CN108533823B - Hydraulic control ball valve system and control method - Google Patents
Hydraulic control ball valve system and control method Download PDFInfo
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- CN108533823B CN108533823B CN201810234556.5A CN201810234556A CN108533823B CN 108533823 B CN108533823 B CN 108533823B CN 201810234556 A CN201810234556 A CN 201810234556A CN 108533823 B CN108533823 B CN 108533823B
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- 238000000034 method Methods 0.000 title abstract description 9
- 230000001502 supplementing effect Effects 0.000 claims abstract description 34
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 21
- 239000003921 oil Substances 0.000 claims description 216
- 239000010720 hydraulic oil Substances 0.000 claims description 14
- 230000001276 controlling effect Effects 0.000 claims description 13
- 230000001105 regulatory effect Effects 0.000 claims description 6
- 238000005299 abrasion Methods 0.000 abstract description 3
- 230000000694 effects Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000004973 liquid crystal related substance Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 230000000153 supplemental effect Effects 0.000 description 1
Classifications
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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
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/021—Installations or systems with accumulators used for damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- 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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
- F16K47/023—Means in valves for absorbing fluid energy for preventing water-hammer or noise for preventing water-hammer, e.g. damping of the valve movement
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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
- F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
- F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
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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
- F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
- F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
- F16K5/0647—Spindles or actuating means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Hydraulic Motors (AREA)
Abstract
The invention belongs to the technical field of pipeline valves, and particularly relates to a hydraulic control ball valve system and a control method. The hydraulic control ball valve system comprises an eccentric ball valve, a hydraulic station and a control cabinet, wherein the hydraulic station comprises an oil cylinder, an oil supplementing pump, an energy accumulator, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve and a sixth electromagnetic valve. The eccentric ball valve adopted by the invention is improved on the basis of the full-diameter eccentric ball valve, and the hydraulic loss of the full-diameter eccentric ball valve is inherited to be zero, and the invention has the characteristics of small abrasion and long service life; then, an intelligent hydraulic control system (namely a control cabinet and a hydraulic station) is additionally arranged, and the effect of completely eliminating the water hammer is achieved through the excellent design of the hydraulic control system and the intelligent control system.
Description
Technical Field
The invention belongs to the technical field of pipeline valves, and particularly relates to a hydraulic control ball valve system and a control method.
Background
The check valves used in conventional pump stations are mainly of two types: one is a water pump control valve controlled by hydraulic power, and the other is a hydraulic control (heavy hammer) butterfly valve controlled by a hydraulic system. Both types of valves have two-stage closing and closing functions to eliminate part of the water hammer, but have the following disadvantages:
1. the adaptability is poor, the intelligent performance is not enough, the influence of pipeline load is great, the valve rule difference is great under different load conditions, and the water hammer (valve opening water hammer, valve closing water hammer and accident pump stopping water hammer) can not be completely eliminated.
2. The hydraulic loss is large, and the water pump control valve is 3-5 m under the normal water delivery speed due to the complex flow channel; the hydraulic loss is larger as the diameter of the hydraulic butterfly valve is smaller, and the hydraulic loss of the small and medium diameters (DN 1800 or below) is generally 0.4-1 m, so that the hydraulic butterfly valve is generally only used on a large-diameter water conveying pipeline.
Disclosure of Invention
In order to solve the problems, the invention provides a control method of a hydraulic control ball valve system, which has the advantages of small hydraulic loss, small abrasion and long service life, and can intelligently control the opening or closing of an eccentric ball valve so as to completely eliminate the water hammer.
The technical scheme adopted by the invention is as follows: the utility model provides a hydraulically controlled ball valve system, includes the eccentric ball valve that sets up behind the water pump pipeline, its characterized in that: the hydraulic station comprises an oil cylinder for storing oil, an oil supplementing pump controlled by a motor, an energy accumulator for storing high-pressure oil, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve and a sixth electromagnetic valve for controlling a hydraulic oil path;
the oil supplementing pump is connected with the energy accumulator through a first electromagnetic valve to form an oil supplementing way; the energy accumulator is connected with a rodless cavity of the hydraulic cylinder through a second electromagnetic valve to form an oil inlet path, and a piston cavity of the hydraulic cylinder is connected with the oil cylinder through the second electromagnetic valve to form an oil return path; the accumulator is connected with a piston cavity of the hydraulic cylinder through a third electromagnetic valve to form an oil inlet path, and a rodless cavity of the hydraulic cylinder is connected with the oil cylinder through the third electromagnetic valve to form an oil return path;
the accumulator is connected with a piston cavity of the hydraulic cylinder through a sixth electromagnetic valve to form an oil inlet path, one path of a rodless cavity of the hydraulic cylinder is connected with the oil cylinder through a fourth electromagnetic valve, and the other path of the rodless cavity of the hydraulic cylinder is connected with the oil cylinder through a fifth electromagnetic valve to form an oil return path.
Preferably, when the oil pressure of the accumulator is lower than a set value, the motor and the first electromagnetic valve are powered, the rest oil pumps and the electromagnetic valves do not work, the oil supplementing pump is started, and the oil supplementing pump pumps hydraulic oil in the oil cylinder into the accumulator after passing through the high-pressure filter; after the oil pressure of the energy accumulator reaches a set value, the motor and the first electromagnetic valve are powered on, and the energy accumulator stops oil supplementing; the first electromagnetic valve and the second electromagnetic valve are powered on, the other oil pumps and the electromagnetic valves do not work, high-pressure oil of the accumulator enters a rodless cavity of the hydraulic cylinder, and the eccentric ball valve is opened at a constant speed; the first electromagnetic valve and the third electromagnetic valve are powered on, the rest oil pumps and the electromagnetic valves do not work, high-pressure oil of the accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed at a constant speed; the fourth electromagnetic valve, the fifth electromagnetic valve and the sixth electromagnetic valve are powered, the other oil pumps and the electromagnetic valves do not work, high-pressure oil of the accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed rapidly; the fifth electromagnetic valve and the sixth electromagnetic valve are electrified, the rest oil pump and the electromagnetic valves do not work, high-pressure oil of the accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed at a low speed.
Further, the hydraulic station also comprises a manual pump and a manual valve, wherein the manual pump is connected with a rodless cavity of the hydraulic cylinder through a left port of the manual valve to form an oil inlet path, and a piston cavity of the hydraulic cylinder is connected with the oil cylinder through a left port of the manual valve to form an oil return path; the manual pump is connected with a piston cavity of the hydraulic cylinder through a right port of the manual valve to form an oil inlet path, and a rodless cavity of the hydraulic cylinder is connected with the oil cylinder through a right port of the manual valve to form an oil return path.
Further, an air filter and a liquid level relay are arranged on the oil cylinder.
Further, an oil return filter is arranged on an oil return path formed by the second electromagnetic valve, the third electromagnetic valve or the manual valve and the oil cylinder.
Furthermore, the oil supplementing path is provided with a first pressure gauge and a pressure sensor.
Furthermore, a throttle valve is arranged on an oil path between the rodless cavity of the hydraulic cylinder and the fourth electromagnetic valve, and a speed regulating valve is arranged on an oil path between the rodless cavity of the hydraulic cylinder and the fifth electromagnetic valve.
Preferably, the eccentric ball valve comprises a valve body, an auxiliary valve body and a ball body arranged between the valve body and the auxiliary valve body, wherein a valve seat is arranged at the position, corresponding to the ball body, of the auxiliary valve body, a spherical crown matched with the valve seat is arranged on the ball body, and the spherical crown is matched with the valve seat to form a seal for closing the eccentric ball valve; the ball body is provided with a driving shaft and a driven shaft which drive the ball body to rotate between the valve body and the auxiliary valve body, the driving shaft extends out of the valve body and the auxiliary valve body and is connected with a piston rod of the hydraulic cylinder through a crank, and the driven shaft is arranged at the opposite end of the driving shaft.
Further, the valve body and the auxiliary valve body are mutually matched, two coaxial equal-diameter valve body flow passages are formed at two ends of the valve body and are respectively connected with ports of two sections of pipelines, and flow passages with the same nominal diameter as the valve body flow passages are arranged on the ball body.
Further, the axis of the driving shaft and the center of the sphere are not in the same straight line.
A method of controlling a hydraulically controlled ball valve comprising the steps of:
a. and (3) manually controlling the opening or closing of the eccentric ball valve: the manual pump is manually started, the manual valve is in the left position, the other electromagnetic valves and the liquid pump do not work, the rodless cavity of the hydraulic cylinder is filled with oil, the piston cavity is filled with oil, the piston of the hydraulic cylinder extends out, and the ball valve is manually started; the manual pump is manually started, the manual valve is manually operated to be at the right position, the other electromagnetic valves and the liquid pump do not work, the rodless cavity of the hydraulic cylinder is used for discharging oil, the piston cavity is used for feeding oil, the piston of the hydraulic cylinder is contracted out, and the ball valve is manually closed;
b. and (3) oil supplementing of the energy accumulator: when the oil pressure of the accumulator is lower than a set value, the motor and the first battery valve are powered on, the rest of the oil pump and the battery valve do not work, the oil supplementing pump is started, and the oil supplementing pump pumps hydraulic oil in the oil cylinder into the accumulator after passing through the high-pressure filter; after the oil pressure of the energy accumulator reaches a set value, the motor and the first battery valve are powered, and the energy accumulator stops oil supplementing;
c. automatically controlling the eccentric ball valve to open or close at constant speed: the first battery valve and the second battery valve are powered, the rest oil pump and the battery valves do not work, high-pressure oil of the energy accumulator enters a rodless cavity of the hydraulic cylinder, and the eccentric ball valve is opened at a constant speed; the first battery valve and the third battery valve are powered, the rest oil pump and the battery valves do not work, high-pressure oil of the energy accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed at a constant speed;
d. automatically controlling the eccentric ball valve to open or close at constant speed: the fourth battery valve, the fifth battery valve and the sixth battery valve are powered, the rest of the oil pump and the battery valves do not work, high-pressure oil of the energy accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed quickly; and the fifth battery valve and the sixth battery valve are powered, the rest of the oil pump and the battery valves do not work, high-pressure oil of the energy accumulator enters a piston cavity of the hydraulic cylinder, and the eccentric ball valve is closed at a low speed.
The beneficial effects obtained by the invention are as follows: the hydraulic station is used for controlling the eccentric ball valve to be opened or closed, the real-time state fed back by the hydraulic station and the eccentric ball valve is further collected through the control cabinet, and related instructions are made to corresponding signals according to actual conditions, so that the hydraulic control ball valve system can be intelligently and normally operated. The hydraulic station ensures realization of various states of the eccentric ball valve through control of the corresponding oil pump and the electromagnetic valve. The hydraulic station adopts the accumulator to output high-pressure oil, and the oil supplementing pump charges the accumulator, so that the high-pressure oil is not directly output, and the stability of the valve in the opening and closing process is ensured. The speed regulating valve is arranged on the oil way between the rodless cavity of the hydraulic cylinder and the fifth electromagnetic valve, so that good stability of the valve opening and closing rule can be ensured, the influence of load is avoided, and the water hammer is eliminated to the greatest extent. The valve body, the auxiliary valve body and the ball body are all provided with coaxially arranged flow passages with equal nominal diameters, so that the hydraulic loss is small.
The eccentric ball valve adopted by the invention is improved on the basis of the full-diameter eccentric ball valve, and the hydraulic loss of the full-diameter eccentric ball valve is inherited to be zero, and the invention has the characteristics of small abrasion and long service life; then, an intelligent hydraulic control system (namely a control cabinet and a hydraulic station) is additionally arranged, and the effect of completely eliminating the water hammer is achieved through the excellent design of the hydraulic control system and the intelligent control system.
Drawings
FIG. 1 is a control schematic diagram of the present invention;
FIG. 2 is a hydraulic schematic of a hydraulic station;
FIG. 3 is a schematic diagram of the structure of the present invention;
FIG. 4 is a schematic structural view of an eccentric ball valve;
FIGS. 5a and 5b are schematic views of the structure of the valve body of the eccentric ball valve;
FIG. 6 is a state diagram of the eccentric ball valve when it is fully closed;
fig. 7 is a state diagram of the eccentric ball valve when it is fully opened.
Detailed Description
The invention will be further described with reference to the drawings and the specific examples.
As shown in fig. 1 and 3, the hydraulic control ball valve system of the invention comprises a control cabinet 100, a hydraulic station 200 and an eccentric ball valve 300, wherein the control cabinet 100 adopts an intelligent PLC control system, can communicate with a central control room, can feed back the real-time state of the eccentric ball valve 300 to the central control room, and can receive an action command of the central control room, thereby realizing linkage with other equipment such as a water pump; the hydraulic station 200 controls the action of a piston rod of the hydraulic cylinder 400, and the piston rod of the hydraulic cylinder 400 drives the driving shaft 306 of the eccentric ball valve 300 to rotate through a crank, so that the ball 303 is driven to rotate, and further the eccentric ball valve 300 is opened or closed; the eccentric ball valve 300 adopts a hydraulic control non-return water hammer-free full-drift diameter eccentric ball valve, and the eccentric ball valve 300 is arranged behind a water pump pipeline and is used for cutting off or communicating the pipeline.
As shown in fig. 1, the control cabinet 100 can collect real-time status and alarm signals fed back by the hydraulic station 200 and the eccentric ball valve 300, and make related instructions to corresponding signals according to actual conditions, so as to ensure normal operation of the system. The hydraulic station 200 is directly controlled by the electric control cabinet 100, and the state and fault alarm signals of the hydraulic station 200 can be fed back to the electric control cabinet 100.
In an embodiment, the control cabinet 100 is provided with a liquid crystal display and an operation panel, and can directly operate the eccentric ball valve 300 on the panel, set the opening and closing rule of the eccentric ball valve 300, and have a remote/on-site operation switching function.
In an embodiment, the control cabinet 100 is internally integrated with a UPS power source, and can automatically switch to the UPS power source to supply power under the condition that the pump room is suddenly powered off, and drive the hydraulic station 200, control the eccentric ball valve 300 to perform multi-stage valve closing action, eliminate the accident of stopping the pump water hammer, and protect the water pump and the pipeline.
As shown in fig. 2, the hydraulic station 200 adopts the accumulator 209 to output high-pressure oil, the oil supplementing pump 203 charges the accumulator 209, and the high-pressure oil is not directly output, so that the stability of the valve opening and closing process can be ensured by the structure.
The hydraulic station 200 includes an oil cylinder 201 for storing oil, a supplemental pump 203 controlled by a motor 202, and an accumulator 209 for storing high-pressure oil, and first, second, third, fourth, fifth, and sixth solenoid valves 211, 212, 213, 214, 215, and 216 that control a hydraulic oil path.
The oil supplementing pump 203 is connected to the accumulator 209 through a first electromagnetic valve 211 to form an oil supplementing path. The accumulator 209 is connected to the cylinder 201 through a ball valve 210. The first electromagnetic valve 211 adopts a two-position two-way valve, and a first pressure gauge 208 and a pressure sensor 207 are arranged on the oil supplementing path and are used for detecting the oil pressure in the accumulator 209. When the oil pressure of the accumulator 209 is lower than 14.5MPa, the motor 202 and the first electromagnetic valve 211 are powered, the rest of the oil pumps and the electromagnetic valves do not work, the oil supplementing pump 203 is started, the first electromagnetic valve 211 conducts an oil duct, and the oil supplementing pump 203 pumps hydraulic oil in the oil cylinder 201 into the accumulator 209 after passing through the high-pressure filter 204; after the oil pressure of the accumulator 209 reaches 16MPa, the motor 202 and the first electromagnetic valve 211 are powered off, the oil supplementing pump 203 stops working, the first electromagnetic valve 211 cuts off the oil passage, and the accumulator 209 stops supplementing oil. The oil outlet of the oil supplementing pump 203 is provided with a check valve 206 and a quick connector 205, so that the installation and the disassembly of the pipeline of the oil supplementing pump 203 are convenient.
The accumulator 209 is connected with a rodless cavity 401 of the hydraulic cylinder 400 through a second electromagnetic valve 212 to form an oil inlet path, and a piston cavity 402 of the hydraulic cylinder 400 is connected with the oil cylinder 201 through the second electromagnetic valve 212 to form an oil return path; the second electromagnetic valve 212 adopts a three-position four-way valve, the first electromagnetic valve 211 and the second electromagnetic valve 212 are powered, the other oil pumps and the electromagnetic valves do not work, high-pressure oil in the accumulator 209 enters the rodless cavity 401 of the hydraulic cylinder 400 through an oil inlet path, hydraulic oil in the piston cavity 402 of the hydraulic cylinder 400 flows back into the oil cylinder 201 through an oil return path, and the eccentric ball valve 300 is opened at a constant speed. A check valve 206 is arranged between the second electromagnetic valve 212 and the rodless cavity 401 of the hydraulic cylinder 400 on the oil inlet path, and a check valve 206 is arranged between the second electromagnetic valve 212 and the piston cavity 402 of the hydraulic cylinder 400 on the oil return path, and the two check valves 206 on the oil inlet path and the oil return path are mutually interlocked, so that the stable oil pressure in the hydraulic cylinder 400 is ensured. An oil return filter 222 is provided between the second solenoid valve 212 and the cylinder 201 on the oil return path to prevent clogging of the pipe.
The accumulator 209 is connected with a piston cavity 402 of the hydraulic cylinder 400 through a third electromagnetic valve 213 to form an oil inlet path, and a rodless cavity 401 of the hydraulic cylinder 400 is connected with the oil cylinder 201 through the third electromagnetic valve 213 to form an oil return path; the third electromagnetic valve 212 adopts a three-position four-way valve, the first electromagnetic valve 211 and the third electromagnetic valve 213 are powered, the rest of the oil pumps and the electromagnetic valves do not work, high-pressure oil in the accumulator 209 enters a piston cavity 402 of the hydraulic cylinder 400, the high-pressure oil in the accumulator 209 enters the piston cavity 402 of the hydraulic cylinder 400 through an oil inlet path, hydraulic oil in a rodless cavity 401 of the hydraulic cylinder 400 flows back into the oil cylinder 201 through an oil return path, and the eccentric ball valve 300 is closed at a constant speed. A check valve 206 is arranged between the third electromagnetic valve 213 and the piston cavity 402 of the hydraulic cylinder 400 on the oil inlet path, and a check valve 206 is arranged between the third electromagnetic valve 213 and the rodless cavity 401 of the hydraulic cylinder 400 on the oil return path, and the two check valves 206 on the oil inlet path and the oil return path are mutually interlocked, so that the oil pressure in the hydraulic cylinder 400 is ensured to be stable. An oil return filter 222 is provided between the third solenoid valve 213 and the cylinder 201 in the oil return path, to prevent clogging of the pipe.
In one embodiment, the second solenoid valve 212 and the third solenoid valve 212 are disposed in parallel, sharing a common set of oil piping.
The accumulator 209 is connected with a piston cavity 402 of the hydraulic cylinder 400 through a sixth electromagnetic valve 216 to form an oil inlet path, one path of a rodless cavity 401 of the hydraulic cylinder 400 is connected with the oil cylinder 201 through a fourth electromagnetic valve 214, and the other path is connected with the oil cylinder 201 through a fifth electromagnetic valve 215 to form an oil return path.
The fourth electromagnetic valve 214, the fifth electromagnetic valve 215 and the sixth electromagnetic valve 215 are electrified, the rest of the oil pumps and the electromagnetic valves do not work, high-pressure oil in the accumulator 209 enters a piston cavity 402 of the hydraulic cylinder 400, hydraulic oil in a rodless cavity 401 of the hydraulic cylinder 400 flows into the oil cylinder 201 through two oil return paths formed by the fourth electromagnetic valve 214 and the fifth electromagnetic valve 215, and the eccentric ball valve 300 is rapidly closed; the fifth electromagnetic valve 215 and the sixth electromagnetic valve 216 are electrified, the rest of the oil pumps and the electromagnetic valves do not work, high-pressure oil in the accumulator 209 enters a piston cavity 402 of the hydraulic cylinder 400, hydraulic oil in a rodless cavity 401 of the hydraulic cylinder 400 flows into the oil cylinder 201 through a path of oil return path formed by the fifth electromagnetic valve 215, and the eccentric ball valve is closed slowly.
A throttle valve 226 is provided in an oil path between the rodless chamber 401 of the hydraulic cylinder 400 and the fourth electromagnetic valve 214, and a speed regulating valve 225 is provided in an oil path between the rodless chamber 401 of the hydraulic cylinder 400 and the fifth electromagnetic valve 215. The speed regulating valve 225 adopts a proportional speed regulating valve (formed by combining a pressure reducing valve and a throttle valve) instead of a common throttle valve, so that good stability of the switching valve law of the eccentric ball valve 300 can be ensured, and the switching valve is not influenced by load, thereby eliminating water hammer to the greatest extent.
In an embodiment, the hydraulic station 200 can also control the eccentric ball valve 300 in a manual mode, the hydraulic station 200 comprises a manual pump 219 and a manual valve 217, the manual pump 219 is connected with a rodless cavity 401 of the hydraulic cylinder 400 through a left port of the manual valve 217 to form an oil inlet path, and a piston cavity 402 of the hydraulic cylinder 400 is connected with the oil cylinder 201 through a left port of the manual valve 217 to form an oil return path; the manual pump 219 is connected with the piston cavity 402 of the hydraulic cylinder 400 through the right port of the manual valve 217 to form an oil inlet path, and the rodless cavity 401 of the hydraulic cylinder 400 is connected with the oil cylinder 201 through the right port of the manual valve 217 to form an oil return path.
In the manual mode, the manual pump 219 is started, the manual valve 217 is positioned at the left, the manual pump 219 pumps hydraulic oil in the oil cylinder 201 into a rodless cavity 401 of the hydraulic cylinder 400 through two one-way valves 206 at an oil inlet and an oil outlet, a piston cavity 402 of the hydraulic cylinder 400 flows back into the oil cylinder 201 through an oil return filter 222, and the eccentric ball valve 300 is opened manually; the manual valve 217 is positioned on the right, the manual pump 219 pumps hydraulic oil in the oil cylinder 201 into the piston cavity 402 of the hydraulic cylinder 400 through the two one-way valves 206 at the oil inlet and the oil outlet, the rodless cavity 401 of the hydraulic cylinder 400 flows back into the oil cylinder 201 through the oil return filter 222, and the eccentric ball valve 300 is closed manually.
In one embodiment, the cylinder 201 is provided with an air filter 224 and a liquid level relay 223; a second pressure gauge 221 and a relief valve 220 are provided in the oil piping system.
The following table is the operating states of the hydraulic station 200 controlling the eccentric ball valve 300:
as shown in fig. 4, the eccentric ball valve 300 comprises a valve body 301, an auxiliary valve body 307 and a ball body 303, wherein the valve body 301 and the auxiliary valve body 307 are used for connecting two sections of pipelines, the valve body 301 and the auxiliary valve body 307 are mutually matched, two ends of the valve body 301 and the auxiliary valve body 307 form two valve body flow passages, the two valve body flow passages are respectively connected with ports of the two sections of pipelines, the ball body 303 is arranged in a cavity formed by the valve body 301 and the auxiliary valve body 307, a valve seat 304 is arranged at a position, corresponding to the ball body 303, in the auxiliary valve body 307, a spherical crown 305 matched with the valve seat 304 is arranged on the ball body 303, and the spherical crown 305 is matched with the valve seat 304 to form a seal for closing the eccentric ball valve 300. The ball 303 is provided with a driving shaft 306 and a driven shaft 302 which drive the ball 303 to rotate between the valve body 301 and the auxiliary valve body 307, the driving shaft 306 extends out of the valve body 301 and the auxiliary valve body 307 and is connected with a piston rod of the hydraulic cylinder 400 through a crank 500, and the driven shaft 302 is arranged at the opposite end of the driving shaft 306. The axis of the drive shaft 306 is not collinear with the center of the sphere 303. A bearing 308 is arranged between the driving shaft 306 and the valve body 301 and the auxiliary valve body 307, so that mechanical friction is reduced.
The valve body 301 and the auxiliary valve body 307 are matched, the nominal diameters DN of the two valve body flow channels formed at the two ends are equal, the flow channel is arranged on the ball body 303, and the nominal diameters DN of the ball body 303 flow channel and the valve body flow channel are equal. In this embodiment, when the eccentric ball valve 300 is fully opened, the flow passage is in a straight-through structure, the hydraulic loss is equivalent to that of a pipeline, and the eccentric ball valve 300 can be of a side-mounted split type or an upper-mounted split type.
As shown in fig. 6, when the eccentric ball valve 300 is closed, the spherical cap 305 and the valve seat 304 cooperate to form a seal, and the flow passage of the ball 303 and the flow passage of the valve body are coaxial.
As shown in fig. 5a, 5b, 6 and 7, the eccentricity between the revolution center M and the flow path center L of the sphere 303 is e2, and the eccentricity between the revolution center M and the seal center N is e1. When the eccentric ball valve 300 is fully opened, the minimum distance between the ball 303 flow channel and the two valve body flow channels is a and b respectively.
In one embodiment, the eccentric ball valve 300 is provided with an angle sensor, and the real-time valve position signal of the ball 303 is fed back to the control cabinet 100.
A method of controlling a hydraulically controlled ball valve comprising the steps of:
a. the eccentric ball valve 300 is manually controlled to be opened or closed: manually opening the manual pump 219, manually operating the manual valve 217 to be in the left position, disabling the other solenoid valves and the liquid pump, feeding oil into the rodless cavity 401 of the hydraulic cylinder 400, discharging oil from the piston cavity 402, extending the piston of the hydraulic cylinder 400, and manually opening the ball valve; manually opening the manual pump 219, manually operating the manual valve 217 to be in the right position, disabling the other solenoid valves and the liquid pump, discharging oil from the rodless cavity 401 of the hydraulic cylinder 400, feeding oil from the piston cavity 402, retracting the piston of the hydraulic cylinder 400, and manually closing the ball valve;
b. the accumulator 209 supplements oil: when the oil pressure of the accumulator 209 is lower than a set value, the motor 202 and the first battery valve 211 are powered, the rest of the oil pumps and the battery valves do not work, the oil supplementing pump 203 is started, and the oil supplementing pump 203 pumps the hydraulic oil in the oil cylinder 201 into the accumulator 209 after passing through a high-pressure filter; after the oil pressure of the accumulator 209 reaches a set value, the motor 202 and the first battery valve 211 are powered, and the accumulator 209 stops oil supplementing;
c. automatically controlling the constant speed opening or closing of the eccentric ball valve 300: the first battery valve 211 and the second battery valve 212 are powered, the rest of the oil pumps and the battery valves do not work, high-pressure oil of the accumulator 209 enters a rodless cavity 401 of the hydraulic cylinder 400, and the eccentric ball valve 300 is opened at a constant speed; the first battery valve 211 and the third battery valve 213 are powered, the rest of the oil pump and the battery valves do not work, high-pressure oil of the accumulator 209 enters a piston cavity 402 of the hydraulic cylinder 400, and the eccentric ball valve 300 is closed at a constant speed;
d. automatically controlling the constant speed opening or closing of the eccentric ball valve 300: the fourth battery valve 214, the fifth battery valve 215 and the sixth battery valve 216 are powered, the rest of the oil pumps and the battery valves do not work, high-pressure oil of the accumulator 209 enters the piston cavity 402 of the hydraulic cylinder 400, and the eccentric ball valve 300 is closed quickly; the fifth and sixth battery valves 215 and 216 are powered, the remaining oil pumps and battery valves are not in operation, high pressure oil from the accumulator 209 enters the piston chamber 402 of the hydraulic cylinder 400 and the eccentric ball valve 300 is slowly closed.
The foregoing has shown and described the basic principles, principal features and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and that the above embodiments and descriptions are merely illustrative of the principles of the present invention, and various changes and modifications may be made without departing from the spirit and scope of the invention, which is defined in the appended claims. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (9)
1. The utility model provides a hydraulically controlled ball valve system, includes eccentric ball valve (300) behind the water pump pipeline, its characterized in that: the hydraulic station (200) is used for controlling the opening or closing of the eccentric ball valve (300) through the hydraulic cylinder (400), and a control cabinet (100) is used for controlling the hydraulic station (200), wherein the hydraulic station (200) comprises an oil cylinder (201) for storing oil and an accumulator (209) for storing high-pressure oil, and a first electromagnetic valve (211), a second electromagnetic valve (212), a third electromagnetic valve (213), a fourth electromagnetic valve (214), a fifth electromagnetic valve (215) and a sixth electromagnetic valve (216) for controlling a hydraulic oil way;
the energy accumulator (209) is connected with a rodless cavity (401) of the hydraulic cylinder (400) through a second electromagnetic valve (212) to form an oil inlet path, and a piston cavity (402) of the hydraulic cylinder (400) is connected with the oil cylinder (201) through the second electromagnetic valve (212) to form an oil return path; the energy accumulator (209) is connected with a piston cavity (402) of the hydraulic cylinder (400) through a third electromagnetic valve (213) to form an oil inlet path, and a rodless cavity (401) of the hydraulic cylinder (400) is connected with the oil cylinder (201) through the third electromagnetic valve (213) to form an oil return path;
the accumulator (209) is connected with a piston cavity (402) of the hydraulic cylinder (400) through a sixth electromagnetic valve (216) to form an oil inlet path, one path of a rodless cavity (401) of the hydraulic cylinder (400) is connected with the oil cylinder (201) through a fourth electromagnetic valve (214), and the other path of the rodless cavity is connected with the oil cylinder (201) through a fifth electromagnetic valve (215) to form an oil return path.
2. The pilot operated ball valve system of claim 1, wherein: the accumulator (209) is used for supplementing oil through an oil supplementing pump (203) controlled by the motor (202); the oil supplementing pump (203) is connected with the accumulator (209) through a first electromagnetic valve (211) to form an oil supplementing way.
3. The pilot operated ball valve system of claim 2, wherein: when the oil pressure of the accumulator (209) is lower than a set value, the motor (202) and the first electromagnetic valve (211) are powered, the rest oil pumps and the electromagnetic valves do not work, the oil supplementing pump (203) is started, and the oil supplementing pump (203) pumps the hydraulic oil in the oil cylinder (201) into the accumulator (209) after passing through a high-pressure filter; after the oil pressure of the accumulator (209) reaches a set value, the motor (202) and the first electromagnetic valve (211) are powered, and the accumulator (209) stops oil supplementing; the first electromagnetic valve (211) and the second electromagnetic valve (212) are powered, the rest oil pump and the electromagnetic valves do not work, high-pressure oil of the accumulator (209) enters a rodless cavity (401) of the hydraulic cylinder (400), and the eccentric ball valve (300) is opened at a constant speed; the first electromagnetic valve (211) and the third electromagnetic valve (213) are powered, the rest of the oil pumps and the electromagnetic valves do not work, high-pressure oil of the accumulator (209) enters a piston cavity (402) of the hydraulic cylinder (400), and the eccentric ball valve (300) is closed at a constant speed; the fourth electromagnetic valve (214), the fifth electromagnetic valve (215) and the sixth electromagnetic valve (216) are powered, the rest of the oil pumps and the electromagnetic valves do not work, high-pressure oil of the accumulator (209) enters a piston cavity (402) of the hydraulic cylinder (400), and the eccentric ball valve (300) is closed rapidly; the fifth electromagnetic valve (215) and the sixth electromagnetic valve (216) are powered, the rest of the oil pump and the electromagnetic valves do not work, high-pressure oil of the accumulator (209) enters a piston cavity (402) of the hydraulic cylinder (400), and the eccentric ball valve (300) is closed slowly.
4. The hydraulic control ball valve system according to any one of claims 1-3, wherein: the hydraulic station (200) further comprises a manual pump (219) and a manual valve (217), wherein the manual pump (219) is connected with a rodless cavity (401) of the hydraulic cylinder (400) through a left port of the manual valve (217) to form an oil inlet path, and a piston cavity (402) of the hydraulic cylinder (400) is connected with the oil cylinder (201) through a left port of the manual valve (217) to form an oil return path; the manual pump (219) is connected with a piston cavity (402) of the hydraulic cylinder (400) through a right port of the manual valve (217) to form an oil inlet path, and a rodless cavity (401) of the hydraulic cylinder (400) is connected with the oil cylinder (201) through a right port of the manual valve (217) to form an oil return path.
5. The pilot operated ball valve system of claim 2, wherein: the oil supplementing path is provided with a first pressure gauge (208) and a pressure sensor (207).
6. The pilot operated ball valve system of claim 4, wherein: a throttle valve (226) is arranged on an oil path between a rodless cavity (401) of the hydraulic cylinder (400) and the fourth electromagnetic valve (214), and a speed regulating valve (225) is arranged on an oil path between the rodless cavity (401) of the hydraulic cylinder (400) and the fifth electromagnetic valve (215).
7. A pilot operated ball valve system according to claim 1 or 2 or 3, wherein: the eccentric ball valve (300) comprises a valve body (301), a subsidiary valve body (307) and a ball body (303) arranged between the valve body (301) and the subsidiary valve body (307), wherein a valve seat (304) is arranged at the position, corresponding to the ball body (303), of the subsidiary valve body (307), a ball crown (305) matched with the valve seat (304) is arranged on the ball body (303), and the ball crown (305) is matched with the valve seat (304) to form a seal for closing the eccentric ball valve (300); the ball body (303) is provided with a driving shaft (306) and a driven shaft (302) which drive the ball body (303) to rotate between the valve body (301) and the auxiliary valve body (307), the driving shaft (306) extends out of the valve body (301) and the auxiliary valve body (307) and is connected with a piston rod of the hydraulic cylinder (400) through a crank (500), and the driven shaft (302) is arranged at the opposite end of the driving shaft (306).
8. The pilot operated ball valve system of claim 7, wherein: the valve body (301) and the auxiliary valve body (307) are mutually matched, two coaxial equal-diameter valve body flow passages are formed at two ends of the valve body, the two valve body flow passages are respectively connected with ports of two sections of pipelines, and flow passages with the same nominal diameter as the valve body flow passages are arranged on the ball body (303).
9. The pilot operated ball valve system of claim 8, wherein: the axis of the driving shaft (306) and the sphere center of the sphere (303) are not in the same straight line.
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| CN201810234556.5A CN108533823B (en) | 2018-03-21 | 2018-03-21 | Hydraulic control ball valve system and control method |
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| CN108533823B true CN108533823B (en) | 2023-12-05 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| IT201900000121A1 (en) * | 2019-01-07 | 2020-07-07 | P M Servizi Srl | Control device of an actuator |
| CN114278742A (en) * | 2022-01-22 | 2022-04-05 | 芜湖市金贸流体科技股份有限公司 | Integrated energy storage type hydraulic control slow-closing butterfly valve and use method |
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| US4899979A (en) * | 1987-04-10 | 1990-02-13 | Davy Mckee (Stockton) Limited | Bleeder valve assembly |
| JPH0893943A (en) * | 1994-09-22 | 1996-04-12 | Hisaka Works Ltd | Ball valve |
| CN2898479Y (en) * | 2005-12-31 | 2007-05-09 | 廖灿长 | Automatic hydraulically-controlled semispherical butterfly valve |
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