CN105587706B - A kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group - Google Patents
A kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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Abstract
The invention provides a kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group, specific design method includes determining that design, physical dimension calculation and check, valve body run four steps such as stress calculation and check and review check according to practical service environment.Reasonable design method of the present invention, computational efficiency and precision are high, and design load with actual use value closer to, the reliability of the design work of the double electric high-pressure reversing valves of deep-sea subsea production tree electrichydraulic control valve group is effectively raised, so as to be favorably improved the stability and reliability of valve body in actual use.
Description
Technical field
It is exactly a kind of deep-sea production tree electrichydraulic control the present invention relates to a kind of double electric high-pressure reversing valve design methods
The double electric high-pressure reversing valve design methods of valve group.
Background technology
At present in the development process of deep-sea oil gas resource, deep-sea subsea production tree equipment application is quite varied, and in depth
There is vital effect in extra large petrol resources exploitation, but find in actual use, the current institute on the production tree of deep-sea
The double electric high-pressure reversing valves used are often to pass through empirical equation, by traditional fresh water double electric high-pressure reversing valves or shallow sea water under water
Lower pair of electric high-pressure reversing valve is transformed and designs preparation, although can meet the need of abyssal environment operation to a certain extent
Will, but design prepares the running technology parameter and reality of the double electric high-pressure reversing valves of deep-sea production tree all obtained in this way
There is larger error between the use environment of border, so as to cause double electric high-pressure reversing valve operation stabilities under abyssal environment serious not
Foot, while the experience that tradition passes through is in double electric high-pressure reversing valve design processes are carried out, one side computational accuracy wretched insufficiency, separately
Under one side computational efficiency is also relatively low, tested while also effective check can not be carried out to the design structure that obtained by calculating
Card, so as to also cause great puzzlement to design work, therefore for this present situation, in the urgent need to develop a kind of highly versatile and
Double electric high-pressure reversing valve design methods simple and easy to apply, the need for meeting actual use.
The content of the invention
There is provided a kind of deep-sea production tree electrichydraulic control valve group double electric high-pressure reversing valves it is an object of the invention to provide the present invention
Design method.
In order to achieve the above object, the present invention provides following technical scheme：
1st, the double electric high-pressure reversing valve design methods of a kind of deep-sea production tree electrichydraulic control valve group, it is characterised in that：Described
The double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group comprise the following steps：
The first step, design is determined according to practical service environment, and actual environment feelings are run under water according to the deep-sea of valve body
Condition, and working media situation, primarily determine that effective working environment accommodation of valve body, set every running technology index of valve body
And the basic mechanical structure of valve body；
Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic mechanical structure are right
The physical dimension of valve body carries out calculation and check, wherein needing to oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valve
Valve port minimum aperture and main valve plug stroke carry out calculation and check；
3rd step, valve body operation stress calculation and check, the running environment set according to the first step and technical parameter, are tied simultaneously
Second specific size for calculating obtained mechanical structure is closed, calculating check is carried out to each stressing conditions in valve body running situation,
Wherein need to carry out school to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, valve element active force and return spring elastic force
Assess calculation；
4th step, main valve design, data according to it obtained by first three step carry out latching ram diameter, return spring
Calculate, control piston diameter is calculated, resetting piston is calculated and the calculating of returning spring；
5th step, review is checked, according to the setup parameter scope of the first step, selectes at least one set data, and by selected number
According to being brought into the specific data that second step and the calculating of the 3rd step are obtained, carry out checking again then in conjunction with valve body practical operation situation
Audit is calculated.
Further, the 5th described step need to carry out at least two groups different parameters and carry out calculation and check.
Reasonable design method of the present invention, computational efficiency and precision are high, and design load is worth with actual use more closely, effectively
The design work for improving the double electric high-pressure reversing valves of deep-sea subsea production tree electrichydraulic control valve group reliability, so as to contribute to
Improve the stability and reliability of valve body in actual use.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the accompanying drawing used required in technology description to be briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can be with
Other accompanying drawings are obtained according to these accompanying drawings.
Fig. 1 is the inventive method flow chart.
Embodiment
Technical scheme is clearly and completely described below in conjunction with the accompanying drawing of the present invention, it is clear that retouched
The embodiment stated is only a part of embodiment of the invention, rather than whole embodiments.Based on the embodiment in the present invention, sheet
The every other embodiment that field those of ordinary skill is obtained under the premise of creative work is not made, belongs to the present invention
The scope of protection.
Embodiment 1：
A kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group as shown in Figure 1, deep-sea is recovered the oil
The double electric high-pressure reversing valve design methods of tree electrichydraulic control valve group comprise the following steps：
The first step, design is determined according to practical service environment, and actual environment feelings are run under water according to the deep-sea of valve body
Condition, and working media situation, primarily determine that effective working environment accommodation of valve body, set every running technology index of valve body
And the basic mechanical structure of valve body：
Working environment：
Above-mentioned hydraulic valve is all in the sealing container of the 3000 meters of depth of water in ocean
1.2 temperature requirement：
1) storage temperature scope：-18℃—+50℃；
2) operating temperature range：-5℃—+40℃.
3) working media：Water base fluid, such as HW443.
Control principle：When oil circuit is normal, valve is under charge oil pressure P=69Mpa, electromagnetism in the range of PP=13.8--37.9Mp
Valve can be by the opening of control valve, locking and closing, and it is 41.4-69Mpa hydraulic oil to provide operating pressure for actuator, its
In the state that often uses be：It is 41.4-69Mpa hydraulic oil that P=69Mpa, PP=34.5Mpa provide operating pressure for actuator；
During in-line decompression, i.e. during P≤27.6Mpa, valve is closed automatically, while actuator resets.
Technical indicator：This valve main valve is two position, three-way electromagnetic change valve, and with reset and auto-lock function, C mouthfuls are gone back band
There is pressure tap；The opening and closing of valve are by pilot valve control, the independent fuel feeding of pilot valve, oil return and the common road of main valve oil return.
Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic mechanical structure are right
The physical dimension of valve body carries out calculation and check, wherein needing to oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valve
Valve port minimum aperture and main valve plug stroke carry out calculation and check：
Oil-out diameter calculation formula：
Wherein：D-hydraulic fluid port diameter
Q-- metered flows (l/min)；
V-oil inlet and outlet diameter d goes out oil flow, and pressure is bigger, and speed is higher, herein from 10m/s
So：
Rounding takes d=6mm；
Cue ball valve base diameter of bore and rod diameter and steel ball size calculation formula:
d1≥1/2 D1
Flow formula by circular passage between valve port and push rod is
Above formula flow Q is brought into metered flow, the oil flow V in circular passage, becauseThen
D1=5mm, d1=3.5mm are 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
Main valve valve port minimum aperture calculation formula：
It is according to by the flow rate calculation formula of valve port：
In formula：
Q --- pass through valve port fluid flow (m3/s)；
A --- valve port area of passage (m2)；
Δ p --- valve port two ends pressure difference (Pa)；
Ρ --- fluid density (kg/m3)；
Cd --- it is valve port flow coefficient；
Valve port area of passage A calculation formula are：
Wherein,
WhenWhen,Above formula can be changed into
So the minimum aperture formula of the opening of valve can be dissolved is：
Δ P=1MPa, Cd=1 are taken, so
X1=0.38mm；
Main valve plug climb displacement formula：
X1 is have to be larger than by the stroke S of valve element to obtain：S>X1, takes
S=1mm；
Wherein：The stroke of S-valve element；
The minimum aperture of X1-main valve valve port；
3rd step, valve body operation stress calculation and check, the running environment set according to the first step and technical parameter, are tied simultaneously
Second specific size for calculating obtained mechanical structure is closed, calculating check is carried out to each stressing conditions in valve body running situation,
Wherein need to carry out school to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, valve element active force and return spring elastic force
Assess calculation：
Frictional resistance calculation formula：
Due to bt=0.55d；
D0 is the end face diameter of O-ring seals.It is assumed that in the presence of Pb, O-ring only comes in contact shifting with control piston
It is dynamic, and contact width is constant.
O-ring is to the clamping force for controlling piston
Then
Fm=fN=0.275 π fPbdtd0
Wherein：Fm--- frictional resistance；
F --- coefficient of friction, can use f=0.1；
Dt --- diameter of piston rod；
D0 --- O-ring end face diameter；
Pb --- allow back pressure；
So
Fm=0.0864Pbdtd0
If there is 5 O-ring seals on main valve plug, for safety, according to the maximal friction of each O-ring seals during calculating
I.e. maximum back pressure when calculate, so respective frictional force is：
From lock control piston
It is Pb1=569bar, O-ring diameter of section d01=1.8mm, piston diameter dt1 to control the maximum back pressure of piston
Fm1=0.0864Pb1dt1d01=4916dt1=8.58N；
Open control piston
It is Pb2=569bar, O-ring diameter of section d02=1.8mm, piston diameter dt2 to control the maximum back pressure of piston
Fm2=0.0864Pb2dt2d02=4916dt2=7.08N；
Closing control piston push rod
Push rod maximum back pressure is Pb3=569bar, O-ring diameter of section d03=1.8mm, piston diameter dt3
Fm3=0.0864Pb3dt3d03=4916dt3=7.08N
Closing control piston
It is Pb4=379bar, O-ring diameter of section d02=1mm, piston diameter dt4 to control the maximum back pressure of piston
Fm4=0.0864Pb4dt4d04=4916dt4=8.58N；
Resistance of motion calculation formula：
Wherein：FV--- the resistance of motion；
D --- control piston diameter；
L --- the contact length of control piston and valve body hole；
V --- valve core movement speed, average speed when can be 0.01s with valve element actuation time is replaced；So valve element
μ --- fluid dynamic viscosity, HW443 kinematic viscosity is 1.9mm2/s；
The unilateral fit clearance of Δ r --- valve element and valve body hole, takes 0.05mm here.
So
Because hydraulic oil viscosity is low, and the fit clearance of valve is relatively large, so the resistance of motion is very small, so calculating
Formula is ignored.
When hydraulic card clamping force is calculated, the generation of hydraulic card clamping force is because fluid matching somebody with somebody between hydraulic pressure valve core and valve body
When closing the flowing in gap, due to valve element and valve body hole is tapered and offset, make the presence of pressure at the different gap of circumferencial direction
Power changes in distribution, and a radial imbalance force is generated to valve element, simultaneously because using O shapes between the valve element and valve body of the design
Sealing ring is sealed, and leakage rate is almost nil, and the design ignores hydraulic card clamping force；
Stable state fluid power calculation formula：
FW=CdπDδΔpsinα
Simultaneously as the structure of valve element, when valve element commutates two mouthfuls all in opening, the liquid stream on one side is into lower manifold
Formula, the liquid stream on one side is into upper form, but the steady-state fluid force that valve element is subject to is all in one direction, all with liquid flow path direction phase
Instead, so the steady-state fluid force of two ball valves need to be calculated in calculating formula.And valve element is either in left position or right position, situation
All it is identical, when calculating, only with steady-state fluid force of the valve element on one side is calculated, the steady-state fluid force of valve element, which is calculated, to be needed to calculate
Steady-state fluid force in the case of two kinds, one kind is the δ max of small opening, i.e. δ=1/3, when one kind is valve element standard-sized sheet；
Thus obtain, steady-state fluid force summation is：
ΣFW=FW1+FW2=CdπDδΔpsinα1+CdπD(s-δ)Δpsinα2
In formula：
Cd --- it is valve port flow coefficient, takes Cd=1；
D --- valve port diameter；
The amount of opening of δ --- valve；
Δ p --- valve port two ends pressure difference (Pa), takes 1MPa, 0.1MPa is taken during big opening during small opening；
α --- fluid flow angle, takes α=69 °, α=21 ° is taken during small opening during big opening；
Due to the structure of valve element, when valve element commutates two mouthfuls all in opening, the liquid stream on one side is into dirty form, one
The liquid stream on side is into upper form, but the steady-state fluid force that valve element is subject to is all in one direction, all with liquid flow path direction on the contrary, so
The steady-state fluid force of two ball valves need to be calculated in calculating formula.And valve element is either in left position or right position, and situation is all phase
With, when calculating, only use the steady-state fluid force for calculating valve element on one side.
The steady-state fluid force of valve element, which is calculated, need to calculate the steady-state fluid force in the case of two kinds, and one kind is small opening, i.e. δ=1/
3 δ max, when one kind is valve element standard-sized sheet.
When valve element is in small opening, δ=0.127mm, steady-state fluid force summation now is：
ΣFW=FW1+FW2=CdπDδΔpsinα1+CdπD(S-δ)Δpsinα2
ΣFW=4.8N
When valve is in standard-sized sheet, δ=S=2mm, steady-state fluid force summation now is
ΣFW=CdπDδΔpsinα1=4.1N
Valve element Calculation of the force formula：
The maximum working load of spring can be calculated as the following formula
Ft2＞ Σ Fw+Fp1=8N
VFw--- the stable state steady-state fluid force on valve element；
FP1--- the hydraulic coupling on valve element
Take Ft2=15N
So the rigidity of spring：
In formula：
ΣFm--- frictional resistance summation；
FP--- the pressure that valve element is produced；
Ft1--- spring minimum workload.
ΣFw--- steady-state fluid force when valve element circle is opened；
Ft2--- little spring maximum working load；
The rigidity of K1 --- spring；
Thus：
Open control piston
Control piston valve element to be opened is opened, following condition need to be met
FOpen 1＞ Σ Fm+FP+Ft1
FOpen 1--- opening valve element active force；
FOpen 2--- closure state valve element active force；
ΣFm--- frictional resistance summation；
FP--- the pressure that valve element is produced；
Ft1--- little spring minimum workload；
When valve element in place after, following condition need to be met:
FOpen 2＞ Σ Fw+FP+Ft2-FFrom；
Closing control piston
When the valves are closed, closure piston pushes main valve plug open, now needs to overcome the power and frictional force of self-locking piston to also have stable state
Hydraulic power.P, R, C are communicated when valve is closed, and the liquid that valve is in unloading condition, self-locking piston loses pressure, closing control piston
Only needing the power of very little can close, so the only power with calculating closing control piston when valve is begun to shut off.
Closing control piston need to meet following condition
Return spring elastic force calculation formula：
K1(XT+ S)=Σ FW1+ΣFm1+FP1
In formula：
ΣFw1--- steady-state fluid force of the valve element in 569bar opens；
ΣFm1--- valve element frictional resistance sum in 569bar；
Fp1--- the fluid pressure that ball valve core is subject in 569bar；
When valve element in place after, following condition need to be met, due to valve element responsiveness quickly, general ＜ 0.01s, thus in order to
Valve element it is reliable, it is assumed that control piston in liquid be not in time for also outflow, so need herein calculate control piston produce work
Firmly.
KXt＞ FFrom 1
When valve element is to small aperture position, following condition need to be met, the active force that control piston is produced need to be equally calculated.
K(Xt+S-1/3δmax) ＞ FFrom 1+ΣFW1 is small+ΣFm1
ΣFW1 is small--- steady-state fluid force of the valve element in the small openings of 69bar；
4th step, main valve design, data according to it obtained by first three step carry out latching ram diameter, return spring
Calculate, control piston diameter is calculated, resetting piston is calculated and the calculating of returning spring：
Latching ram diameter
Latching ram is in locked position, and the pilot valve of left and right two is not switched on, and PP pressure, which is acted on, controls the power on piston to be
Zero.Latching ram moves to right left ball, and push rod pushes right ball open, main valve is always held at open mode, oil inlet P=69MPa, the back of the body
Press as 0, valve element could be locked；
The calculating of return spring
When controlling oil circuit to break down, valve passes through platform HPU pressure releases, self-closing valve core.Return spring exists
Start to reset in 11.7Mpa-27.6Mpa.During latching ram left chamber P≤27.6MPa, return spring overcomes locking tongue plug to act on
F6, P mouthfuls act on return control piston left end power F8, little spring compression stress and O row circles at frictional force start reset.Just
The frictional force of O row sealing rings, hydraulic card clamping force and liquid steady power are not considered during calculating.
Initially：F1=F2
It is 27.6MPa to take reset pressure
Then take F5=265N, return spring operating position F=265N, initial pressure F=300N
The calculating of returning spring
When P mouthfuls of pressure are reduced to 27.8Mpa, main valve is closed automatically, and returning spring resets sealing Ceramic Balls.
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, according to the setup parameter scope of the first step, selectes at least one set data, and by selected number
According to being brought into the specific data that second step and the calculating of the 3rd step are obtained, carry out checking again then in conjunction with valve body practical operation situation
Audit is calculated.
In the present embodiment, the 5th described step need to carry out at least two groups different parameters and carry out calculation and check.
Reasonable design method of the present invention, computational efficiency and precision are high, and design load is worth with actual use more closely, effectively
The design work for improving the double electric high-pressure reversing valves of deep-sea subsea production tree electrichydraulic control valve group reliability, so as to contribute to
Improve the stability and reliability of valve body in actual use.
The foregoing is only a specific embodiment of the invention, but protection scope of the present invention is not limited thereto, any
Those familiar with the art the invention discloses technical scope in, change or replacement can be readily occurred in, should all be contained
Cover within protection scope of the present invention.Therefore, protection scope of the present invention described should be defined by scope of the claims.
Claims (1)
1. a kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group, it is characterised in that：Described deep-sea
The double electric high-pressure reversing valve design methods of production tree electrichydraulic control valve group comprise the following steps：
The first step, design is determined according to practical service environment, and actual environment situation is run under water according to the deep-sea of valve body, and
Working media situation, the effective working environment accommodation for primarily determining that valve body, the every running technology index for setting valve body and valve
The basic mechanical structure of body；
Second step, physical dimension calculation and check, the valve body technical parameter set according to the first step and basic mechanical structure, to valve body
Physical dimension carry out calculation and check, wherein needing to oil inlet and outlet diameter, cue ball valve base endoporus and rod diameter, main valve valve port
Minimum aperture and main valve plug stroke carry out calculation and check；
3rd step, valve body operation stress calculation and check, the running environment set according to the first step and technical parameter, in combination with the
Two steps calculate the specific size of obtained mechanical structure, and calculating check is carried out to each stressing conditions in valve body running situation, wherein
Check meter need to be carried out to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, valve element active force and return spring elastic force
Calculate；
4th step, main valve design, the data according to it obtained by first three step, carry out latching ram diameter, the calculating of return spring,
Control piston diameter calculating, resetting piston calculating and the calculating of returning spring；
5th step, review is checked, according to the setup parameter scope of the first step, selectes at least one set data, and by selected data band
Enter to second step and the 3rd step and calculate in obtained specific data, carry out checking review meter then in conjunction with valve body practical operation situation
Calculate；
The 5th described step need to carry out at least two groups different parameters and carry out calculation and check.
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