CN116906633A - Steam extraction check valve - Google Patents
Steam extraction check valve Download PDFInfo
- Publication number
- CN116906633A CN116906633A CN202311184281.6A CN202311184281A CN116906633A CN 116906633 A CN116906633 A CN 116906633A CN 202311184281 A CN202311184281 A CN 202311184281A CN 116906633 A CN116906633 A CN 116906633A
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- valve
- unit
- closing shaft
- strong closing
- extraction check
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Links
- 238000000605 extraction Methods 0.000 title claims abstract description 37
- 238000012856 packing Methods 0.000 claims abstract description 11
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical group [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 32
- 239000000945 filler Substances 0.000 claims description 12
- 210000004907 gland Anatomy 0.000 claims description 7
- 238000004364 calculation method Methods 0.000 claims description 6
- 230000005484 gravity Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 6
- 230000001133 acceleration Effects 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- 238000013461 design Methods 0.000 abstract description 6
- 238000011160 research Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- 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
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member
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- 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
- F16K15/00—Check valves
- F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
- F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
- F16K15/1821—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism for check valves with a hinged or pivoted closure member
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- 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
- F16K27/02—Construction of housing; Use of materials therefor of lift valves
- F16K27/0209—Check valves or pivoted valves
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details Of Valves (AREA)
Abstract
The invention discloses a steam extraction check valve, belongs to the field of valve design of a nuclear turbine system, and aims to solve the problems of long working time and low efficiency of obtaining valve opening moment required by the steam extraction check valve under different opening degrees by means of three-dimensional software and analysis software. According to the scheme provided by the invention, the structures of the packing and the valve cavity are designed, and when the structure sizes of the valve body, the valve seat structure and the valve clack assembly meet the relation provided by the invention, the total opening moment and the total resisting moment of the steam extraction check valve can be directly calculated when the valve clack assembly is opened by a certain angle beta, the problems of long working time, low efficiency and the like caused by solving by means of three-dimensional model software and analysis software are avoided, the dimensional proportion relation affecting the valve opening moment is standardized, and the design efficiency is improved. The invention provides a steam extraction check valve, which is characterized in that a valve clack assembly does not vibrate under an opening working condition.
Description
Technical Field
The invention belongs to the field of valve design of a nuclear turbine system, and particularly relates to a steam extraction check valve.
Background
The opening and closing mode of the steam extraction check valve is swing type, the medium is superheated steam, the medium is arranged on a horizontal pipeline between an outlet of the steam turbine and the heater, and the medium is close to the steam turbine and used for preventing uncontrolled high-energy steam in the steam extraction pipeline from flowing backwards to damage the blades of the steam turbine.
If the valve clack opening angle of the steam extraction check valve leaves enough travel allowance, when the valve actually operates, the valve clack can vibrate repeatedly, the valve clack impacts the valve body, potential safety hazards and noise are generated, and therefore the research on the calculation method of the valve opening moment is significant.
Preliminary researches are carried out on valve opening moments of the steam extraction check valve by scientific researchers, internal flow channel models of the valve under different opening degrees are drawn through three-dimensional software, then the internal flow channel models are led into CFX analysis software, working condition parameters are set and solved, and the valve opening moments required under the different opening degrees of the steam extraction check valve can be extracted.
Therefore, it is needed to provide a steam extraction check valve which is convenient for calculating the valve opening moment so as to solve the above technical problems.
Disclosure of Invention
The invention aims to provide a steam extraction check valve, which aims to solve the problems of long working time and low efficiency caused by the fact that valve opening moments required under different opening degrees of the steam extraction check valve are extracted by means of three-dimensional software modeling and CFX software analysis and solving. The technical scheme adopted by the invention is as follows:
a steam extraction check valve comprises a valve body, a valve clack assembly and a strong closing shaft; the valve body is provided with a valve cavity, an inlet and an outlet at two sides of the valve body are communicated through the valve cavity, the tail end of the inlet is provided with a valve seat structure, the valve clack assembly comprises a valve clack body, a rocker arm and a main shaft, the main shaft is hinged in the valve cavity, the valve clack body is connected with the main shaft through the rocker arm, the valve clack body opens and closes the valve seat structure, the strong closing shaft is in rotary sealing fit with the valve body through a filler, the output end of the strong closing shaft is circumferentially provided with a plurality of clutch bulges, the input end of the main shaft is circumferentially provided with a plurality of clutch grooves, the clutch bulges are correspondingly inserted into the clutch grooves one by one, and the clutch grooves are provided with spaces for the corresponding clutch bulges to circumferentially rotate;
the valve cavity consists of a first spherical table-shaped cavity and a second spherical table-shaped cavity, the spherical table sections of the first spherical table-shaped cavity and the second spherical table-shaped cavity are overlapped and aligned, and the spherical centers of the first spherical table-shaped cavity and the second spherical table-shaped cavity are on the overlapped spherical table sections;
the valve seat structure has an inner diameter of a minimum flow path diameter D in m:
SR 1 =（0.97~1）×D；
SR 2 =（1.6~1.8）×D；
L=（0.7~0.75）×D；
wherein:
SR 1 the radius of the first spherical cavity is m;
SR 2 the radius of the second spherical cavity is m;
l is the distance between the main shaft and the central line of the valve cavity, and the unit is m;
setting the diameter of the front end of the inlet to be D 1 In m, then D 1 =（1.08~1.2）×D；
The packing is formed by overlapping a plurality of layers of graphite rings with square sections, and when the outer diameter of the strong closing shaft is 14-16 mm, the number of the graphite rings is 5, and the width of the graphite rings is 5mm; when the outer diameter of the strong closing shaft is 18-24 mm, the number of the graphite rings is 6, and the width of the graphite rings is 6mm; when the outer diameter of the strong closing shaft is 28-36 mm, 7 graphite rings are arranged and the width is 8mm; when the outer diameter of the strong closing shaft is 40-48 mm, 7 graphite rings are arranged and the width is 10mm; when the outer diameter of the strong closing shaft is 52-62 mm, 7 graphite rings are arranged and the width is 13mm; when the outer diameter of the strong closing shaft is 65-78 mm, 7 graphite rings are arranged and the width is 16mm; when the outer diameter of the strong closing shaft is 82-100 mm, 7 graphite rings are arranged and the width is 19mm;
setting the outer diameter of the valve clack body as D S The unit is m; the opening angle of the valve clack body is beta, the unit is degrees, and the opening angle is less than or equal to 35 degrees through limit structures in the valve cavity; when the opening angle of the valve clack body is beta, the valve opening moment generated by the superheated steam is M 0 The unit is N.m; when the opening angle of the valve clack body is beta, the valve closing moment generated by the valve clack assembly is M 1 The unit is N.m; the friction resisting moment generated by the strong closing shaft and the filler during rotation is M 2 In N.m, L and D S The following four formulas are satisfied:
；
；
；
M 0 ＞M 1 +M 2 ；
wherein:
p is the dynamic pressure of the medium, and the unit is MPa;
e is an empirical coefficient, and is equal to beta;
m is the mass of the valve clack assembly, and the unit is kg;
L 1 the unit is m, which is the distance between the gravity center G of the valve clack assembly and the central line of the main shaft;
in the valve closing state, the theta is the included angle between the connecting line of the gravity center G of the valve clack assembly and the spindle axis and the sealing surface of the valve seat structure, and the unit is an angle;
gravitational acceleration;
pi is the circumference ratio;
mu is the friction coefficient between the filler and the strong off axis;
P 1 for the calculation of the pressure, the unit is MPa;
d is the diameter of the strong off axis, and the unit is m;
the medium dynamic pressure P is determined by the following formula:
；
wherein: w is the medium flow rate, and the unit is m/s;
v is the specific volume of the medium, and the unit is m 3 /kg；
Calculate the resulting pressure P 1 Determined by the following formula:
when P W P is less than or equal to 2.5MPa 1 =10.2; when P W At > 2.5MPa, P 1 =10.2×P W ；
Wherein:
P W the nominal pressure is given in MPa.
Further, one end of the rocker arm is sleeved on the screw rod on the back of the valve clack body and can be detachably fixed through the valve clack nut.
Further, the valve cover is connected with the valve body through bolts.
Further, the number of the clutch protrusions is two.
Further, the valve further comprises an actuator, the actuator is fixed on the valve body through a bracket, and the output end of the actuator is connected with the input end of the strong closing shaft.
Further, the actuator is a servo motor, a stepping motor, a rotary hydraulic cylinder or a rotary cylinder.
Further, a shaft shoulder structure is arranged at the inner end of the strong closing shaft, the packing is sleeved on the strong closing shaft, the packing is pressed on the shaft shoulder structure by the gland, and the gland is arranged on the side face of the valve body through a bolt.
Compared with the prior art, the invention has the beneficial effects that:
1. the steam extraction check valve provided by the invention standardizes the dimensional proportion relation affecting the valve opening moment, and improves the design efficiency.
2. The steam extraction check valve provided by the invention can efficiently and accurately calculate the valve opening moment generated by superheated steam.
3. After the minimum flow passage through which superheated steam flows is set by the steam extraction check valve provided by the invention, dynamic pressure can uniformly act on the valve clack body.
4. The steam extraction check valve provided by the invention can accurately calculate the friction resisting moment generated at the filler.
5. The invention provides a steam extraction check valve, which is characterized in that a valve clack assembly does not vibrate under an opening working condition.
Drawings
FIG. 1 is a schematic cross-sectional view of the present invention;
FIG. 2 is a front view of the present invention;
FIG. 3 is a structural and parametric diagram of a valve body;
FIG. 4 is a parametric diagram of a valve flap assembly and an air intake;
fig. 5 is a schematic illustration of the axial fit of the spindle and the strong off-axis.
In the drawings, 1, valve body, 11, inlet, 12, first spherical table-shaped cavity, 13, second spherical table-shaped cavity, 14, outlet, 15, valve seat structure, 16, valve cavity, 2, valve flap assembly, 21, valve flap body, 22, rocker arm, 23, main shaft, 231, clutch groove, 24, valve flap nut, 3, valve cover, 4, strong closing shaft, 41, clutch bulge, 5, actuator, 6, gland, 7.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, the present invention is described below by means of specific embodiments shown in the accompanying drawings. It should be understood that the description is only illustrative and is not intended to limit the scope of the invention. In addition, in the following description, descriptions of well-known structures and techniques are omitted so as not to unnecessarily obscure the present invention.
The connection mentioned in the invention is divided into fixed connection and detachable connection, wherein the fixed connection is a conventional fixed connection mode such as folding connection, rivet connection, bonding connection, welding connection and the like, the detachable connection comprises a conventional detachable mode such as bolt connection, buckle connection, pin connection, hinge connection and the like, and when a specific connection mode is not limited, at least one connection mode can be found in the conventional connection mode by default to realize the function, and the person skilled in the art can select the function according to the needs. For example: the fixed connection is welded connection, and the detachable connection is bolted connection.
The present invention will be described in further detail below with reference to the accompanying drawings, the following examples being illustrative of the present invention and the present invention is not limited to the following examples.
Examples: as shown in fig. 1-5, a steam extraction check valve comprises a valve body 1, a valve clack assembly 2 and a strong shut-off shaft 4; the valve body 1 is provided with a valve cavity 16, an inlet 11 and an outlet 14 at two sides of the valve body 1 are communicated through the valve cavity 16, the tail end of the inlet 11 is provided with a valve seat structure 15, the valve clack assembly 2 comprises a valve clack body 21, a rocker arm 22 and a main shaft 23, the main shaft 23 is hinged in the valve cavity 16, the valve clack body 21 is connected with the main shaft 23 through the rocker arm 22, the valve clack body 21 opens and closes the valve seat structure 15, the strong closing shaft 4 is in rotary sealing fit with the valve body 1 through a filler 7, the output end of the strong closing shaft 4 is circumferentially provided with a plurality of clutch bulges 41, the input end of the main shaft 23 is circumferentially provided with a plurality of clutch grooves 231, the clutch bulges 41 are correspondingly inserted into the clutch grooves 231 one by one, and the clutch grooves 231 are provided with spaces for the corresponding clutch bulges 41 to circumferentially rotate;
the valve cavity 16 consists of a first spherical table-shaped cavity 12 and a second spherical table-shaped cavity 13, wherein the spherical table sections of the first spherical table-shaped cavity 12 and the second spherical table-shaped cavity 13 are aligned in a superposition way, the spherical centers of the first spherical table-shaped cavity 12 and the second spherical table-shaped cavity 13 are on the spherical table sections which are coincident, the other spherical table section of the first spherical table-shaped cavity 12 is communicated with the inlet 11 of the valve body 1, and the other spherical table section of the second spherical table-shaped cavity 13 is communicated with the outlet 14 of the valve body 1;
the valve seat structure 15 has an inner diameter of the minimum flow path diameter D in m:
SR 1 =（0.97~1）×D；
SR 2 =（1.6~1.8）×D；
L=（0.7~0.75）×D；
wherein:
SR 1 radius of the first spherical cavity 12 is m;
SR 2 the radius of the second spherical table-shaped cavity 13 is m;
l is the distance between the main shaft 23 and the central line of the valve cavity 16, and the unit is m;
the diameter of the front end of the inlet 11 is set to D 1 In m, then D 1 =（1.08~1.2）×D；
The packing 7 is formed by overlapping a plurality of layers of graphite rings with square cross sections, and when the outer diameter of the strong closing shaft 4 is 14-16 mm, the number of the graphite rings is 5, and the width of the graphite rings is 5mm; when the outer diameter of the strong closing shaft 4 is 18-24 mm, the number of the graphite rings is 6, and the width is 6mm; when the outer diameter of the strong closing shaft 4 is 28-36 mm, the number of graphite rings is 7, and the width is 8mm; when the outer diameter of the strong closing shaft 4 is 40-48 mm, 7 graphite rings are arranged, and the width of the graphite rings is 10mm; when the outer diameter of the strong closing shaft 4 is 52-62 mm, 7 graphite rings are arranged and the width is 13mm; when the outer diameter of the strong closing shaft 4 is 65-78 mm, the number of the graphite rings is 7, and the width is 16mm; when the outer diameter of the strong closing shaft 4 is 82-100 mm, 7 graphite rings are arranged, and the width is 19mm;
set the outer diameter of the valve clack body 21 to D S The unit is m; the opening angle of the valve clack body 21 is beta, the unit is degrees, and the opening angle is less than or equal to 35 degrees through limit structures in the valve cavity 16 according to design experience; when the opening angle of the valve flap body 21 is beta, the valve opening moment generated by the superheated steam is M 0 The unit is N.m; valve clack body21 is beta, the valve closing moment generated by the valve clack assembly 2 is M 1 The unit is N.m; the friction resisting moment generated by the strong closing shaft 4 and the filler 7 when rotating is M 2 In N.m, L and D S The following four formulas are satisfied:
；
；
；
M 0 ＞M 1 +M 2 ；
wherein:
p is the dynamic pressure of the medium, and the unit is MPa;
e is an empirical coefficient, and is equal to beta;
m is the mass of the valve clack assembly 2, and the unit is kg;
L 1 the unit is m which is the distance between the gravity center G of the valve clack assembly 2 and the central line of the main shaft 23;
in the valve closing state, the included angle between the connecting line of the gravity center G of the valve clack assembly 2 and the axial lead of the main shaft 23 and the sealing surface of the valve seat structure 15 is expressed in degrees;
gravitational acceleration;
pi is the circumference ratio;
μ is the coefficient of friction between the filler 7 and the strong off-axis 4; the higher the nominal pressure of the valve, the smaller the friction coefficient, and the μ value is 0.78 when the nominal pressure of the valve is PN25, and the μ value is 0.525 when the nominal pressure of the valve is PN 150.
P 1 For the calculation of the pressure, the unit is MPa;
d is the diameter of the strong off axis 4, and the unit is m;
the medium dynamic pressure P is determined by the following formula:
；
wherein:
w is the medium flow rate, and the unit is m/s;
v is the specific volume of the medium, and the unit is m 3 /kg；
Calculate the resulting pressure P 1 Determined by the following formula:
when P W P is less than or equal to 2.5MPa 1 =10.2; when P W At > 2.5MPa, P 1 =10.2×P W ；
Wherein:
P W the nominal pressure is given in MPa.
One end of the rocker arm 22 is sleeved on a screw rod on the back surface of the valve clack body 21 and is detachably fixed through a valve clack nut 24.
The valve cover 3 is connected with the valve body 1 through bolts.
The clutch projections 41 are two.
The valve further comprises an actuator 5, wherein the actuator 5 is fixed on the valve body 1 through a bracket, and the output end of the actuator 5 is connected with the input end of the strong closing shaft 4.
The actuator 5 is a servo motor, a stepping motor, a rotary hydraulic cylinder or a rotary cylinder.
The inner end of the strong closing shaft 4 is provided with a shaft shoulder structure, the packing 7 is sleeved on the strong closing shaft 4, the packing 7 is pressed on the shaft shoulder structure by the gland 6, and the gland 6 is arranged on the side face of the valve body 1 through a bolt.
The following specifically describes the calculation process in connection with DN600, PN25 extraction check valve examples related to the present invention:
superheated steam flow rate w=54.8m/s, specific volume v= 0.4326151m 3 Kg, valve clack external diameter D S =0.587m, mass of the flap assembly m= 174.41kg, angle θ=11.27 °, distance L 1 0.3262m, minimum flow diameter d=0.55 m, and strong axis outer diameter 48mm;
then, SR 1 = (0.97-1) ×d= (0.97-1) ×0.55=0.5335-0.55 m, with a value of 0.535m;
SR 2 = (1.6-1.8) ×d= (1.6-1.8) ×0.55=0.88-0.99 m, with a value of 0.88m;
center line distance l= (0.7-0.75) ×d= (0.7-0.75) ×0.55=0.385-0.4125 m, and the value is 0.39m;
the width of the graphite ring is 10mm, and the number of the graphite ring layers is 7;
inlet diameter D 1 = (1.08-1.2) ×d= (1.08-1.2) ×0.55=0.594-0.66 m, with a value of 0.6m;
calculating to obtain the dynamic pressure P= 3470.8MPa of the medium;
when the opening angle beta of the valve clack body 21 is 35 DEG, the valve opening moment M generated by the superheated steam 0 =708.68N·m；
Nominal pressure P W =2.5 MPa, calculate pressure P 1 =10.2MPa；
The friction resisting moment generated by the strong closing shaft 4 and the filler 7 when rotating is M 2 =122.1N·m；
When the opening angle β of the valve flap body 21 is 35 °, the valve closing moment generated by the valve flap assembly 2 is:
M 1 =402.82N·m；
the total opening moment of the valve is as follows:
M 0 =708.68N·m；
the total resisting moment is as follows:
M 1 +M 2 =122.1+402.82=524.92N·m；
conclusion: the total opening moment of the steam extraction check valve with the structural dimensions of DN600 and PN25 is larger than the total closing moment, and the valve clack assembly 2 does not vibrate under the operating condition.
Through research, when the structural parameters of the packing 7 and the valve cavity 16 are set according to the scheme provided by the invention, and SR 1 、SR 2 、L、D 1 And D satisfy the relation given in the present invention, then L and D S Namely, meets the requirements of the invention and M 0 、M 1 And M 2 The relation between the three-dimensional model software and the analysis software can be used for directly calculating the total opening moment and the total resisting moment of the steam extraction check valve when the valve clack assembly 2 is opened by a certain angle beta, so that the working time caused by solving by the three-dimensional model software and the analysis software is avoided, the efficiency is low, and the practical verification of the relation for many years is carried out on each relation provided by the invention, so that the calculation result is accurate and the efficiency is high.
The steam extraction check valve provided by the invention standardizes the dimensional proportion relation affecting the valve opening moment, and improves the design efficiency.
The steam extraction check valve provided by the invention can efficiently and accurately calculate the valve opening moment generated by superheated steam.
After the minimum flow passage through which superheated steam flows is set by the steam extraction check valve provided by the invention, dynamic pressure can uniformly act on the valve clack body 21.
The steam extraction check valve provided by the invention can accurately calculate the friction resisting moment generated at the filler 7.
The invention provides a steam extraction check valve, wherein a valve clack component 2 does not vibrate under an opening working condition.
The above embodiments are only illustrative of the present invention and do not limit the scope thereof, and those skilled in the art may also make modifications to parts thereof without departing from the spirit of the invention.
Claims (7)
1. A steam extraction check valve comprises a valve body (1), a valve clack assembly (2) and a strong closing shaft (4); the valve body (1) is provided with a valve cavity (16), an inlet (11) and an outlet (14) on two sides of the valve body (1) are communicated through the valve cavity (16), a valve seat structure (15) is arranged at the tail end of the inlet (11), the valve clack assembly (2) comprises a valve clack body (21), a rocker arm (22) and a main shaft (23), the main shaft (23) is hinged in the valve cavity (16), the valve clack body (21) is connected with the main shaft (23) through the rocker arm (22), the valve seat structure (15) is opened and closed by the valve clack body (21), the strong closing shaft (4) is in rotary sealing fit with the valve body (1) through a filler (7), a plurality of clutch protrusions (41) are circumferentially arranged at the output end of the strong closing shaft (4), a plurality of clutch grooves (231) are circumferentially arranged at the input end of the main shaft (23), the clutch protrusions (41) are correspondingly inserted into the clutch grooves (231) one by one, and spaces for the corresponding clutch protrusions (41) to circumferentially rotate.
The method is characterized in that: the valve cavity (16) consists of a first spherical table-shaped cavity (12) and a second spherical table-shaped cavity (13), the spherical table sections of the first spherical table-shaped cavity (12) and the second spherical table-shaped cavity (13) are aligned in a superposition manner, and the spherical centers of the first spherical table-shaped cavity (12) and the second spherical table-shaped cavity (13) are positioned on the spherical table sections where the spherical centers are coincident;
the valve seat structure (15) has an inner diameter of a minimum flow path diameter D, and the unit is m:
SR 1 =（0.97~1）×D；
SR 2 =（1.6~1.8）×D；
L=（0.7~0.75）×D；
wherein:
SR 1 the radius of the first spherical table-shaped cavity (12) is m;
SR 2 the radius of the second spherical table-shaped cavity (13) is m;
l is the distance between the main shaft (23) and the central line of the valve cavity (16), and the unit is m;
setting the diameter of the front end of the inlet (11) to be D 1 In m, then D 1 =（1.08~1.2）×D；
The packing (7) is formed by overlapping a plurality of layers of graphite rings with square sections, and when the outer diameter of the strong closing shaft (4) is 14-16 mm, the number of the graphite rings is 5, and the width of the graphite rings is 5mm; when the outer diameter of the strong closing shaft (4) is 18-24 mm, the number of the graphite rings is 6, and the width of the graphite rings is 6mm; when the outer diameter of the strong closing shaft (4) is 28-36 mm, the number of graphite rings is 7, and the width is 8mm; when the outer diameter of the strong closing shaft (4) is 40-48 mm, the number of graphite rings is 7, and the width is 10mm; when the outer diameter of the strong closing shaft (4) is 52-62 mm, the graphite rings are 7 and 13mm in width; when the outer diameter of the strong closing shaft (4) is 65-78 mm, the graphite rings are 7 and 16mm in width; when the outer diameter of the strong closing shaft (4) is 82-100 mm, the graphite rings are 7 and 19mm in width;
the outer diameter of the valve clack body (21) is set as D S The unit is m; the opening angle of the valve clack body (21) is beta, the unit is degrees, and the opening angle is less than or equal to 35 degrees through limit structure limitation in the valve cavity (16); when the opening angle of the valve clack body (21) is beta, the valve opening moment generated by the superheated steam is M 0 Sheet (S)The bit is N.m; when the opening angle of the valve clack body (21) is beta, the valve closing moment generated by the valve clack assembly (2) is M 1 The unit is N.m; the friction resisting moment generated by the strong closing shaft (4) and the filler (7) when rotating is M 2 In N.m, L and D S The following four formulas are satisfied:
；
；
；
M 0 ＞M 1 +M 2 ；
wherein:
p is the dynamic pressure of the medium, and the unit is MPa;
e is an empirical coefficient, and is equal to beta;
m is the mass of the valve clack assembly (2), and the unit is kg;
L 1 the unit is m which is the distance between the gravity center G of the valve clack assembly (2) and the central line of the main shaft (23);
in the valve closing state, the included angle between the connecting line of the gravity center G of the valve clack assembly (2) and the axial lead of the main shaft (23) and the sealing surface of the valve seat structure (15) is expressed in the unit of degree;
gravitational acceleration;
pi is the circumference ratio;
mu is the friction coefficient between the filler (7) and the strong closing shaft (4);
P 1 for the calculation of the pressure, the unit is MPa;
d is the diameter of the strong closing shaft (4) and the unit is m;
the medium dynamic pressure P is determined by the following formula:
；
wherein:
w is the medium flow rate, and the unit is m/s;
v is the specific volume of the medium, and the unit is m 3 /kg；
Calculate the resulting pressure P 1 Determined by the following formula:
when P W P is less than or equal to 2.5MPa 1 =10.2; when P W At > 2.5MPa, P 1 =10.2×P W ；
Wherein:
P W the nominal pressure is given in MPa.
2. The extraction check valve of claim 1, wherein: one end of the rocker arm (22) is sleeved on a screw rod on the back of the valve clack body (21) and is detachably fixed through a valve clack nut (24).
3. The extraction check valve of claim 1, wherein: the valve cover (3) is connected with the valve body (1) through bolts.
4. The extraction check valve of claim 1, wherein: the number of the clutch protrusions (41) is two.
5. The extraction check valve of claim 1, wherein: the valve further comprises an actuator (5), the actuator (5) is fixed on the valve body (1) through a bracket, and the output end of the actuator (5) is connected with the input end of the strong closing shaft (4).
6. The extraction check valve of claim 5, wherein: the actuator (5) is a servo motor, a stepping motor, a rotary hydraulic cylinder or a rotary cylinder.
7. A steam extraction check valve according to any one of claims 1 to 6 wherein: the inner end of the strong closing shaft (4) is provided with a shaft shoulder structure, a packing (7) is sleeved on the strong closing shaft (4), a gland (6) presses the packing (7) on the shaft shoulder structure, and the gland (6) is arranged on the side face of the valve body (1) through a bolt.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311184281.6A CN116906633B (en) | 2023-09-14 | 2023-09-14 | Steam extraction check valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311184281.6A CN116906633B (en) | 2023-09-14 | 2023-09-14 | Steam extraction check valve |
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| CN116906633A true CN116906633A (en) | 2023-10-20 |
| CN116906633B CN116906633B (en) | 2023-11-24 |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN200955611Y (en) * | 2006-10-08 | 2007-10-03 | 兰州高压阀门有限公司 | Pneumatic air-extraction non-return valve |
| CN103267150A (en) * | 2013-05-14 | 2013-08-28 | 哈电集团哈尔滨电站阀门有限公司 | Novel steam-pumping check valve |
| US20150198343A1 (en) * | 2013-06-24 | 2015-07-16 | Kevin Huber | Valve for roof vent |
| US20200056447A1 (en) * | 2015-08-25 | 2020-02-20 | Interventek Subsea Engineering Limited | Valve |
| CN114776846A (en) * | 2022-05-18 | 2022-07-22 | 哈电集团哈尔滨电站阀门有限公司 | Air extraction check valve and flow passage boundary determining method thereof |
-
2023
- 2023-09-14 CN CN202311184281.6A patent/CN116906633B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN200955611Y (en) * | 2006-10-08 | 2007-10-03 | 兰州高压阀门有限公司 | Pneumatic air-extraction non-return valve |
| CN103267150A (en) * | 2013-05-14 | 2013-08-28 | 哈电集团哈尔滨电站阀门有限公司 | Novel steam-pumping check valve |
| US20150198343A1 (en) * | 2013-06-24 | 2015-07-16 | Kevin Huber | Valve for roof vent |
| US20200056447A1 (en) * | 2015-08-25 | 2020-02-20 | Interventek Subsea Engineering Limited | Valve |
| CN114776846A (en) * | 2022-05-18 | 2022-07-22 | 哈电集团哈尔滨电站阀门有限公司 | Air extraction check valve and flow passage boundary determining method thereof |
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| 郑红丽;: "抽气逆止阀的设计", 锅炉制造, no. 03, pages 56 - 58 * |
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| CN116906633B (en) | 2023-11-24 |
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