CN105625982B - A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM - Google Patents
A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM Download PDFInfo
- Publication number
- CN105625982B CN105625982B CN201610071543.1A CN201610071543A CN105625982B CN 105625982 B CN105625982 B CN 105625982B CN 201610071543 A CN201610071543 A CN 201610071543A CN 105625982 B CN105625982 B CN 105625982B
- Authority
- CN
- China
- Prior art keywords
- valve
- spool
- check
- valve body
- diameter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 19
- 238000004519 manufacturing process Methods 0.000 title claims abstract description 16
- 238000004364 calculation method Methods 0.000 claims abstract description 28
- 239000012530 fluid Substances 0.000 claims description 34
- 239000003921 oil Substances 0.000 claims description 19
- 239000007788 liquid Substances 0.000 claims description 11
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 4
- 239000010720 hydraulic oil Substances 0.000 claims description 3
- 238000003860 storage Methods 0.000 claims description 2
- 244000147058 Derris elliptica Species 0.000 claims 1
- 230000005611 electricity Effects 0.000 abstract description 6
- 238000005516 engineering process Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 238000012550 audit Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000002360 preparation method Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 239000013505 freshwater Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B34/00—Valve arrangements for boreholes or wells
- E21B34/02—Valve arrangements for boreholes or wells in well heads
Landscapes
- Life Sciences & Earth Sciences (AREA)
- Engineering & Computer Science (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention provides a kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM, specific design method includes that four steps such as design scheme, geometric dimension calculation and check, valve body operation stress calculation and check and review check are determined according to practical service environment.Reasonable design method of the present invention, computational efficiency and precision are high, and design value and actual use value are more close, the reliability for effectively raising the design work of deep-sea subsea production tree electrichydraulic control valve group list electricity low pressure reversal valve, to help to improve the stability and reliability of valve body in actual use.
Description
Technical field
The present invention relates to a kind of mono- electric low pressure reversing valve designs methods of deep-sea subsea production tree SCM, are exactly a kind of
The mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM.
Background technique
At present in the development process of deep-sea oil gas resource, deep-sea subsea production tree equipment application is very extensive, and in depth
There is vital effect in extra large petrol resources exploitation, but finds in actual use, the current institute on the production tree of deep-sea
The single electric low pressure reversal valve used, will be under the underwater single electric low pressure reversal valve of traditional fresh water or shallow sea water often over empirical equation
Single electricity low pressure reversal valve is transformed and designs preparation, although can satisfy the needs of deep-marine-environment operation to a certain extent,
But in this way the design deep-sea production tree that all obtains of preparation with single electricity low pressure reversal valve running technology parameter with actually make
With between environment there are biggish error, so as to cause single electric low pressure reversal valve operation stability wretched insufficiency under deep-marine-environment,
The experience that tradition passes through simultaneously is during into single electric low pressure reversing valve designs, one side computational accuracy wretched insufficiency, another party
Face computational efficiency is also relatively low, while effective check verifying can not be also carried out to the design structure by being calculated, from
And also cause greatly to perplex to design work, therefore be directed to this status, there is an urgent need to develop a kind of versatile and simple
Easy single electric low pressure reversing valve designs method, to meet the needs of actual use.
Summary of the invention
The object of the present invention is to provide the present invention to provide a kind of mono- electric low pressure reversing valve designs side deep-sea subsea production tree SCM
Method.
In order to achieve the above object, the invention provides the following technical scheme:
A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM, includes the following steps:
The first step determines design scheme according to practical service environment, runs actual environment feelings under water according to the deep-sea of valve body
Condition and working media situation primarily determine effective working environment adaptation range of valve body, set every running technology index of valve body
And the basic mechanical structure of valve body；
Second step, geometric dimension calculation and check are right according to the valve body technical parameter of first step setting and basic mechanical structure
The geometric dimension of valve body carries out calculation and check, wherein needing to oil inlet and outlet diameter, cue ball valve base inner hole and rod diameter, main valve
Valve port minimum aperture and main valve plug stroke carry out calculation and check；
Third step, valve body run stress calculation and check, according to the running environment and technical parameter of first step setting, tie simultaneously
The specific size for closing second mechanical structure being calculated, carries out calculating check to each stress condition in valve body operating condition,
It wherein needs to carry out school to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool active force and return spring elastic force
Assess calculation；
4th step, main valve design, according to it, first three walks obtained data, carries out control piston diameter and calculates and reply bullet
The calculating of spring；
5th step, review is checked, and according to the setup parameter range of the first step, selectes at least one set data, and by selected number
According to be brought into second step and specific data that third step is calculated in, check then in conjunction with valve body practical operation situation multiple
Audit is calculated.
Further, the 5th 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 value and actual use value are more closely, effectively
The design work for improving deep-sea subsea production tree electrichydraulic control valve group list electricity low pressure reversal valve reliability, to facilitate
Improve the stability and reliability of valve body in actual use.
Detailed description of the invention
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technical description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention for those of ordinary skill in the art without creative efforts, can be with
It obtains other drawings based on these drawings.
Fig. 1 is the method for the present invention flow chart.
Specific embodiment
Technical solution of the present invention is clearly and completely described below in conjunction with attached drawing of the invention, it is clear that retouched
The embodiment stated is only a part of the embodiment of the present invention, instead of all the embodiments.Based on the embodiments of the present invention, originally
Field those of ordinary skill every other embodiment obtained without creative efforts, belongs to the present invention
The range of protection.
Embodiment 1:
A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM as shown in Figure 1, deep-sea production tree are electro-hydraulic
Control valve group list electricity low pressure reversing valve designs method includes the following steps:
The first step determines design scheme according to practical service environment, runs actual environment feelings under water according to the deep-sea of valve body
Condition and working media situation primarily determine effective working environment adaptation range 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 mounted in the sealing container of the 3000 meters of depth of water in ocean
1.2 temperature requirements:
1) storage temperature range: -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 in charge oil pressure P=56.9Mpa hereinafter, within the scope of PP=13.8--37.9Mp
Solenoid valve can be by the opening of control valve, locking and closing, and providing operating pressure for actuator is 11.3-56.9Mpa liquid
Pressure oil, wherein the state being often used is: it is 11.3-that P=56.9Mpa, PP=34.5Mpa, which provide operating pressure for actuator,
56.9Mpa hydraulic oil；
Second step, geometric dimension calculation and check are right according to the valve body technical parameter of first step setting and basic mechanical structure
The geometric dimension of valve body carries out calculation and check, wherein needing to oil inlet and outlet diameter, cue ball valve base inner hole and rod diameter, main valve
Valve port minimum aperture and main valve plug stroke carry out calculation and check:
Oil outlet diameter calculation formula:
Wherein: d-hydraulic fluid port diameter
Q-- metered flow (l/min)；
V-oil inlet and outlet diameter d goes out oil flow, and pressure is bigger, and speed is higher, herein select 10m/s so:
Rounding takes d=6mm；
Cue ball valve base diameter of bore and rod diameter and steel ball size calculation formula:
d1≥1/2D1
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
Valve port of main valve minimum aperture calculation formula:
According to the flow rate calculation formula for passing through valve port are as follows:
In formula:
Q --- pass through valve port fluid flow (m3/s)；
A --- valve port area of passage (m2)；
Δ p --- valve port both 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 as follows:
Wherein,
WhenX1When < < R,
Above formula can be changed to
So the opening minimum aperture formula of valve can be dissolved are as follows:
Δ P=1MPa, Cd=1 are taken, so
X1=0.38mm；
Main valve plug climb displacement formula:
It X1 is had to be larger than by the stroke S of spool obtains: S > X1 and take
S=1mm；
Wherein: S-spool stroke；
X1-valve port of main valve minimum aperture；
Third step, valve body run stress calculation and check, according to the running environment and technical parameter of first step setting, tie simultaneously
The specific size for closing second mechanical structure being calculated, carries out calculating check to each stress condition in valve body operating condition,
It wherein needs to carry out school to frictional resistance, the resistance of motion, hydraulic card clamping force, stable state fluid power, spool 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 O-ring and control piston are only in contact shifting under the action of Pb
It is dynamic, and contact width is constant.
O-ring to control piston clamping force be
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 when calculating
I.e. maximum back pressure when calculate, so respective frictional force are as follows:
Open control piston
Control piston maximum back pressure is Pb2=569bar, O-ring diameter of section d02=1.8mm, piston diameter dt2
Fm2=0.0864Pb2dt2d02=4916dt2=7.08N；
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, can with spool actuation time by 0.01s when average speed replace；So spool
μ --- oil liquid dynamic viscosity, the kinematic viscosity of HW443 are 1.9mm2/s；
The unilateral fit clearance of Δ r --- spool and valve body hole, takes 0.05mm here.
So
Since 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 calculates, the generation of hydraulic card clamping force is because of fluid matching between hydraulic valve core and valve body
When closing the flowing in gap, due to spool and valve body hole is tapered and eccentricity, makes the presence of pressure at the different gap of circumferencial direction
Power changes in distribution, and a radial imbalance force is produced to spool, simultaneously because using O shape between the spool and valve body of the design
Sealing ring sealing, 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 spool, in spool commutation two mouthfuls all in open state, the liquid stream on one side is at lower manifold
Formula, the liquid stream on one side is at upper form, but the steady-state fluid force that spool 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 spool is either in left position or right position, situation
All be it is identical, calculate when, only with calculate spool one side steady-state fluid force, spool steady-state fluid force calculating need to calculate
Steady-state fluid force in the case of two kinds, one is small openings, i.e. the δ max of δ=1/3, and one is when spool standard-sized sheet；
Thus it obtains, steady-state fluid force summation are as follows:
∑FW=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 both ends pressure difference (Pa), when small opening, take 1MPa, and when big opening takes 0.1MPa；
α --- fluid flow angle, when big opening, take α=69 °, and when small opening takes α=21 °；
Due to the structure of spool, in spool commutation two mouthfuls all in open state, the liquid stream on one side is at dirty form, one
The liquid stream on side is at upper form, but the steady-state fluid force that spool 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 spool is either in left position or right position, and situation is all phase
With, when calculating, only uses and calculate spool in the steady-state fluid force on one side.
The steady-state fluid force of spool calculates the steady-state fluid force that need to be calculated in the case of two kinds, and one is small openings, i.e. δ=1/
3 δ max, one is when spool standard-sized sheet.
When spool is in small opening, δ=0.127mm, steady-state fluid force summation at this time are as follows:
∑FW=FW1+FW2=CdπDδΔpsinα1+CdπD(S-δ)Δpsinα2
∑FW=4.8N
When valve is in standard-sized sheet, δ=S=2mm, steady-state fluid force summation at this time is
∑FW=CdπDδΔpsinα1=4.1N
Spool Calculation of the force formula:
The maximum working load of spring can be calculated as the following formula
Ft2> ∑ FW+Fp1=8N
∑FW--- the stable state steady-state fluid force on spool；
Fp1--- the hydraulic coupling on spool
Take Ft2=15N
So the rigidity of spring:
In formula:
∑Fm--- frictional resistance summation；
Fp--- the pressure that spool generates；
Ft1--- spring minimum workload.
∑FW--- steady-state fluid force when spool circle is opened；
Ft2--- little spring maximum working load；
The rigidity of K1 --- spring；
Thus:
Open control piston
Control piston spool to be opened is opened, the following conditions need to be met
FOpen 1> ∑ Fm+Fp+Ft1
FOpen 1--- open state spool active force；
FOpen 2--- closed state spool active force；
∑Fm--- frictional resistance summation；
Fp--- the pressure that spool generates；
Ft1--- little spring minimum workload；
When spool in place after, the following conditions need to be met:
FOpen 2> ∑ FW+Fp+Ft2-FFrom；
Close control piston
When the valves are closed, closure piston pushes main valve plug open, and needing the power for overcoming self-locking piston and frictional force at this time, there are also stable states
Hydraulic power.P, R, C are communicated when valve is closed, and valve is in unloading condition, and the liquid in self-locking piston loses pressure, close control piston
Only needing the power of very little can close, so only closing power of the control piston when valve is begun to shut off with calculating.
The following conditions need to be met by closing control piston
FIt closes> ∑ Fm+∑FW+FFrom-K(Xt+S)-Fp
Return spring elastic force calculation formula:
K1(XT+ S)=∑ FW1+∑Fm1+Fp1
In formula:
∑Fw1--- steady-state fluid force of the spool in 569bar open；
∑Fm1--- spool the sum of frictional resistance in 569bar；
Fp1--- the fluid pressure that ball valve core is subject in 569bar；
When spool in place after, the following conditions need to be met, quickly due to spool movement speed, general < 0.01s, thus in order to
Spool it is reliable, it is assumed that control piston in liquid have enough time flowing out not yet, so need herein calculate control piston generate work
Firmly.
KXt> FFrom 1
When spool is to small aperture position, the following conditions need to be met, need to equally calculate the active force that control piston generates.
K(Xt+S-1/3δmax) > FFrom 1+∑FW1 is small+∑Fm1
∑FW1 is small--- steady-state fluid force of the spool in the small opening of 69bar；
4th step, main valve design, according to it, first three walks obtained data, carries out locking piston diameter, return spring
It calculates, control piston diameter calculates, resetting piston calculates and the calculating of returning spring:
Lock piston diameter
Piston is locked in locked position, two pilot valves of left and right are not switched on, and the power that PP pressure acts on control piston is
Zero.Locking piston moves to right left ball, and push rod pushes right ball open, and main valve is made to be always held at opening state, oil inlet P=69MPa, back
Pressure is 0, and spool could lock；
The calculating of returning spring
When P mouthfuls of pressure reductions are to 27.8Mpa, main valve is automatically closed,
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, and according to the setup parameter range of the first step, selectes at least one set data, and by selected number
According to be brought into second step and specific data that third step is calculated in, check then in conjunction with valve body practical operation situation multiple
Audit is calculated.
In the present embodiment, the 5th 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 value and actual use value are more closely, effectively
The design work for improving deep-sea subsea production tree electrichydraulic control valve group list electricity low pressure reversal valve reliability, to facilitate
Improve the stability and reliability of valve body in actual use.
The above description is merely a specific embodiment, but scope of protection of the present invention is not limited thereto, any
Those familiar with the art in the technical scope disclosed by the present invention, can easily think of the change or the replacement, and should all contain
Lid is within protection scope of the present invention.Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (1)
1. a kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM, it is characterised in that: adopt under water at the deep-sea
The mono- electric low pressure reversing valve designs method of oil tree SCM includes the following steps:
The first step determines that design scheme, valve body are installed in 3000 meters of underwater sealing containers in deep-sea according to practical service environment,
Storage temperature is -18 DEG C -+50 DEG C, and operating temperature is -5 DEG C -+40 DEG C, and working media is water base fluid, valve body P=
The operating pressure for providing hydraulic oil under the charge oil pressure of 56.9Mpa, PP=34.5Mpa for actuator is 11.3-56.9Mpa, just
Walk the basic mechanical structure for determining valve body；
Second step, geometric dimension calculation and check, according to the valve body technical parameter of first step setting and basic mechanical structure, to valve body
Geometric dimension carry out calculation and check, utilize formulaCheck oil inlet and outlet diameter；It is checked using the D1 of formula d1 >=1/2
Cue ball valve base inner hole and rod diameter；Utilize formulaValve port of main valve minimum is checked to open
Degree；Main valve plug stroke is checked using formula S > X1；
Third step, valve body run stress calculation and check, according to the running environment and technical parameter of first step setting, in combination with the
The specific size for the mechanical structure that two steps are calculated carries out calculating check to each stress condition in valve body operating condition, utilizes
FormulaCheck frictional resistance；Utilize formulaIt checks the resistance of motion, utilize formulaIt checks stable state fluid power, utilize formulaSpool active force when check spool to be opened；Utilize formula
Check spool back valve core active force in place；Utilize formulaCheck return spring
Elastic force；
4th step, main valve design, according to it, first three walks obtained data, analyzes and determines control piston diameter and returning spring；
5th step, review is checked, and according to the setup parameter range of the first step, selectes at least one set data, and by selected data band
Enter in the specific data being calculated to second step and third step, carries out checking review meter then in conjunction with valve body practical operation situation
It calculates；5th step need to carry out at least two groups different parameters and carry out calculation and check；
Wherein: d-hydraulic fluid port diameter；V-oil inlet and outlet diameter d goes out oil flow；D1-rod diameter；D1-rod diameter master
Ball seat diameter of bore；Oil flow in v-circular passage；Q --- pass through valve port fluid flow (m3/s)；Δp——
Valve port both ends pressure difference (Pa)；Cd --- it is valve port flow coefficient；S-spool stroke；X1-valve port of main valve minimum aperture；
--- frictional resistance；
Dt --- diameter of piston rod；D0 --- O-ring end face diameter；Pb --- allow back pressure；--- the resistance of motion；D——
Control piston diameter；L --- the contact length of control piston and valve body hole；V --- valve core movement speed；μ --- oil liquid power
Viscosity；The unilateral fit clearance of Δ r --- spool and valve body hole；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 both ends pressure difference；--- frictional resistance summation；
--- the pressure that spool generates；--- spring minimum workload；
--- steady-state fluid force when spool circle is opened；
--- spring maximum working load；--- steady-state fluid force of the spool in 569bar open；
--- spool the sum of frictional resistance in 569bar；--- the fluid pressure that ball valve core is subject in 569bar.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610071543.1A CN105625982B (en) | 2016-02-02 | 2016-02-02 | A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610071543.1A CN105625982B (en) | 2016-02-02 | 2016-02-02 | A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105625982A CN105625982A (en) | 2016-06-01 |
| CN105625982B true CN105625982B (en) | 2019-08-23 |
Family
ID=56041273
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610071543.1A Active CN105625982B (en) | 2016-02-02 | 2016-02-02 | A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105625982B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114109950B (en) * | 2021-11-16 | 2024-04-09 | 大连海事大学 | Multifunctional matching calculation method for valve port independent control electrohydraulic system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004084871A (en) * | 2002-08-28 | 2004-03-18 | Mitsubishi Heavy Ind Ltd | Solenoid valve designing method and solenoid valve |
| CN102141156A (en) * | 2011-03-31 | 2011-08-03 | 西华大学 | Four eccentric butterfly valve and design method |
| CN103615570A (en) * | 2013-11-21 | 2014-03-05 | 北京工业大学 | Two-position three-way electromagnetic reversing valve for deep-sea collection |
| WO2015052423A1 (en) * | 2013-10-09 | 2015-04-16 | Snecma | Method for designing a valve and method for producing a valve |
| CN105179708A (en) * | 2015-10-14 | 2015-12-23 | 四川华林自控科技有限公司 | Energy-saving balance high-pressure valve and design method |
-
2016
- 2016-02-02 CN CN201610071543.1A patent/CN105625982B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004084871A (en) * | 2002-08-28 | 2004-03-18 | Mitsubishi Heavy Ind Ltd | Solenoid valve designing method and solenoid valve |
| CN102141156A (en) * | 2011-03-31 | 2011-08-03 | 西华大学 | Four eccentric butterfly valve and design method |
| WO2015052423A1 (en) * | 2013-10-09 | 2015-04-16 | Snecma | Method for designing a valve and method for producing a valve |
| CN103615570A (en) * | 2013-11-21 | 2014-03-05 | 北京工业大学 | Two-position three-way electromagnetic reversing valve for deep-sea collection |
| CN105179708A (en) * | 2015-10-14 | 2015-12-23 | 四川华林自控科技有限公司 | Energy-saving balance high-pressure valve and design method |
Non-Patent Citations (2)
| Title |
|---|
| 井下液控换向阀的设计与应用研究;朱朝发;《中国优秀硕士学位论文全文数据库基础科学辑》;20141031;A011-534 |
| 电液换向阀在水下生产控制系统中的应用研究;李磊等;《石油机械》;20130331;第41卷(第3期);58-62 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105625982A (en) | 2016-06-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8991416B2 (en) | Shuttle valve | |
| CN104864137B (en) | Leading type water pressure overflow valve | |
| CN105508674B (en) | A kind of slip damp type hydraulic overflow valve for high-pressure high-flow system | |
| CN203230907U (en) | Cavitation-resistant regulated drain valve | |
| US7757703B2 (en) | Device for regulating pressure | |
| US9879799B2 (en) | Pressure regulator | |
| CN105625982B (en) | A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM | |
| US9657850B2 (en) | High performance subsea pressure regulator | |
| CN105587707B (en) | A kind of double electric low pressure reversing valve designs methods of deep-sea subsea production tree SCM | |
| CN105718696B (en) | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method | |
| CN105587706B (en) | A kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group | |
| CN105740552B (en) | A kind of double electric low pressure reversing valve designs methods of deep-sea production tree electrichydraulic control valve group | |
| CN102072216B (en) | Energy-saving reducing valve for hydraulic system | |
| CA2968380C (en) | Gas lift valve assemblies and methods of assembling same | |
| RU2493355C2 (en) | Back pressure valve | |
| CN103162007A (en) | V-shaped ball valve | |
| CN204717128U (en) | A kind of step-down noise reduction modulating valve | |
| CN107781458A (en) | New hydraulic pressure pilot operated electromagnetic relief valve | |
| RU115819U1 (en) | CHECK VALVE | |
| CN214598281U (en) | Energy recovery pump for reverse osmosis water treatment system | |
| CN202580200U (en) | Lining fluorine valve arranged in medical equipment pipeline | |
| CN103982685B (en) | Seawater corrosion resistance equilibrated valve | |
| CN205956421U (en) | Valve door part that leakproofness is high | |
| CN211875243U (en) | Electromagnetic valve seat assembly | |
| RU72291U1 (en) | SEMI-HOUSING VALVE LATCH AND VALVE LATCH |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |