CN105718696B - A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method - Google Patents
A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method Download PDFInfo
- Publication number
- CN105718696B CN105718696B CN201610071544.6A CN201610071544A CN105718696B CN 105718696 B CN105718696 B CN 105718696B CN 201610071544 A CN201610071544 A CN 201610071544A CN 105718696 B CN105718696 B CN 105718696B
- Authority
- CN
- China
- Prior art keywords
- valve
- valve core
- force
- diameter
- formula
- 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
- 230000005611 electricity Effects 0.000 title abstract 2
- 239000007788 liquid Substances 0.000 claims description 20
- 241000191291 Abies alba Species 0.000 claims description 14
- 239000012530 fluid Substances 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 6
- 229910000831 Steel Inorganic materials 0.000 claims description 4
- 239000010959 steel Substances 0.000 claims description 4
- 230000006978 adaptation Effects 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 23
- 238000011161 development Methods 0.000 description 2
- 230000014509 gene expression Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 108700041286 delta Proteins 0.000 description 1
- 238000012938 design process Methods 0.000 description 1
- 239000013505 freshwater Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computational Mathematics (AREA)
- Mechanical Engineering (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Taps Or Cocks (AREA)
Abstract
The present invention provides a kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method, 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 the double electric low pressure reversal valves of deep-sea subsea production tree electrichydraulic control valve group, to help to improve the stability and reliability of valve body in actual use.
Description
Technical Field
The invention relates to a single-electric low-voltage reversing valve design method, in particular to a single-electric low-voltage reversing valve design method for an electro-hydraulic control valve group of a deep-sea Christmas tree.
Background
At present, in the development process of deep sea oil and gas resources, deep sea underwater Christmas tree equipment is widely applied and plays a vital role in the development of deep sea oil and gas resources, but in practical use, the current single-electric low-voltage reversing valve used on the deep sea Christmas tree is designed and prepared by transforming the traditional fresh water underwater single-electric low-voltage reversing valve or shallow sea underwater single-electric low-voltage reversing valve through an empirical formula, although the requirement of deep sea environment operation can be met to a certain extent, the operation technical parameters of the deep sea Christmas tree single-electric low-voltage reversing valve designed and prepared by the method have larger errors with the practical use environment, so that the single-electric low-voltage reversing valve has serious insufficient operation stability in the deep sea environment, and meanwhile, the traditional experience is seriously insufficient in the design process of the single-electric low-voltage reversing valve on the one hand, on the other hand, the calculation efficiency is relatively low, and meanwhile, effective verification and verification cannot be performed on the design structure obtained through calculation, so that great trouble is caused to the design work, and therefore, aiming at the current situation, a valve body design and preparation method which is strong in universality, simple and easy to implement is urgently needed to be developed to meet the requirement of actual use.
Disclosure of Invention
The invention aims to provide a design method of a single-electric low-pressure reversing valve of an electro-hydraulic control valve group of a deep-sea Christmas tree.
In order to achieve the purpose, the invention provides the following technical scheme:
a design method for a single-electric low-voltage reversing valve of an electro-hydraulic control valve group of a deep-sea Christmas tree comprises the following steps:
firstly, determining a design scheme according to an actual use environment, preliminarily determining an effective working environment adaptation range of a valve body, various operation technical indexes of the valve body and a basic mechanical structure of the valve body according to the actual deep sea underwater operation environment condition of the valve body and the working medium condition;
secondly, checking and calculating the geometric dimension, namely checking and calculating the geometric dimension of the valve body according to the technical parameters of the valve body and the basic mechanical structure set in the first step, wherein the checking and calculating of the diameters of an oil inlet and an oil outlet, the diameter of an inner hole and a push rod of a valve seat of a main ball valve, the minimum opening of a valve port of the main valve and the stroke of the main valve core are required;
thirdly, checking and calculating the running stress of the valve body, and according to the running environment and the technical parameters set in the first step and the specific size of the mechanical structure obtained by calculation of the second part, calculating and checking each stress condition in the running condition of the valve body, wherein the friction resistance, the motion resistance, the hydraulic clamping force, the steady hydraulic force, the valve core acting force and the return spring elastic force need to be checked and calculated;
and fourthly, reviewing and checking, namely selecting at least one group of data according to the set parameter range of the first step, bringing the selected data into the specific data obtained by the calculation of the second step and the third step, and then carrying out the reviewing and checking calculation by combining the actual operation condition of the valve body.
Further, it is characterized in that: and in the second step, the diameter of the oil outlet, the diameter of the inner hole of the valve seat of the main ball valve and the push rod, the minimum opening of the valve port of the main valve and the stroke of the main valve core are checked by the following calculation formula:
the oil outlet diameter calculation formula:
wherein: d-diameter of oil port
Q-rated flow l/min;
v is the flow rate of the oil outlet liquid of the diameter d of the oil inlet and outlet, and the higher the pressure is, the higher the speed is;
the calculation formula of the diameter of the inner hole of the valve seat of the main ball valve, the diameter of the push rod and the diameter of the steel ball is as follows:
d1≥1/2D1
the flow formula of the annular channel between the valve port and the push rod is
The flow Q of the above formula is brought in by the rated flow, and the oil flow velocity V in the annular channel is caused byThen
Wherein: d1Diameter of push rod
D1Diameter of push rod and inner hole diameter of main ball valve seat
Velocity of oil flow in V-ring
The minimum opening calculation formula of the main valve port is as follows:
the formula for calculating the flow through the valve port is:
in the formula:
q-liquid flow m through the valve port3/s；
A-valve port flow area m2；
Δ p-differential pressure Pa across the valve port;
rho-fluid density kg/m3；
Cd-is the valve port flow coefficient;
the valve port flow area A is calculated by the formula:
wherein,
when in useWhen the temperature of the water is higher than the set temperature,
the above formula can be changed into
The opening minimum opening formula of the valve can be solved as follows:
the main valve core stroke calculation formula:
the stroke S of the valve core must be larger than X1Obtaining:
S>X1
wherein: s is the stroke of the valve core;
X1-minimum opening of the main valve port;
furthermore, the calculation formulas of the friction resistance, the movement resistance, the hydraulic clamping force, the steady hydraulic force, the valve core acting force and the return spring elastic force in the third step are as follows:
the friction resistance calculation formula is as follows:
Fm＝fN＝0.275πfPbdtd0
wherein: fm-a frictional resistance;
f is friction coefficient, and f can be 0.1;
dt-the diameter of the piston rod;
d0-O-ring end face diameter;
Pb-allowing a back pressure;
the motion resistance calculation formula is as follows:
wherein: fV-resistance to movement;
d-control piston diameter;
l is the contact length of the control piston and the valve body hole;
v is the valve core movement speed;
μ — hydrodynamic viscosity of oil;
delta r is the unilateral fit clearance between the valve core and the valve body hole;
when the hydraulic clamping force is calculated, the hydraulic clamping force is generated because when fluid flows in a fit clearance between a valve core and a valve body of the hydraulic valve, because the valve core and a valve body hole have conicity and eccentricity, pressure distribution changes exist at different clearances in the circumferential direction, a radial unbalanced force is generated on the valve core, and meanwhile, because an O-shaped sealing ring is adopted for sealing between the valve core and the valve body, the leakage amount is almost zero, and the hydraulic clamping force is ignored in the design;
the steady state hydraulic calculation formula is as follows:
FW＝CdπDδΔpsinα (2-17)
meanwhile, due to the structure of the valve core, when the valve core is reversed, two ports are in an open state, the liquid flow on one side is in a downflow mode, the liquid flow on one side is in an upflow mode, but the steady-state hydrodynamic force received by the valve core faces to one direction and is opposite to the liquid flow direction, so the steady-state hydrodynamic force of the two ball valves needs to be calculated in a calculation formula, the conditions of the valve core are the same whether the valve core is in a left position or a right position, when the calculation is carried out, the steady-state hydrodynamic force of the valve core is only calculated on one side, the steady-state hydrodynamic force of the valve core needs to be calculated in two conditions, one is a small opening, namely, delta is 1/3 delta max, and the other is when the valve core;
this gives the sum of the steady-state hydraulic forces:
∑FW＝FW1+FW2＝CdπDδΔpsinα1+CdπD(S-δ)Δpsinα2
in the formula:
Cdto the valve port flowA coefficient;
d is the diameter of the valve port;
δ — amount of opening of valve;
Δ p-differential pressure Pa across the valve port;
α1and α2Angle of flow
Valve core acting force calculation formula:
because the valve core has two working states of opening and closing when the valve body works, the acting forces favored by the valve core in the opening state and the closing state need to be respectively calculated,
thus open state force: fOpening 1＞∑Fm+FP+Ft1
Closed state force: fOpening 2＞∑Fw+FP+Ft2
In the formula: fOpening 1-valve core force in open state;
Fopening 2-closed state spool force;
∑Fm-the sum of the frictional resistances;
FP-the pressure generated by the spool;
Ft1spring minimum workload.
∑Fw-steady state hydrodynamic forces when the spool ring is open;
Ft2-small spring maximum working load;
the elastic force calculation formula of the return spring is as follows:
K1(XT+S)＝∑FW1+∑Fm1+FP1
in the formula:
∑Fw1-steady state hydrodynamic force of the spool at full opening of 569 bar;
∑Fm1-the sum of the frictional resistances of the spool at 569 bar;
FP1the liquid pressure to which the ball valve element is subjected at 569 bar.
The design method is reasonable, the calculation efficiency and the calculation precision are high, the design value is closer to the actual use value, and the reliability of the design work of the single-electric low-pressure reversing valve of the electro-hydraulic control valve group of the deep-sea underwater Christmas tree is effectively improved, so that the stability and the reliability of the valve body in the actual use are improved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a flow chart of the method of the present invention.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example 1:
the design method of the single-electric low-pressure reversing valve of the deep-sea Christmas tree electro-hydraulic control valve group shown in the figure 1 comprises the following steps:
firstly, determining a design scheme according to an actual use environment, preliminarily determining an effective working environment adaptation range of a valve body, various operation technical indexes of the valve body and a basic mechanical structure of the valve body according to the actual deep sea underwater operation environment condition of the valve body and the working medium condition;
secondly, checking and calculating the geometric dimension, namely checking and calculating the geometric dimension of the valve body according to the technical parameters of the valve body and the basic mechanical structure set in the first step, wherein the checking and calculating of the diameters of an oil inlet and an oil outlet, the diameter of an inner hole and a push rod of a valve seat of a main ball valve, the minimum opening of a valve port of the main valve and the stroke of the main valve core are required;
wherein:
the oil outlet diameter calculation formula:
wherein: d-diameter of oil port
Q-rated flow l/min;
v-oil outlet flow velocity of the diameter d of the oil inlet and the oil outlet, the larger the pressure is, the higher the velocity is, and therefore, 10m/s is selected:
rounding to obtain a circle d equal to 6 mm;
the calculation formula of the diameter of the inner hole of the valve seat of the main ball valve, the diameter of the push rod and the diameter of the steel ball is as follows:
d1≥1/2D1
the flow formula of the annular channel between the valve port and the push rod is
The flow Q is carried in at rated flow, the oil flow velocity V in the annular channel is less than or equal to 10m/s, and the oil flow velocity is obtainedThen, becauseThen
Wherein: d1Diameter of push rod
D1Diameter of push rod and inner hole diameter of main ball valve seat
Velocity of oil flow in V-ring
Rounding and taking D1＝7mm,d1＝3.5mm，
The diameter of the steel ball is 10 mm;
the minimum opening calculation formula of the main valve port is as follows:
the formula for calculating the flow through the valve port is:
in the formula:
q-liquid flow m through the valve port3/s；
A-valve port flow area m2；
Δ p-differential pressure Pa across the valve port;
pp-fluid density kg/m3；
Cd-is the valve port flow coefficient;
the valve port flow area A is calculated by the formula:
wherein,
when in useWhen the temperature of the water is higher than the set temperature,the above formula can be changed into
The opening minimum opening formula of the valve can be solved as follows:
taking Delta P as 1MPa, Cd1, so
X1＝0.38mm；
The main valve core stroke calculation formula:
the stroke S of the valve core must be larger than X1Obtaining:
S>X1
get S2 (mm)
Wherein: s is the stroke of the valve core;
X1-minimum opening of the main valve port;
and thirdly, checking and calculating the running stress of the valve body, and according to the running environment and the technical parameters set in the first step and the specific size of the mechanical structure obtained by calculation of the second part, calculating and checking each stress condition in the running condition of the valve body, wherein the friction resistance, the motion resistance, the hydraulic clamping force, the steady hydraulic force, the valve core acting force and the return spring elastic force need to be checked and calculated:
the friction resistance calculation formula is as follows:
Fm＝fN＝0.275πfPbdtd0
wherein: fm-a frictional resistance;
f is friction coefficient, and f can be 0.1;
dt-the diameter of the piston rod;
d0-O-ring end face diameter;
Pb-allowing a back pressure;
if there are 5O-rings on the main valve core, for safety, the maximum friction force of each O-ring, i.e. the maximum back pressure, is calculated, so the respective friction force is
Controlling the maximum back pressure of the piston to be Pb237.9bar, O-ring cross-section diameter d021.8mm, piston diameter dt2
Fm2＝0.0864Pb2dt2d02＝4916dt2
Fm3＝4916×0.018＝10.6N
The motion resistance calculation formula is as follows:
wherein: fV-resistance to movement;
d-control piston diameter;
l-contact length of control piston and valve body hole, taking 6mm
V is the motion speed of the valve core, and can be replaced by the average speed when the action time of the valve core is 0.01 s; so that the valve core
Mu-kinematic viscosity of oil dynamic viscosity HW443 of 1.9mm2/s；
Delta r is the unilateral fit clearance between the valve core and the valve body hole, and is 0.05 mm.
Therefore, it is not only easy to use
As can be seen from the expressions (2 to 17), since the hydraulic oil has a low viscosity and the valve fitting clearance is relatively large, the movement resistance is very small, and therefore, it is ignored in the calculation expression.
When the hydraulic clamping force is calculated, the hydraulic clamping force is generated because when fluid flows in a fit clearance between a valve core and a valve body of the hydraulic valve, because the valve core and a valve body hole have conicity and eccentricity, pressure distribution changes exist at different clearances in the circumferential direction, a radial unbalanced force is generated on the valve core, and meanwhile, because an O-shaped sealing ring is adopted for sealing between the valve core and the valve body, the leakage amount is almost zero, and the hydraulic clamping force is ignored in the design;
the steady state hydraulic calculation formula is as follows:
FW＝CdπDδΔpsinα (2-17)
meanwhile, due to the structure of the valve core, when the valve core is reversed, two ports are in an opening state, the liquid flow on one side is in a downward flow mode, the liquid flow on the other side is in an upward flow mode, but the steady-state hydrodynamic force applied to the valve core faces to one direction and is opposite to the liquid flow direction, so the steady-state hydrodynamic force of the two ball valves needs to be calculated in a calculation formula. The valve core is the same whether in the left position or the right position, and during calculation, only the steady-state hydrodynamic force of the valve core on one side is calculated, and the steady-state hydrodynamic force of the valve core needs to be calculated under two conditions, namely, one is a small opening, namely, delta 1/3 delta max, and the other is when the valve core is fully opened;
this gives the sum of the steady-state hydraulic forces:
∑FW＝FW1+FW2＝CdπDδΔpsinα1+CdπD(S-δ)Δpsinα2
in the formula:
Cdto obtain the valve port flow coefficient, Cd＝1；
D is the diameter of the valve port;
δ — amount of opening of valve;
delta p is the pressure difference (Pa) between two ends of the valve port, 1MPa is taken when the valve port is opened small, and 0.1MPa is taken when the valve port is opened large;
α, when the liquid flow angle is large, α is 69 degrees, and when the liquid flow angle is small, α is 21 degrees;
due to the structure of the valve core, when the valve core is reversed, two ports are in an open state, one side of the valve core is in a downflow mode, and the other side of the valve core is in an upflow mode, but the steady-state hydrodynamic force applied to the valve core is in one direction and is opposite to the direction of the liquid flow, so that the steady-state hydrodynamic forces of the two ball valves need to be calculated in a calculation formula. And the valve core is the same whether in the left position or the right position, and only the steady state hydrodynamic force of the valve core on one side is calculated during calculation.
The steady-state hydrodynamic force calculation of the valve element needs to calculate the steady-state hydrodynamic force in two cases, one is small opening, namely, delta is 1/3 delta max, and the other is when the valve element is fully opened.
When the valve core is in a small opening, delta is 0.127mm, and the sum of the steady-state hydraulic power at the moment is as follows:
∑FW＝FW1+FW2＝CdπDδΔpsinα1+CdπD(S-δ)Δpsinα2 (2-18)
∑FW＝4.8N
when the valve is fully open, delta-S-2 mm, the steady state hydrodynamic sum is
∑FW＝CdπDδΔpsinα1＝4.1N；
Valve core acting force calculation formula:
because the valve core has two working states of opening and closing when the valve body works, the acting forces favored by the valve core in the opening state and the closing state need to be respectively calculated,
thus open state force: fOpening 1＞∑Fm+FP+Ft1
Closed state force: fOpening 2＞∑Fw+FP+Ft2
In the formula: fOpening 1-valve core force in open state;
Fopening 2-closed state spool force;
∑Fm-the sum of the frictional resistances;
FP-the pressure generated by the spool;
Ft1-minimum spring working load.
∑Fw-steady state hydrodynamic forces when the spool ring is open;
Ft2-small spring maximum working load;
the elastic force calculation formula of the return spring is as follows:
K1(XT+S)＝∑FW1+∑Fm1+FP1
in the formula:
∑Fw1-steady state hydrodynamic force of the spool at full opening of 569 bar;
∑Fm1-the sum of the frictional resistances of the spool at 569 bar;
FP1-the liquid pressure to which the ball valve element is subjected at 569 bar;
and fourthly, reviewing and checking, namely selecting at least one group of data according to the set parameter range of the first step, bringing the selected data into the specific data obtained by the calculation of the second step and the third step, and then carrying out the reviewing and checking calculation by combining the actual operation condition of the valve body.
The design method is reasonable, the calculation efficiency and the calculation precision are high, the design value is closer to the actual use value, and the reliability of the design work of the single-electric low-pressure reversing valve of the electro-hydraulic control valve group of the deep-sea underwater Christmas tree is effectively improved, so that the stability and the reliability of the valve body in the actual use are improved.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (3)
1. A design method of a single-electric low-voltage reversing valve of an electro-hydraulic control valve group of a deep-sea Christmas tree is characterized by comprising the following steps: the design method of the single-electric low-voltage reversing valve of the deep-sea Christmas tree electro-hydraulic control valve group comprises the following steps:
firstly, determining a design scheme according to an actual use environment, preliminarily determining an effective working environment adaptation range of a valve body, various operation technical indexes of the valve body and a basic mechanical structure of the valve body according to the actual deep sea underwater operation environment condition of the valve body and the working medium condition;
secondly, checking and calculating the geometric dimension, namely checking and calculating the geometric dimension of the valve body according to the technical indexes and basic mechanical structures of the valve body set in the first step, wherein the checking and calculating of the diameters of an oil inlet and an oil outlet, the diameter of an inner hole and a push rod of a valve seat of a main ball valve, the minimum opening of a valve port of the main valve and the stroke of the main valve core are required;
thirdly, checking and calculating the running stress of the valve body, and according to the running actual environment and the technical indexes set in the first step and the specific size of the mechanical structure obtained by calculation of the second part, calculating and checking each stress condition in the running condition of the valve body, wherein the friction resistance, the motion resistance, the hydraulic clamping force, the steady hydraulic force, the valve core acting force and the return spring elastic force need to be checked and calculated;
and fourthly, reviewing and checking, namely selecting at least one group of data according to the set parameter range of the first step, bringing the selected data into the specific data obtained by the calculation of the second step and the third step, and then carrying out the reviewing and checking calculation by combining the actual operation condition of the valve body.
2. The design method of the single-electric low-pressure reversing valve of the deep-sea Christmas tree electro-hydraulic control valve group according to claim 1, is characterized in that: and in the second step, the diameter of the oil outlet, the diameter of the inner hole of the valve seat of the main ball valve and the push rod, the minimum opening of the valve port of the main valve and the stroke of the main valve core are checked by the following calculation formula:
the oil outlet diameter calculation formula:
wherein: d-diameter of oil port
Q- -rated flow (l/min);
the flow rate of the oil outlet of the oil inlet and outlet port is increased when the pressure is high;
the calculation formula of the diameter of the inner hole of the valve seat of the main ball valve, the diameter of the push rod and the diameter of the steel ball is as follows:
d1≥1/2 D1
the flow formula of the annular channel between the valve port and the push rod is
The flow Q of the above formula is brought in by the rated flow, and the oil flow velocity V in the annular channel is caused byThen, then
Wherein: d1Diameter of push rod
D1Diameter of push rod and inner hole diameter of main ball valve seat
Velocity of oil flow in V-ring
The minimum opening calculation formula of the main valve port is as follows:
the formula for calculating the flow through the valve port is:
in the formula:
q-liquid flow m through the valve port3/s；
A-valve port flow area m2；
Δ p-differential pressure Pa across the valve port;
rho-fluid density kg/m3;
Cd-is the valve port flow coefficient;
the valve port flow area A is calculated by the formula:
；
wherein,；
when in useWhen the temperature of the water is higher than the set temperature,，
the above formula can be changed into
；
The opening minimum opening formula of the valve can be solved as follows:
；
the main valve core stroke calculation formula:
the stroke S of the valve core must be larger than X1Obtaining:
S> X1
wherein: s is the stroke of the valve core;
X1minimum opening of the main valve port.
3. The design method of the single-electric low-pressure reversing valve of the deep-sea Christmas tree electro-hydraulic control valve group according to claim 1, is characterized in that: the calculation formulas of the friction resistance, the movement resistance, the hydraulic clamping force, the steady hydraulic force, the valve core acting force and the return spring elastic force in the third step are as follows:
the friction resistance calculation formula is as follows:
wherein:-a frictional resistance;
ƒ -coefficient of friction, ƒ = 0.1;
dt-piston rod diameter;
d0-O-ring end face diameter;
Pb-allowing a back pressure;
the motion resistance calculation formula is as follows:
wherein:-resistance to movement;
d-control piston diameter;
l is the contact length of the control piston and the valve body hole;
v is the valve core movement speed;
μ — hydrodynamic viscosity of oil;
delta r is the unilateral fit clearance between the valve core and the valve body hole;
when the hydraulic clamping force is calculated, the hydraulic clamping force is generated because when fluid flows in a fit clearance between a valve core and a valve body of the hydraulic valve, because the valve core and a valve body hole have conicity and eccentricity, pressure distribution changes exist at different clearances in the circumferential direction, a radial unbalanced force is generated on the valve core, and meanwhile, because an O-shaped sealing ring is adopted for sealing between the valve core and the valve body, the leakage amount is almost zero, and the hydraulic clamping force is ignored in the design;
the steady state hydraulic calculation formula is as follows:
（2-17）
meanwhile, due to the structure of the valve core, when the valve core is reversed, two ports are in an open state, the liquid flow on one side is in a downflow mode, the liquid flow on one side is in an upflow mode, but the steady-state hydrodynamic force borne by the valve core faces to one direction and is opposite to the liquid flow direction, so the steady-state hydrodynamic force of the two ball valves needs to be calculated in a calculation formula, the conditions of the valve core are the same whether the valve core is in a left position or a right position, when the calculation is carried out, the steady-state hydrodynamic force of the valve core on one side is only calculated, the steady-state hydrodynamic force of the valve core needs to be calculated under two conditions, one is a small opening, namely delta =1/3 delta max, and the other is when the valve;
this gives the sum of the steady-state hydraulic forces:
in the formula:
Cd-is the valve port flow coefficient;
d is the diameter of the valve port;
δ — amount of opening of valve;
Δ p-differential pressure Pa across the valve port;
α1and α2-the liquid flow angle;
valve core acting force calculation formula:
because the valve core has two working states of opening and closing when the valve body works, the acting forces favored by the valve core in the opening state and the closing state need to be respectively calculated,
thus open state force:
closed state force:
in the formula:-valve core force in open state;
-closed state spool force;
-the sum of the frictional resistances;
-the pressure generated by the spool;
-spring minimum work load;
-steady state hydrodynamic forces when the spool ring is open;
-small spring maximum working load;
the elastic force calculation formula of the return spring is as follows:
in the formula:
-steady state hydrodynamic force of the spool at full opening of 569 bar;
-the sum of the frictional resistances of the spool at 569 bar;
the liquid pressure to which the ball valve element is subjected at 569 bar.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610071544.6A CN105718696B (en) | 2016-02-02 | 2016-02-02 | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610071544.6A CN105718696B (en) | 2016-02-02 | 2016-02-02 | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105718696A CN105718696A (en) | 2016-06-29 |
| CN105718696B true CN105718696B (en) | 2019-07-05 |
Family
ID=56155503
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610071544.6A Active CN105718696B (en) | 2016-02-02 | 2016-02-02 | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105718696B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106089855B (en) * | 2016-06-13 | 2017-11-10 | 哈尔滨工业大学 | The hydraulic power optimization method of hydraulic valve |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1375641A (en) * | 2001-03-15 | 2002-10-23 | Dbt有限公司 | Electrohydraulic control apparatus |
| CN1400455A (en) * | 2002-09-19 | 2003-03-05 | 北京航空航天大学 | Hydraulic energy source equipment |
| CN201103401Y (en) * | 2007-10-24 | 2008-08-20 | 中国航天科技集团公司烽火机械厂 | Electric-hydraulic control device |
| CN103511361A (en) * | 2013-10-24 | 2014-01-15 | 江汉石油钻头股份有限公司 | Hydraulic system for underwater Christmas tree |
-
2016
- 2016-02-02 CN CN201610071544.6A patent/CN105718696B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1375641A (en) * | 2001-03-15 | 2002-10-23 | Dbt有限公司 | Electrohydraulic control apparatus |
| CN1400455A (en) * | 2002-09-19 | 2003-03-05 | 北京航空航天大学 | Hydraulic energy source equipment |
| CN201103401Y (en) * | 2007-10-24 | 2008-08-20 | 中国航天科技集团公司烽火机械厂 | Electric-hydraulic control device |
| CN103511361A (en) * | 2013-10-24 | 2014-01-15 | 江汉石油钻头股份有限公司 | Hydraulic system for underwater Christmas tree |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105718696A (en) | 2016-06-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102650342B (en) | Piston type compound sealing axial flow type check valve | |
| EP2564098A1 (en) | Shuttle valve | |
| CN102086938B (en) | Reducing valve | |
| CN203162254U (en) | Check valve | |
| CN105718696B (en) | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method | |
| CN105587707B (en) | A kind of double electric low pressure reversing valve designs methods of deep-sea subsea production tree SCM | |
| CN105625982B (en) | A kind of mono- electric low pressure reversing valve designs method of deep-sea subsea production tree SCM | |
| CN105587706B (en) | A kind of double electric high-pressure reversing valve design methods of deep-sea production tree electrichydraulic control valve group | |
| CN201810811U (en) | Multi-stage seal valve seat structure | |
| CA2968380C (en) | Gas lift valve assemblies and methods of assembling same | |
| CN105740552B (en) | A kind of double electric low pressure reversing valve designs methods of deep-sea production tree electrichydraulic control valve group | |
| CN102094979B (en) | Integrated water hydraulic distributing valve | |
| CN204459327U (en) | A kind of safety valve | |
| CN204083343U (en) | A kind of drilling rod stopcock | |
| CN1766387A (en) | Self-closing valve for tube bursting | |
| CN205064864U (en) | Eccentric metal of two -way four -dimension butterfly valve sealed firmly | |
| Sotoodeh | Selecting a butterfly valve instead of a globe valve for fluid control in a utility service in the offshore industry (based on an industrial experience) | |
| CN107314141A (en) | Straight-through valve and method for controlling water pressure by straight-through valve | |
| CN103162007A (en) | V-shaped ball valve | |
| CN214662230U (en) | Direct-acting pressure reducing valve | |
| CN104964043A (en) | Seawater hydraulic two-position three-way electromagnetic valve for deep sea | |
| CN104595360A (en) | Hydrostatic bearing system | |
| CN107781458A (en) | New hydraulic pressure pilot operated electromagnetic relief valve | |
| CN204628657U (en) | A kind of silencing type safety check | |
| CN203868433U (en) | Mute check valve |
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 |