CN105625982A - Method for designing SCM (Single Chip Microcomputer) single-charged low-pressure reversing valve for deep sea underwater Christmas tree - Google Patents

Abstract

The invention provides a method for designing an SCM (Single Chip Microcomputer) single-charged low-pressure reversing valve for a deep sea underwater Christmas tree. Particularly, the design method comprises four steps of: according to an actual use environment, determining a design scheme; checking and calculating geometric dimensioning; checking and calculating an operation stress of a valve body; reexamining and checking. The design method provided by the invention is reasonable, and has high calculation efficiency and accuracy; a design value is closer to an actual use value; reliability of the design work of the single-charged low-pressure reversing valve of an electrohydraulic control valve bank for the deep sea underwater Christmas tree is effectively improved so as to facilitate improving stability and reliability of the valve body in the actual use.

Description

A kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method

Technical field

The present invention relates to a kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method, be exactly a kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method.

Background technology

At present in the development process of deep-sea oil gas resource, deep-sea subsea production tree equipment application is very extensive, and in deep-sea oil gas development of resources, have vital effect, but find in actual use, the current single electricity low pressure reversal valve used on the production tree of deep-sea is often over empirical equation, the electricity low pressure reversal valve that traditional fresh water single electricity low pressure reversal valve or shallow sea water under water placed an order carries out transforming and designs preparation, although the needs of abyssal environment operation can be met to a certain extent, but there is bigger error with between single electricity low pressure reversal valve running technology parameter and practical service environment in the deep-sea production tree that design preparation all obtains in this way, thus causing single electricity low pressure reversal valve operation stability wretched insufficiency under abyssal environment, the experience that tradition is passed through simultaneously is in entering single electricity low pressure reversing valve designs process, computational accuracy wretched insufficiency on the one hand, on the other hand computational efficiency also relatively low under, also cannot effectively check checking to through calculated design structure simultaneously, thus also causing great puzzlement to design work, hence for this present situation, in the urgent need to developing a kind of highly versatile and simple single electricity low pressure reversing valve designs method, to meet actually used needs.

Summary of the invention

It is an object of the invention to provide the present invention and a kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method is provided.

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

A kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method, comprises the steps:

The first step, design is determined according to practical service environment, deep-sea according to valve body runs actual environment situation and working media situation under water, the basic frame for movement of the effective working environment subject range primarily determining that valve body, the every running technology index setting valve body and valve body;

Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic frame for movement, the physical dimension of valve body is carried out calculation and check, wherein needs oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, the minimum aperture of main valve valve port and main valve plug stroke are carried out calculation and check;

3rd step, valve body runs stress calculation and check, the running environment set according to the first step and technical parameter, concrete size in combination with second calculated frame for movement, it is calculated stressing conditions each in valve body ruuning situation checking, wherein needs frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force are carried out calculation and check;

4th step, main valve designs, according to first three obtained data of step, be controlled piston diameter and calculate and the calculating of returning spring;

5th step, review is checked, the setup parameter scope according to the first step, selected least one set data, and is brought into by selected data in second step and the calculated concrete data of the 3rd step, carries out checking review then in conjunction with valve body practical operation situation and calculates.

Further, the 5th described step need to carry out at least two group different parameters and carry out calculation and check.

Reasonable design method of the present invention, computational efficiency and precision are high, and design load and actually used value closer to, effectively raise the reliability of the design work of deep-sea subsea production tree electric hydraulic control valve group list electricity low pressure reversal valve, thus being favorably improved valve body stability in actual use and reliability.

Accompanying drawing explanation

In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, the accompanying drawing used required in embodiment or description of the prior art will be briefly described below, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skill in the art, under the premise not paying creative work, it is also possible to obtain other accompanying drawing according to these accompanying drawings.

Fig. 1 is the inventive method flow chart.

Detailed description of the invention

Technical scheme is clearly and completely described by the accompanying drawing below in conjunction with the present invention, it is clear that described embodiment is only a part of embodiment of the present invention, rather than whole embodiments. Based on the embodiment in the present invention, the every other embodiment that those of ordinary skill in the art obtain under not making creative work premise, broadly fall into the scope of protection of the invention.

Embodiment 1:

A kind of deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method as shown in Figure 1, deep-sea production tree electric hydraulic control valve group list electricity low pressure reversing valve designs method comprises the steps:

The first step, design is determined according to practical service environment, deep-sea according to valve body runs actual environment situation and working media situation under water, the basic frame for movement of the effective working environment subject range primarily determining that valve body, the every running technology index setting valve body and valve body:

Working environment:

Above-mentioned hydraulic valve is all arranged in the sealing 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, such as HW443.

Control principle: when oil circuit is normal, valve is at below charge oil pressure P=56.9Mpa, within the scope of PP=13.8--37.9Mp, electromagnetic valve can pass through to control opening, lock and cutting out of valve, and provide operating pressure to be 11.3 56.9Mpa hydraulic oil for executor, the state wherein often used is: P=56.9Mpa, PP=34.5Mpa provide operating pressure to be 11.3 56.9Mpa hydraulic oil for executor;

Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic frame for movement, the physical dimension of valve body is carried out calculation and check, wherein needs oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, the minimum aperture of main valve valve port and main valve plug stroke are carried out calculation and check:

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 more big speed of pressure is more high, herein select 10m/s so:

$d\≥\sqrt{\frac{4Q}{\mathrm{\π}v}}=\sqrt{\frac{4\×16.8\×{\mathrm{10}}^{\mathrm{-3}}}{\mathrm{\π}\×\mathrm{10}\×\mathrm{60}}}\×\mathrm{1000=5}\mathrm{.97}mm$

Rounding takes d=6mm;

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

d1��1/2D1

By the flow formula of circular passage between valve port and push rod it 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 ofThen

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

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

D1=5mm, d1=3.5mm is taken after rounding,

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 by the flow rate calculation formula of valve port it is:

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

In formula:

Q passes through valve port fluid flow (m3/s);

A valve port area of passage (m2);

�� p valve port two ends pressure reduction (Pa);

�� fluid density (kg/m3);

Cd is valve port flow 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 $x_1<<\frac{d}{2},$ X₁During < < R, $\sqrt{{(D/2)}^2+{(h+X_1)}^2}\&ap;R,\frac{X_1}{2h}\&ap;0,$

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:

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

Take �� P=1MPa, Cd=1, so

X1=0.38mm;

Main valve plug climb displacement formula:

Be have to be larger than X1 by the stroke S of spool to obtain: S > X1, take

S=1mm;

Wherein: the stroke of S spool;

The minimum aperture of X1 main valve valve port;

3rd step, valve body runs stress calculation and check, the running environment set according to the first step and technical parameter, concrete size in combination with second calculated frame for movement, it is calculated stressing conditions each in valve body ruuning situation checking, wherein needs frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force are carried out calculation and check:

Frictional resistance computing formula:

Due to bt=0.55d;

D0 is the end face diameter of O-ring seals. Assuming that under the effect of Pb, O only comes in contact movement with controlling piston, and contact width is constant.

The clamping force controlling piston is by O

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

Then

F_m=fN=0.275 �� fP_bd_td₀

Wherein: F_mFrictional resistance;

F coefficient of friction, desirable f=0.1;

Dt diameter of piston rod;

D0 O end face diameter;

Pb allows back pressure;

So

F_m=0.0864P_bd_td₀

If main valve plug has 5 O-ring seals, for safety, calculate time during calculating according to the maximal friction of each O-ring seals and maximum back pressure, so respective frictional force is:

Open and control piston

Controlling the maximum back pressure of piston is Pb2=569bar, O diameter of section d02=1.8mm, piston diameter dt2

F_m2=0.0864P_b2d_t2d₀₂=4916d_t2=7.08N;

Resistance of motion computing formula:

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

Wherein: F_vThe resistance of motion;

D controls piston diameter;

L controls the contact length of piston and valve body hole;

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

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

�� r spool and the monolateral fit clearance of valve body hole, take 0.05mm here.

So

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

Owing to hydraulic oil viscosity is low, and the fit clearance of valve is relatively large, so the resistance of motion is very little, so being ignored in calculating formula.

When hydraulic card clamping force calculates, when the generation of hydraulic card clamping force is because the flowing in fluid fit clearance between hydraulic valve spool and valve body, due to spool with valve body hole is tapered and offset, there is pressure distribution change in the different gap place making circumferencial direction, and spool is created a radial imbalance force, simultaneously because adopt O-ring seals to seal between the spool of the design and valve body, leakage rate is almost nil, and the design ignores hydraulic card clamping force;

Stable state fluid power computing formula:

F_W=C_d��D�Ħ�psin��

Simultaneously, structure due to spool, when spool commutates two mouthfuls all in opening, liquid stream on one side is streamed under becoming, liquid stream on one side becomes upper streamed, but the steady-state fluid force that spool is subject to is all in one direction, all in opposite direction with liquid stream, so the steady-state fluid force of two ball valves need to be calculated in calculating formula. And no matter spool is in left position or right position, situation is all identical, when calculating, only with calculating spool at steady-state fluid force on one side, the steady-state fluid force of spool calculates the steady-state fluid force that need to calculate in two kinds of situations, one is little opening, i.e. ��=1/3 �� max, when one is spool standard-sized sheet;

Thus obtaining, steady-state fluid force summation is:

��F_W=F_W1+F_W2=C_d��D�Ħ�psin��₁+C_d��D(S-��)��psin��₂

In formula:

Cd is valve port flow coefficient, takes Cd=1;

D valve port diameter;

The opening amount of �� valve;

�� p valve port two ends pressure reduction (Pa), takes 1MPa during little opening, take 0.1MPa during big opening;

�� fluid flow angle, takes ��=69 �� during big opening, take ��=21 �� during little opening;

Structure due to spool, when spool commutates two mouthfuls all in opening, liquid stream on one side is streamed under becoming, liquid stream on one side becomes upper streamed, but the steady-state fluid force that spool is subject to is all in one direction, all in opposite direction with liquid stream, so the steady-state fluid force of two ball valves need to be calculated in calculating formula. And no matter spool is in left position or right position, situation is all identical, when calculating, only with calculate spool steady-state fluid force.

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

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

��F_W=F_W1+F_W2=C_d��D�Ħ�psin��₁+C_d��D(S-��)��psin��₂

��F_W=4.8N

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

��F_W=C_d��D�Ħ�psin��₁=4.1N

Spool Calculation of the force formula:

The maximum working load of spring can be calculated by following formula

F_t2> �� F_W+F_p1=8N

��F_WStable state steady-state fluid force on spool;

F_p1Hydraulic coupling on spool

Take Ft2=15N

So the rigidity of spring:

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

In formula:

��F_mFrictional resistance summation;

F_pThe pressure that spool produces;

F_t1Spring minimum workload.

��F_WSteady-state fluid force when spool circle is opened;

F_t2Little spring maximum working load;

The rigidity of K1 spring;

Thus:

Open and control piston

Open control piston to be intended to open spool, need to meet the following conditions

F_{Open 1}> �� F_m+F_p+F_t1

F_{Open 1}Opening spool active force;

F_{Open 2}Closure state spool active force;

��F_mFrictional resistance summation;

F_pThe pressure that spool produces;

F_t1Little spring minimum workload;

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

F_{Open 2}> �� F_W+F_p+F_t2-F_From;

Closing control piston

When the valves are closed, closure piston pushes main valve plug open, now needs to overcome the power of self-locking piston and frictional force to also have steady-state fluid force. When valve cuts out, P, R, C communicate, and valve is in unloading condition, and the liquid in self-locking piston loses pressure, and closing control piston only needs only small power to close, so only with calculating the closing control piston power when valve begins to shut off.

Closing control piston need to meet the following conditions

F_Close> �� F_m+��F_W+F_From-K(X_t+S)-F_p

Return spring elastic force computing formula:

K₁(X_T+ S)=�� F_W1+��F_m1+F_p1

In formula:

��F_w1The spool steady-state fluid force when 569bar open;

��F_m1Spool is frictional resistance sum when 569bar;

F_p1The fluid pressure that ball valve core is subject to when 569bar;

After spool puts in place, need to meet the following conditions, due to spool speed of action quickly, general < 0.01s, so reliable for spool, it is assumed that control liquid in piston and flow out but without having enough time, so need to calculate to control the active force that piston produces herein.

KX_t> F_{From 1}

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

K(X_t+S-1/3��_max) > F_{From 1}+��F_{W1 is little}+��F_m1

��F_{W1 is little}The spool steady-state fluid force when the little opening of 69bar;

4th step, main valve designs, according to first three obtained data of step, carry out latching ram diameter, return spring calculating, control that piston diameter calculates, resetting piston calculates and the calculating of returning spring:

Latching ram diameter

Latching ram is when locked position, and left and right two pilot valve is not switched on, and it is zero that PP pressure acts on the power controlled on piston. Latching ram makes left ball move to right, and push rod pushes right ball open, makes main valve be always held at open mode, oil inlet P=69MPa, and back pressure is 0, and spool could be locked;

The calculating of returning spring

When P mouth pressure is reduced to 27.8Mpa, main valve is automatically switched off,

Valve port diameter D=3.5mm

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

Fetch multiple spring works position F=250N, initial pressure F=200N

5th step, review is checked, the setup parameter scope according to the first step, selected least one set data, and is brought into by selected data in second step and the calculated concrete data of the 3rd step, carries out checking review then in conjunction with valve body practical operation situation and calculates.

In the present embodiment, the 5th described step need to carry out at least two group different parameters and carry out calculation and check.

Reasonable design method of the present invention, computational efficiency and precision are high, and design load and actually used value closer to, effectively raise the reliability of the design work of deep-sea subsea production tree electric hydraulic control valve group list electricity low pressure reversal valve, thus being favorably improved valve body stability in actual use and reliability.

The above; being only the specific embodiment of the present invention, but protection scope of the present invention is not limited thereto, any those familiar with the art is in the technical scope that the invention discloses; change can be readily occurred in or replace, all should be encompassed within protection scope of the present invention. Therefore, protection scope of the present invention should described be as the criterion with scope of the claims.

Claims (2)

1. deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method, it is characterised in that: described deep-sea subsea production tree SCM mono-electricity low pressure reversing valve designs method comprises the steps:

The first step, design is determined according to practical service environment, deep-sea according to valve body runs actual environment situation and working media situation under water, the basic frame for movement of the effective working environment subject range primarily determining that valve body, the every running technology index setting valve body and valve body;

Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic frame for movement, the physical dimension of valve body is carried out calculation and check, wherein needs oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, the minimum aperture of main valve valve port and main valve plug stroke are carried out calculation and check;

3rd step, valve body runs stress calculation and check, the running environment set according to the first step and technical parameter, concrete size in combination with second calculated frame for movement, it is calculated stressing conditions each in valve body ruuning situation checking, wherein needs frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force are carried out calculation and check;

4th step, main valve designs, according to first three obtained data of step, be controlled piston diameter and calculate and the calculating of returning spring;

5th step, review is checked, the setup parameter scope according to the first step, selected least one set data, and is brought into by selected data in second step and the calculated concrete data of the 3rd step, carries out checking review then in conjunction with valve body practical operation situation and calculates.

2. a kind of deep-sea subsea production tree SCM according to claim 1 mono-electricity low pressure reversing valve designs method, it is characterised in that: the 5th described step need to carry out at least two group different parameters and carry out calculation and check.