CN105587706A - Design method for dual-power high-voltage reversing valve of electro-hydraulic control valve set of deep sea Christmas tree - Google Patents

Abstract

The invention provides a design method for a dual-power high-voltage reversing valve of an electro-hydraulic control valve set of a deep sea Christmas tree. The specific design method comprises the following four steps: determining a design scheme according to an actual use environment, checking and calculating a geometrical dimension, checking and calculating valve body operation force, and re-checking. The design method provided by the invention is reasonable, is high in calculating efficiency and precision, and a design value is more close to an actual use value, so that the reliability of the design work for the dual-power high-voltage reversing valve of the electro-hydraulic control valve set of the deep sea underwater Christmas tree is effectively improved, and therefore, the design method is beneficial for improving the stability and the reliability, in the actual use, of a valve body.

Description

The two electric high-pressure reversing valve methods for designing of a kind of deep-sea production tree electric hydraulic control valve group

Technical field

The present invention relates to a kind of two electric high-pressure reversing valve method for designing, is exactly the production tree electrichydraulic control of a kind of deep-seaThe two electric high-pressure reversing valve methods for designing of valve group.

Background technology

At present, in the development process of deep-sea oil gas resource, subsea production tree equipment application in deep-sea is very extensive, and deeplyIn the petrol resources exploitation of sea, there is vital effect, but find in actual use current institute on the production tree of deep-seaThe two electric high-pressure reversing valve using passes through empirical equation often, by traditional fresh water two electric high-pressure reversing valves or shallow sea water under waterThe lower pair of electric high-pressure reversing valve transformed and designed preparation, although can meet to a certain extent the need of abyssal environment operationWant, but the deep-sea production tree that design preparation all obtains in this way running technology parameter and the reality of two electric high-pressure reversing valvesBetween the environment for use of border, have larger error, thereby cause two electric high-pressure reversing valves, under abyssal environment, operation stability is not seriouslyFoot, the experience that simultaneously tradition is passed through is carrying out in two electric high-pressure reversing valve design processes, and computational accuracy wretched insufficiency is on the one hand anotherComputational efficiency is also relatively low on the one hand, simultaneously also cannot be to carrying out effectively checking and testing through the project organization calculatingCard, thus also cause great puzzlement to design work, therefore for this present situation, in the urgent need to develop a kind of highly versatile andSimple two electric high-pressure reversing valve method for designing, to meet the needs of actual use.

Summary of the invention

The object of this invention is to provide and the invention provides the two electric high-pressure reversing valves of a kind of deep-sea production tree electric hydraulic control valve groupMethod for designing.

In order to achieve the above object, the invention provides following technical scheme:

1, the two electric high-pressure reversing valve methods for designing of deep-sea production tree electric hydraulic control valve group, is characterized in that: describedProduction tree electric hydraulic control valve group two electric high-pressure reversing valve methods for designing in deep-sea comprise the steps:

The first step, determines design according to practical service environment, moves actual environment feelings under water according to the deep-sea of valve bodyCondition, and working media situation, tentatively determine effective working environment accommodation of valve body, every running technology index of establishing valve bodyAnd the basic frame for movement of valve body;

Second step, physical dimension is checked and is calculated, and the valve body technical parameter of setting according to the first step and basic frame for movement are rightThe physical dimension of valve body is checked calculating, wherein needs oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valveThe minimum aperture of valve port and main valve plug stroke are checked calculating;

The 3rd step, valve body moves stressed check and calculates, running environment and the technical parameter set according to the first step, simultaneously knotClose the concrete size of second frame for movement calculating, each stressing conditions in valve body ruuning situation calculated to check,Wherein need frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force to carry out schoolAssess calculation;

The 4th step, main valve design, according to the data that three steps obtain before, carries out latching ram diameter, return springCalculating, control piston diameter calculate, resetting piston calculates and the calculating of returning spring;

The 5th step, review is checked, according to the setup parameter scope of the first step, selected at least one group of data, and will select numberAccording to being brought in the concrete data that second step and the 3rd step calculate, then check multiple in conjunction with valve body practical operation situationAudit is calculated.

Further, the 5th described step need be carried out at least two group different parameters and checked calculating.

Reasonable design method of the present invention, computational efficiency and precision are high, and design load and actual use value more approaching, effectivelyRaising the reliability of design work of the two electric high-pressure reversing valves of deep-sea subsea production tree electric hydraulic control valve group, thereby contribute toImprove valve body stability and reliability in actual use.

Brief description of the drawings

In order to be illustrated more clearly in the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existingHave the accompanying drawing of required use in technical description to be briefly described, apparently, the accompanying drawing in the following describes is only thisSome embodiment of invention, for those of ordinary skill in the art, not paying under the prerequisite of creative work, all rightObtain other accompanying drawing according to these accompanying drawings.

Fig. 1 is the inventive method flow chart.

Detailed description of the invention

Below in conjunction with accompanying drawing of the present invention, technical scheme of the present invention is clearly and completely described, obviously, institute retouchesThe embodiment stating is only the present invention's part embodiment, instead of whole embodiment. Based on the embodiment in the present invention, thisField those of ordinary skill, not making the every other embodiment obtaining under creative work prerequisite, all belongs to the present inventionThe scope of protection.

Embodiment 1:

The two electric high-pressure reversing valve methods for designing of a kind of deep-sea production tree electric hydraulic control valve group as shown in Figure 1, recover the oil in deep-seaThe two electric high-pressure reversing valve methods for designing of tree electric hydraulic control valve group comprise the steps:

The first step, determines design according to practical service environment, moves actual environment feelings under water according to the deep-sea of valve bodyCondition, and working media situation, tentatively determine effective working environment accommodation of valve body, every running technology index of establishing valve bodyAnd the basic frame for movement of valve body:

Working environment:

Above-mentioned hydraulic valve is all arranged in the airtight container of the 3000 meters of depth of waters in ocean

1.2 temperature requirements:

1) storage temperature scope :-18 DEG C-+50 DEG C;

2) operating temperature range :-5 DEG C-+40 DEG C.

3) working media: water base fluid, as HW443.

Control principle: when oil circuit is normal, valve under charge oil pressure P=69Mpa, electromagnetism within the scope of PP=13.8--37.9MpValve can be by the opening, lock and cut out of control valve, and be 41.4-69Mpa hydraulic oil for actuator provides operating pressure, itsIn the normal state using be: P=69Mpa, PP=34.5Mpa is 41.4-69Mpa hydraulic oil for actuator provides operating pressure;

When in-line decompression, when P≤27.6Mpa, valve cuts out automatically, and actuator resets simultaneously.

Technical indicator: this valve main valve is two position, three-way electromagnetic change valve, and there is reset and auto-lock function, C mouth is also withThere is pressure tap; The opening and closing of valve are by pilot valve control, the independent fuel feeding of pilot valve, and oil return and main valve oil return be road altogether.

Second step, physical dimension is checked and is calculated, and the valve body technical parameter of setting according to the first step and basic frame for movement are rightThe physical dimension of valve body is checked calculating, wherein needs oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valveThe minimum aperture of valve port and main valve plug stroke are checked calculating:

Oil-out diameter computing formula:

Wherein: d-hydraulic fluid port diameter

Q--metered flow (l/min);

V-oil inlet and outlet diameter d goes out oil flow, and the larger speed of pressure is higher, selects 10m/s herein

So:

$d\≥\sqrt{\frac{4Q}{\mathrm{\π}v}}=\sqrt{\frac{4\×16.8\×{10}^{-3}}{\mathrm{\π}\×10\×60}}\×1000=5.97mm$

Rounding is got d=6mm;

Cue ball valve base diameter of bore and rod diameter and steel ball size computing formula:

d1≥1/2D1

Flow formula by circular passage between valve port and push rod is

$Q=\frac{\mathrm{\π}}{4}\[{D_1}^2-{d_1}^2\]V$

Above formula flow Q brings into metered flow, the oil flow V in circular passage, because of?

$Q\≤\frac{\mathrm{\π}}{4}\[{D_1}^2-{\left(\frac{D_1}{2}\right)}^2\]V$

$D_1\≥\sqrt{\frac{16Q}{3\mathrm{\π}V}}=6.89mm$

After rounding, get D1=5mm, d1=3.5mm,

Steel ball size 8mm;

Wherein: d1-rod diameter

D1-rod diameter cue ball valve base diameter of bore

Oil flow in v-circular passage

The minimum aperture computing formula of main valve valve port:

According to the flow rate calculation formula by valve port be:

$Q=C_{d}A\sqrt{2\mathrm{\Δ}p/\mathrm{\ρ}}$

In formula:

Q---by valve port fluid flow (m3/s);

A---valve port area of passage (m2);

Δ p---valve port two ends pressure reduction (Pa);

Ρ---fluid density (kg/m3);

Cd---be valve port discharge coefficient;

Valve port area of passage A computing formula is:

$A={\mathrm{\πDhX}}_1(1+X_1/2h)/\sqrt{{(D/2)}^2+{(h+X_1)}^2};$

Wherein, $h=\sqrt{R^2-\frac{D^2}{4}};$

When $X_1<<\frac{d}{2},X_1<<R$ Time, $\sqrt{{(D/2)}^2+{(h+X_1)}^2}\&ap;R,\frac{X_1}{2h}\&ap;0,$ Above formula can be changed into

$A=\mathrm{\&pi;}D\sqrt{R^2-\frac{D^2}{4}}{X}_1/R;$

So the minimum aperture formula of the opening of valve can dissolve for:

$X_1=\frac{QR}{C_d\mathrm{\&pi;}D\sqrt{\frac{2\mathrm{\&Delta;}P(R^2-\frac{D^2}{4})}{\mathrm{\&rho;}}}};$

Get Δ P=1MPa, Cd=1, so

X1＝0.38mm；

Main valve plug stroke computing formula:

Must be greater than X1 by the stroke S of spool obtains: S > X1, gets

S＝1mm；

Wherein: the stroke of S-spool;

The minimum aperture of X1-main valve valve port;

The 3rd step, valve body moves stressed check and calculates, running environment and the technical parameter set according to the first step, simultaneously knotClose the concrete size of second frame for movement calculating, each stressing conditions in valve body ruuning situation calculated to check,Wherein need frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force to carry out schoolAssess calculation:

Frictional resistance computing formula:

Due to bt=0.55d;

D0 is the end face diameter of O-ring seals. Suppose under the effect of Pb, O shape circle only comes in contact and moves with control pistonMoving, and contact width is constant.

O shape circle to the clamping force of control piston is

$N=\frac{P_b}{2}{\mathrm{\&pi;d}}_t{b}_t;$

?

F_m＝fN＝0.275πfP_bd_td₀

Wherein: F_m---frictional resistance;

F---coefficient of friction, desirable f=0.1;

Dt---diameter of piston rod;

D0---O shape circle end face diameter;

Pb---allow back pressure;

So

F_m＝0.0864P_bd_td₀

If there are 5 O-ring seals on main valve plug, for safety, when calculating according to the maximal friction of each O-ring sealsWhile being maximum back pressure, calculate, so frictional force is separately:

Self-locking control piston

The maximum back pressure of control piston is Pb1=569bar, O shape ring cross-section diameter d 01=1.8mm, piston diameter dt1

F_m1＝0.0864P_b1d_t1d₀₁＝4916d_t1＝8.58N；

Open control piston

The maximum back pressure of control piston is Pb2=569bar, O shape ring cross-section diameter d 02=1.8mm, piston diameter dt2

F_m2＝0.0864P_b2d_t2d₀₂＝4916d_t2＝7.08N；

Closing control piston push rod

The maximum back pressure of push rod is Pb3=569bar, O shape ring cross-section diameter d 03=1.8mm, piston diameter dt3

F_m3＝0.0864P_b3d_t3d₀₃＝4916d_t3＝7.08N

Closing control piston

The maximum back pressure of control piston is Pb4=379bar, O shape ring cross-section diameter d 02=1mm, piston diameter dt4

F_m4＝0.0864P_b4d_t4d₀₄＝4916d_t4＝8.58N；

Resistance of motion computing formula:

$F_V=\frac{\mathrm{\&pi;}DLV\mathrm{\&mu;}}{\mathrm{\&Delta;}r}$

Wherein: F_V---the resistance of motion;

D---control piston diameter;

The contact length of L---control piston and valve body hole;

V---valve core movement speed, average speed when available spool is 0.01s actuation time replaces; So spool $V=\frac{s}{\&lsqb;t_{dh}\&rsqb;}=\frac{0.002}{0.01}=0.2m/s;$

μ---fluid dynamic viscosity, the kinematic viscosity of HW443 is 1.9mm2/s;

The monolateral fit clearance of Δ r---spool and valve body hole, gets 0.05mm here.

So

$F_{V1}=\frac{{\mathrm{\&pi;d}}_{t1}LV\mathrm{\&mu;}}{\mathrm{\&Delta;}r}=0.14d_{t1}$

Because hydraulic oil viscosity is low, and the fit clearance of valve is relatively large, so the resistance of motion is very little, so calculatingFormula is ignored.

When hydraulic card clamping force calculates, the generation of hydraulic card clamping force is because fluid joining between hydraulic valve spool and valve bodyWhile closing mobile in gap, because spool and valve body hole have tapering and offset, the different gap place of circumferencial direction is existed and pressPower changes in distribution, and spool has been produced to a radial imbalance force, simultaneously owing to adopting O shape between the design's spool and valve bodySealing ring sealing, leakage rate is almost nil, and the design ignores hydraulic card clamping force;

Stable state fluid power computing formula:

F_W＝C_dπDδΔpsinα

Meanwhile, due to the structure of spool, in the time that spool commutates two mouthfuls all in opening, liquid stream on one side becomes dirty shapeFormula, liquid stream on one side becomes upper streamed, but the steady-state fluid force that spool is subject to is all towards a direction, all with liquid flow path direction phaseInstead, so need calculate the steady-state fluid force of two ball valves in calculating formula. And spool is no matter be in left or right position, situationBe all identical, in the time calculating, only, with calculating spool at steady-state fluid force on one side, the steady-state fluid force of spool calculates to be needed to calculateSteady-state fluid force in two kinds of situations, one is little opening, i.e. δ=1/3 δ max, when one is spool standard-sized sheet;

Obtain thus, steady-state fluid force summation is:

ΣF_W＝F_W1+F_W2＝C_dπDδΔpsinα₁+C_dπD(s-δ)Δpsinα₂

In formula:

Cd---for valve port discharge coefficient, get Cd=1;

D---valve port diameter;

The opening amount of δ---valve;

Δ p---valve port two ends pressure reduction (Pa), get 1MPa when little opening, get 0.1MPa when large opening;

α---fluid flow angle, gets α=69 ° when large opening, gets α=21 ° when little opening;

Due to the structure of spool, in the time that spool commutates two mouthfuls all in opening, liquid stream on one side becomes lower streamed, oneThe liquid stream on limit becomes upper streamed, but the steady-state fluid force that spool is subject to is all towards a direction, all contrary with liquid flow path direction, soNeed calculate the steady-state fluid force of two ball valves in calculating formula. And spool is no matter be in left position or right position, and situation is all phaseWith, in the time calculating, only with calculating spool at steady-state fluid force on one side.

The steady-state fluid force of spool calculates to be needed to calculate the steady-state fluid force in two kinds of situations, and one is little opening, i.e. δ=1/3 δ max, when one is spool standard-sized sheet.

When spool is during in little opening, δ=0.127mm, steady-state fluid force summation is now:

ΣF_W＝F_W1+F_W2＝C_dπDδΔpsinα₁+C_dπD(S-δ)Δpsinα₂

ΣF_W＝4.8N

When valve is during in standard-sized sheet, δ=S=2mm, steady-state fluid force summation is now

ΣF_W＝C_dπDδΔpsinα₁＝4.1N

Spool Calculation of the force formula:

The maximum working load of spring can calculate by following formula

F_t2＞ΣF_w+F_p1＝8N

VF_w---the stable state steady-state fluid force on spool;

F_P1---the hydraulic coupling on spool $F_{p1}=\frac{{\mathrm{\&pi;D}}^2}{4}\&lsqb;\mathrm{\&Delta;}P\&rsqb;=3.9N;$

Get Ft2=15N

So rigidity of spring:

$K_1=\frac{F_{t2}-F_{t1}}{S}=2.5N/mm$

In formula:

ΣF_m---frictional resistance summation;

F_P---the pressure that spool produces;

F_t1---spring minimum workload.

ΣF_w---steady-state fluid force when spool circle is opened;

F_t2---little spring maximum working load;

The rigidity of K1---spring;

Thus:

Open control piston

Open control piston and want to open spool, need meet the following conditions

F_{Open 1}＞ΣF_m+F_P+F_t1

F_{Open 1}---opening spool active force;

F_{Open 2}---closure state spool active force;

ΣF_m---frictional resistance summation;

F_P---the pressure that spool produces;

F_t1---little spring minimum workload;

After spool puts in place, need meet the following conditions:

F_{Open 2}＞ΣF_w+F_P+F_t2-F_From；

Closing control piston

In the time that valve cuts out, closure piston is pushed main valve plug open, now needs the power and the frictional force that overcome self-locking piston to also have stable stateHydraulic power. When valve cuts out, P, R, C communicate, and valve is in unloading condition, and the liquid in self-locking piston loses pressure, closing control pistonOnly need very little power to close, so only with calculating the power of closing control piston in the time that valve starts to cut out.

Closing control piston need meet the following conditions

Return spring elastic force computing formula:

K₁(X_T+S)＝ΣF_W1+ΣF_m1+F_P1

In formula:

ΣF_w1---the steady-state fluid force of spool in the time of 569bar open;

ΣF_m1---spool is frictional resistance sum in the time of 569bar;

F_p1---the fluid pressure that ball valve core is subject in the time of 569bar;

After spool puts in place, need meet the following conditions, because spool responsiveness is very fast, general < 0.01s, so forSpool reliable, suppose that in control piston, liquid does not also have enough time to flow out, so need to calculate the work of control piston generation hereinFirmly.

KX_t＞F_{From 1}

In the time that spool arrives little aperture position, need meet the following conditions, need equally to calculate the active force that control piston produces.

K(X_t+S-1/3δ_max)＞F_{From 1}+ΣF_{W1 is little}+ΣF_m1

ΣF_{W1 is little}---the steady-state fluid force of spool in the time of the little opening of 69bar;

The 4th step, main valve design, according to the data that three steps obtain before, carries out latching ram diameter, return springCalculating, control piston diameter calculate, resetting piston calculates and the calculating of returning spring:

Latching ram diameter

Latching ram is in the time of locked position, and left and right two pilot valves are not opened, and the power of PP pressure-acting on control piston isZero. Latching ram moves to right left ball, and push rod is pushed right ball open, makes main valve remain on open mode always, oil inlet P=69MPa, the back of the bodyPressure is 0, and spool could be locked;

The calculating of return spring

In the time that oil circuit control breaks down, valve is by platform HPU pressure release, self-closing valve core. Return spring existsIn 11.7Mpa-27.6Mpa, start to reset. When the left chamber P≤27.6MPa of latching ram, return spring overcomes the effect of locking tongue plugF₆, P mouth acts on the power F of return control piston left end₈, the compression stress of little spring and the frictional force at the capable circle of O place starts to reset. JustWhen calculating, do not consider the frictional force of the capable sealing ring of O, hydraulic card clamping force and liquid steady power.

Initial: F₁＝F₂

Getting reseat pressure is 27.6MPa

Get F₅=265N, return spring operating position F=265N, initial pressure F=300N

The calculating of returning spring

In the time that P mouth pressure is reduced to 27.8Mpa, main valve is closed automatically, returning spring reset sealed ceramic ball.

Valve port diameter D=3.5mm

The hydraulic coupling P==265N that valve port is subject to

Get returning spring operating position F=250N, initial pressure F=200N

The 5th step, review is checked, according to the setup parameter scope of the first step, selected at least one group of data, and will select numberAccording to being brought in the concrete data that second step and the 3rd step calculate, then check multiple in conjunction with valve body practical operation situationAudit is calculated.

In the present embodiment, the 5th described step need be carried out at least two group different parameters and be checked calculating.

Reasonable design method of the present invention, computational efficiency and precision are high, and design load and actual use value more approaching, effectivelyRaising the reliability of design work of the two electric high-pressure reversing valves of deep-sea subsea production tree electric hydraulic control valve group, thereby contribute toImprove valve body stability and reliability in actual use.

The above, be only the specific embodiment of the present invention, but protection scope of the present invention is not limited to this, anyBe familiar with those skilled in the art in the technical scope of the present invention's exposure, can expect easily changing or replacing, all should containCover within protection scope of the present invention. Therefore, protection scope of the present invention should described be as the criterion with the protection domain of claim.

Claims (2)

1. the two electric high-pressure reversing valve methods for designing of deep-sea production tree electric hydraulic control valve group, is characterized in that: described deep-seaThe two electric high-pressure reversing valve methods for designing of production tree electric hydraulic control valve group comprise the steps:

The first step, determines design according to practical service environment, moves actual environment situation under water according to the deep-sea of valve body, andWorking media situation, tentatively determine valve body effective working environment accommodation, establish every running technology index and the valve of valve bodyThe basic frame for movement of body;

Second step, physical dimension is checked and is calculated, and the valve body technical parameter of setting according to the first step and basic frame for movement, to valve bodyPhysical dimension check calculating, wherein need oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valve valve portMinimum aperture and main valve plug stroke are checked calculating;

The 3rd step, valve body moves stressed check and calculates, and running environment and the technical parameter set according to the first step, simultaneously in conjunction with theThe concrete size of two frame for movements that calculate, calculates check to each stressing conditions in valve body ruuning situation, whereinNeed check meter to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic forceCalculate;

The 4th step, main valve design, according to the data that three steps obtain before, carry out latching ram diameter, return spring calculating,Control piston diameter calculates, resetting piston calculates and the calculating of returning spring;

The 5th step, review is checked, according to the setup parameter scope of the first step, selected at least one group of data, and by selected data bandEnter in the concrete data that calculate to second step and the 3rd step, then check review meter in conjunction with valve body practical operation situationCalculate.

2. the two electric high-pressure reversing valve methods for designing of a kind of deep-sea according to claim 1 production tree electric hydraulic control valve group, itsBe characterised in that: the 5th described step need be carried out at least two group different parameters and be checked calculating.