as (v pm, j, a m,j), j=1,2 ..., J, J are the data count in these group data;
Make f mthe input quantity of () is y, then have:
f m ( y ) = a m , j , y = v p m , j a m , j - 1 ( v p m , j - y v p m , j - v p m , j - 1 ) &times; a m , j ( y - v p m , j - 1 v p m , j - v p m , j - 1 ) , v p m , j - 1 < y < v p m , j .
5. the modeling method of check valve as claimed in claim 3, is characterized in that, empty row's direction valve resistance fitting function f k() obtains in the following way:
According to sky row directional flow G kp, empty row direction inlet outlet pressure differential Δ P k, empty row direction fluid density ρ kpwith the experimental data of the Lift h of flap assembly, calculate empty row's direction valve aperture respectively with the admittance of sky row direction valve according to sky row direction valve aperture v pkorder from small to large, obtains about (v pk, a k) one group of data, be labeled as (v pk, r, a k,r), r=1,2 ..., R, R are the data count in these group data;
Make f kthe input quantity of () is z, then have:
f k ( z ) = a k , r , z = v p k , r a k , r - 1 ( v p k , r - z v p k , r - v p k , r - 1 ) &times; a k , r ( z - v p k , r - 1 v p k , r - v p k , r - 1 ) , v p k , r - 1 < z < v p k , r .
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109306979A (en) * 2018-10-29 2019-02-05 北京航天发射技术研究所 A kind of machine liquid throttling control valve design method based on mechanism displacement speed planning
CN109306979B (en) * 2018-10-29 2020-05-08 北京航天发射技术研究所 Mechanical hydraulic throttling control valve design method based on mechanism displacement speed planning
CN113051687A (en) * 2021-04-01 2021-06-29 珠海格力智能装备有限公司 Method and device for processing flow field of check valve

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