CN111043365A - High-pressure-difference water-control piston type pressure reducing valve - Google Patents

High-pressure-difference water-control piston type pressure reducing valve Download PDF

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Publication number
CN111043365A
CN111043365A CN201911135864.3A CN201911135864A CN111043365A CN 111043365 A CN111043365 A CN 111043365A CN 201911135864 A CN201911135864 A CN 201911135864A CN 111043365 A CN111043365 A CN 111043365A
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CN
China
Prior art keywords
valve
pressure
flow passage
main valve
clack
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Pending
Application number
CN201911135864.3A
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Chinese (zh)
Inventor
张梅华
马志祥
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WUHAN DAYU VALVE CO Ltd
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WUHAN DAYU VALVE CO Ltd
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Priority to CN201911135864.3A priority Critical patent/CN111043365A/en
Publication of CN111043365A publication Critical patent/CN111043365A/en
Pending legal-status Critical Current

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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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0446—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces
    • F16K17/046—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces the valve being of the gate valve type or the sliding valve type
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/164—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side and remaining closed after return of the normal pressure
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • 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
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member

Abstract

The invention relates to the technical field of valve structures, in particular to a high-pressure-difference water-control piston type pressure reducing valve. Comprises a main valve; the main valve body is a hollow cavity with an inlet flow passage and an outlet flow passage, and a main valve clack is arranged in the main valve body; the main valve clack is fixedly connected with the piston through a valve rod; the lower chamber of the piston is communicated with the outlet flow passage and also comprises a pilot valve; the pilot valve comprises a pilot valve body; an inlet channel of the pilot valve body is communicated with an upper cavity of the piston; the outlet channel of the pilot valve body is communicated with the outlet flow passage; the upper cavity of the piston is communicated with the inlet flow passage; and a control structure which closes the pilot valve when the pressure of the outlet flow passage is less than the set pressure so as to increase the valve clack opening of the main valve and opens the pilot valve when the pressure of the outlet flow passage is greater than the set pressure so as to reduce the valve clack opening of the main valve is arranged in the valve body of the pilot valve. The pressure reducing valve is simple in structure and convenient in control mode, and a fragile structure does not need to be arranged in the flow, so that the service life of the pressure reducing valve is prolonged.

Description

High-pressure-difference water-control piston type pressure reducing valve
Technical Field
The invention relates to the technical field of valve structures, in particular to a high-pressure-difference water-control piston type pressure reducing valve.
Background
According to GB/T12244-. The piston type pressure reducing valve is a pressure reducing valve which adopts a piston as a sensitive element to drive a valve clack to move. Like the chinese utility model patent of "high temperature high pressure guide piston relief pressure valve" of "CN 206617631U", this patent has protected a piston relief pressure valve, and this relief pressure valve includes main valve and pilot valve, and the main valve includes the piston of valve clack and control valve clack, is provided with a spring on the valve gap of valve clack below, and the position of piston control valve clack realizes the aperture control to the outlet flow way. The outlet of the pilot valve is communicated with the upper cavity of the piston, the lower cavity of the piston is communicated with the outlet flow passage of the main valve, and the inlet of the pilot valve is communicated with the inlet flow passage of the valve body. When the pressure of the medium in the main valve outlet channel is reduced to be lower than the setting pressure of the pilot valve, the opening degree of the pilot valve is increased, flowing medium enters the upper piston chamber through the pilot valve, the pressure of the upper chamber is increased, the piston is pushed to move downwards, the opening degree of the valve clack is increased, and the pressure of the medium in the main valve outlet channel is increased. On the contrary, when the medium pressure of the outlet channel of the main valve rises to be higher than the setting pressure of the pilot valve, the opening degree of the pilot valve is reduced, the pressure entering the upper chamber of the piston is reduced, the valve clack rises under the action of the thrust of the spring, the opening degree of the main valve is reduced, and the outlet of the main valve falls back through the pressure. The method controls the medium pressure of the main valve outlet channel to be stabilized at the setting pressure value of the pressure setting device. The pressure reducing valve has the advantages of simple structure, convenient control mode and high control precision, and can stably maintain the medium pressure of the main valve outlet flow passage. However, in the pressure reducing valve structure, a pressure spring needs to be arranged in an inlet flow passage of the main valve as a driving part, the spring is soaked in a flowing medium for a long time and is easy to rust and damage, and the elastic damage of the spring is gradually reduced along with the service time of the main valve, so that the control precision is gradually reduced.
Disclosure of Invention
The invention aims to solve the defects of the background technology and provide a high-pressure-difference water-control piston type pressure reducing valve.
The technical scheme of the invention is as follows: a high pressure difference water control piston type pressure reducing valve comprises a main valve; the main valve comprises a main valve body; the main valve body is a hollow cavity with an inlet flow passage and an outlet flow passage, and a main valve clack for controlling the opening degree of the flow passage is arranged in the main valve body; the main valve clack is fixedly connected with a piston in a piston cylinder on the main valve body through a valve rod; the lower chamber of the piston is in communication with the outlet flow passage,
the method is characterized in that: the device also comprises a pilot valve; the pilot valve comprises a pilot valve body; the pilot valve body is a hollow cavity with an inlet channel and an outlet channel; the inlet channel is communicated with the upper cavity of the piston; the outlet channel is communicated with the outlet flow passage; the upper chamber of the piston is communicated with the inlet flow channel; and a control structure which closes the pilot valve when the pressure of the outlet flow passage is less than the set pressure so as to increase the valve clack opening of the main valve and opens the pilot valve when the pressure of the outlet flow passage is greater than the set pressure so as to reduce the valve clack opening of the main valve is arranged in the valve body of the pilot valve.
Further the control structure comprises an upper flap; a hollow flow passage for communicating the inlet passage and the outlet passage is arranged in the valve body of the pilot valve; the upper valve clack is a block structure which can move in the hollow flow passage to control opening and closing, and a pressure adjusting structure used for adjusting water pressure in the hollow flow passage is arranged in the hollow flow passage below the upper valve clack.
The pressure adjusting structure further comprises a lower valve clack; the lower valve clack is a blocky structure which can move in the hollow flow passage and is arranged at intervals with the upper valve clack, and the lower valve clack, the bottom cover at the lower end of the hollow flow passage and the pilot valve body form a control chamber with variable volume; the control chamber is in communication with the outlet flow passage.
And a pressure setting structure for adjusting the set pressure is further arranged on the pilot valve body above the upper valve clack.
The pressure setting structure further comprises an adjusting screw, a spring seat and a spring; one end of the adjusting screw penetrates through a valve cover at the upper end of the pilot valve body and is fixedly connected with a spring seat in the pilot valve body; one end of the spring is fixed on the spring seat, and the other end of the spring is connected with the upper valve clack.
Furthermore, the main valve clack is of a hollow squirrel-cage structure fixed at the end part of the valve rod, and a plurality of overflowing slotted holes are formed in the circumferential side wall of the main valve clack.
Furthermore, a plurality of strip-shaped through holes which are uniformly arranged at intervals along the circumferential direction are formed in the circumferential side wall of the main valve clack.
The cross-sectional area of the end of the main valve clack far away from the valve rod is smaller than that of the axial end of the piston.
And a throttle valve is arranged on a communication pipeline between the inlet flow channel and the upper cavity of the piston.
And further, a sealing ring is arranged between the circumferential side walls of the upper valve clack and the lower valve clack and the hollow flow channel.
The invention has the advantages that: 1. the pressure reducing valve is simple in structure, the control mode is extremely simple and convenient, the pilot valve is closed when the pressure of the outlet flow passage is smaller than the set pressure, and the pilot valve is opened when the pressure of the outlet flow passage is larger than the set pressure, the control mode is completely different from the existing structure, the control precision is higher, a spring structure does not need to be arranged in the main valve of the pressure reducing valve to serve as an auxiliary force application structure, the problems that parts are easy to damage in flowing and the service life is influenced do not exist, and the service life of the pressure reducing valve is greatly prolonged;
2. the hollow flow channel controls the opening and closing of the flow through the movement of the upper valve clack, so that the pilot valve is opened or closed, the upper valve clack is matched with the pressure adjusting structure, the position of the upper valve clack can be adjusted through changing the pressure in the hollow flow channel, the real-time adjustment of the opening degree of the hollow flow channel is realized in sequence, and the adjusting mode is more accurate and timely;
3. according to the invention, the lower valve clack, the bottom cover and the pilot valve body form a closed control chamber, the control chamber is communicated with the outlet flow channel, namely, the pressure source of the control chamber and the water pressure change of the outlet flow channel are controlled, the control chamber directly acts on the hollow flow channel, the water pressure of the outlet flow channel can be quickly and accurately reflected to the hollow flow channel, the upper valve clack in the hollow flow channel quickly adjusts the water pressure change according to the pressure in the hollow flow channel, so that the water pressure of the outlet flow channel is controlled, and the adjusting mode is extremely simple, efficient and accurate;
4. the pressure setting structure for adjusting the set pressure is arranged on the valve body of the pilot valve, and the position of the upper valve clack in the hollow flow passage can be adjusted through the pressure setting structure, so that the pressure setting structure is suitable for different outlet flow passage pressure requirements and different pipeline structures;
5. the pressure setting structure controls the position of the spring through the adjusting screw, so that the position of the upper valve clack in the hollow flow channel is adjusted, the adjusting mode is very simple, and the pressure setting structure can adapt to various pressure requirements and pipeline structures;
6. the main valve clack of the invention is a squirrel-cage structure, and the structure can cause the water flow entering the main valve clack from the inlet channel to generate mutual impact, and can effectively reduce the water pressure of the outlet channel;
7. the strip-shaped through holes on the main valve clack are uniformly distributed, water flow enters the main valve clack from the strip-shaped through holes, and water column clash is formed in the main valve clack to achieve the effect of energy dissipation and pressure reduction, so that when the opening degree of the valve is smaller, the pressure of the outlet of the valve is far smaller than the pressure of the inlet of the valve, and even if the valve is fully opened, the pressure of the outlet of the valve is obviously lower than the pressure of the inlet of the valve;
8. according to the invention, the throttle valve is arranged between the upper chamber of the piston and the inlet flow channel, so that the water pressure condition in the upper chamber of the piston can be effectively controlled.
The pressure reducing valve has the advantages of simple structure, convenient control mode, accurate water pressure control of the main valve outlet flow passage, short reaction time, no need of arranging a fragile structure in the flow, prolonged service life and great popularization value.
Drawings
FIG. 1: the pressure reducing valve of the invention is structurally schematic;
FIG. 2: the main valve structure of the invention is schematic;
FIG. 3: the invention is a schematic diagram of the structure of a main valve clack;
FIG. 4: FIG. 3 is a schematic view A-A of the present invention;
FIG. 5: the structure schematic diagram of the pilot valve of the invention (C-C view in figure 6);
FIG. 6: the structure schematic diagram of the pilot valve of the invention (B-B view in figure 5);
wherein: 1-a main valve; 11-main valve body; 12-an inlet channel; 13-outlet flow channel; 14-main valve flap; 15-valve stem; 16-a piston cylinder; 17-a piston; 18-a strip-shaped through hole; 19-a throttle valve; 110-valve seat;
2-a pilot valve; 21-a pilot valve body; 22-inlet channel; 23-an outlet channel; 24-upper flap; 25-lower valve flap; 26-hollow flow channel; 27-a bottom cover; 28-adjusting screws; 29-spring seat; 210-a spring; 211-valve cover; 212-sealing ring.
Detailed Description
The invention is described in further detail below with reference to the figures and the specific embodiments.
Referring to fig. 1 to 6, the pressure reducing valve of the present embodiment includes a main valve 1 and a pilot valve 2, fig. 2 is a structure of the main valve 1 of the present embodiment, the main valve 1 includes a main valve body 11, the main valve body 11 is a hollow cavity structure, an inlet channel 12 and an outlet channel 13 are respectively disposed at two ends of the main valve body 11, and water flows into the main valve body 11 from the inlet channel 12 and flows out from the outlet channel 13. The main valve body 1 is internally provided with a main valve clack 14 for controlling the opening degree of the flow channel, as shown in fig. 3 to 4, the main valve clack 14 of the embodiment is of a hollow squirrel cage structure, the circumferential side wall of the main valve clack 14 is provided with a plurality of strip-shaped through holes 18 uniformly arranged at intervals along the circumferential direction, water flows enter the main valve clack 14 to form water column clash, and the effect of energy dissipation and pressure reduction is achieved, when the opening degree of the valve is small, the pressure of the outlet flow channel 13 is far smaller than that of the inlet flow channel 12, and even when the main valve clack 14 is fully opened, the pressure of the.
As shown in fig. 1-2, a valve seat 110 is disposed in the main valve body 11, and the valve seat 110 cooperates with the main valve flap 14 to open or close the main valve body 11. The main valve flap 14 is secured by a valve stem 15 to a piston 17 in a piston cylinder 16 on the main valve body 11. By varying the pressure on both sides of the piston 17, control of the main valve flap 14 is achieved. The piston 17 divides the piston cylinder 16 internal cavity into an upper chamber of the piston 17 and a lower chamber of the piston 17. Since the lower chamber of the piston 17 is communicated with the outlet flow channel 13, the main valve body 11 of the present embodiment is actually divided into three pressure areas, i.e., one pressure area is located in the inlet flow channel 12, one pressure area is defined by the lower chamber of the piston 17 and the outlet flow channel 13, and one pressure area is defined by the upper chamber of the piston 17. In order to realize the control of the main valve flap 14 of the present embodiment, the cross-sectional area of the end of the main valve flap 14 away from the valve stem 15 is smaller than the cross-sectional area of the axial end of the piston 17.
As shown in fig. 5 to 6, for the pilot valve 2 of this embodiment, the pilot valve 2 includes a pilot valve body 21, the pilot valve body 21 is a hollow cavity structure arranged along the vertical direction, an inlet channel 22 and an outlet channel 23 are provided on the pilot valve body 21, the inlet channel 22 and the outlet channel 23 are vertically spaced, a height difference exists, and the inlet channel 22 is located above the outlet channel 23. The cavity inside the pilot valve body 21 forms a hollow flow passage 26 communicating the inlet passage 22 and the outlet passage 23, an upper valve flap 24 is arranged in the hollow flow passage 26, as shown in fig. 5-6, the upper valve flap 24 is a block structure which can move in the hollow flow passage 26 to control opening and closing, the upper valve flap 24 is positioned above the inlet passage 22 when the pilot valve 2 is opened, and the upper valve flap 24 moves vertically to open or close the inlet passage 22.
As shown in fig. 5 to 6, in the present embodiment, a pressure setting structure for adjusting the position of the upper valve flap 24 is disposed at the upper end of the pilot valve body 21, the pressure setting structure includes an adjusting screw 28, a spring seat 29 and a spring 210, one end of the adjusting screw 28 penetrates through a valve cover 211 at the upper end of the pilot valve body 21 and is fixedly connected with the spring seat 29 in the pilot valve body 21, one end of the spring 210 is fixed on the spring seat 29, and the other end is connected to the upper valve flap 24. By screwing the adjusting screw 28, the position of the upper valve flap 24 within the pilot valve body 21 can be changed, thereby adjusting the set pressure at which the pilot valve 2 operates.
In addition, the present embodiment is provided with a control chamber at the lower end of the pilot valve body 21, and the control chamber is used for adjusting the pressure in the hollow flow passage 26, thereby changing the position of the upper valve clack 24 and realizing the real-time adjustment control of the pilot valve 2. As shown in fig. 5 to 6, the lower end of the pilot valve body 21 is provided with a bottom cap 27, a lower valve flap 25 is disposed in the hollow flow passage 26 above the bottom cap 27, the lower valve flap 25 is a block structure movable in the hollow flow passage 26 and spaced from the upper valve flap 24, and the lower valve flap 25 forms a control chamber with variable volume with the bottom cap 27 at the lower end of the hollow flow passage 26 and the pilot valve body 21. The bottom cover 27 is provided with a communication through hole, the pressure intensity in the control cavity is changed by connecting other cavities so as to drive the vertical movement of the lower valve clack 25, the movement of the lower valve clack 25 can change the pressure intensity in the hollow flow passage 26, and therefore the position of the upper valve clack 24 is controlled, and the control and adjustment of the whole pilot valve 2 are realized.
A communication pipeline is provided between the pilot valve 2 and the main valve 1 in this embodiment, the pipeline structure is as shown in fig. 1, the inlet flow passage 12 is communicated with the upper chamber of the piston 17 through a pipeline, and a throttle valve 19 is provided on the communication pipeline. The upper chamber of the piston 17 communicates with the inlet passage 22 via a conduit. The outlet passage 23 communicates with the outlet flow passage 13 through a pipe. The control chamber is connected to the outlet channel 13 via a conduit, i.e. substantially no flow medium is generated in the conduit between the control chamber and the outlet channel 13, and only as a pressure conducting structure.
The function to be realized in this embodiment is that the water pressure of the outlet flow path 13 should be maintained at a set value regardless of the change in the water pressure of the inlet flow path 12, and in order to realize this function, the opening degree of the main valve flap 14 needs to be comprehensively controlled. The force applied to the main valve flap 14 during use is shown in FIG. 2, where P is1For inlet channel 12 water pressure, P2Is the outlet flow passage 13 and the lower chamber water pressure, P, of the piston 173Is the water pressure of the upper chamber of the piston 17, S1Is the cross-sectional area, S, of the end of the main valve flap 14 remote from the valve stem 152Is a piston17 cross-sectional area of the axial end, thus:
the main valve flap 14 being subjected to upward hydraulic thrust F1＝P1*S1，
The main valve flap 14 being subjected to a downward hydraulic thrust F2＝P2*S1，
Piston 17 is subjected to upward hydraulic thrust F3＝P2*S2，
The piston 17 is subjected to a downward hydraulic thrust F4＝P3*S2；
Therefore, if the upward direction is positive, the combined force of the main valve flap 14 and the piston 17 is:
F＝F1-F2+F3-F4
＝P1*S1-P2*S1+P2*S2-P3*S2
＝(P1-P2)S1-(P3-P2)S2
wherein S is1<S2(ii) a If F>0, the main valve 1 opening will decrease; if F<0, the main valve 1 opening will increase.
The specific control measures of this embodiment are: a. when the pressure in the outlet flow passage 12 is lower than the set pressure of the pilot valve 2 (i.e. the water pressure in the hollow flow passage 26 cannot overcome the elastic force of the spring 210, and the upper valve flap 24 blocks the inlet passage 22), the pilot valve 2 is in a closed state, and at this time, part of the water flow enters the upper chamber of the piston 17 from the inlet flow passage 12 through the throttle 19 (no flow, only pressure conduction), so the water pressure in the upper chamber of the piston 17 should be equal to the water pressure in the inlet flow passage 12, i.e. P3＝P1Then, the main valve flap 14 is stressed:
F＝(P1-P2)S1-(P3-P2)S2
＝(P1-P2)(S1-S2)
and the water pressure of the inlet flow path 12 must be P which is greater than the water pressure of the outlet flow path 131>P2，S1<S2So that the force F exerted on the main valve flap 14 at this time is calculated<0, the piston 17 and the main valve flap 14 are forced downward, the opening of the main valve 1 increases, and the pressure in the outlet flow passage 13 rises.
b. When the pressure of the outlet channel 13 is higher than the set pressure of the pilot valve 2, the pilot valve 2 is in an open state (i.e. the water pressure in the hollow channel 26 overcomes the elastic force of the spring 210, and the upper valve flap 24 moves upward to open the inlet channel 22), at this time, part of the water flow enters the upper chamber of the piston 17 from the inlet channel 12 through the throttle valve 19, and at the same time, the upper chamber of the piston 17 is also connected with the inlet channel 22, at this time, a clear passage is formed, the water flow passes through the throttle valve 19 from the inlet channel 12 to enter the upper chamber of the piston 17 and then flows into the inlet channel 22, the water flow in the inlet channel 22 enters the outlet channel 23 through the hollow channel 26, and finally flows into the outlet channel 13, the upper chamber of the piston 17, the hollow channel 26, and the outlet channel 13 form a passage, so that the water pressure in3＝P2However, since the flow rate is restricted by the throttle valve 19, the water pressure between the inlet flow passage 12 and the upper chamber of the piston 17 is not equal, and the force applied to the main valve flap 14 in this case is calculated according to the above formula:
F＝(P1-P2)S1-(P3-P2)S2
＝(P1-P2)S1
while the water pressure in the inlet channel 12 must be greater than the water pressure P in the outlet channel 131>P2So that the force F exerted on the main valve flap 14 at this time is calculated>0, the piston 17 and the main valve flap 14 are forced upward, the opening of the main valve 1 decreases, and the water pressure in the outlet flow passage 13 decreases.
During actual operation, P3Will be at P2To P1The pressure of the outlet flow channel 13 tends to be stable, and the outlet pressure value is equal to the preset pressure of the spring 210 of the pilot valve 2, so that the hydraulic automatic control of the opening degree of the main valve 1 and the stability of the outlet pressure are realized.
When the outlet pressure of the main valve 1 needs to be changed, the adjusting screw 28 of the pilot valve 2 can be adjusted to change the preset pressure of the spring 210, so as to control the outlet pressure of the main valve 1.
A sealing ring 212 is arranged between the circumferential side walls of the upper and lower valve flaps 24, 25 and the hollow flow channel 26.
As shown in fig. 1, the vertical direction of the present embodiment refers to the up-down direction in fig. 1.
The foregoing shows and describes the general principles, essential 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, which are given by way of illustration of the principles of the present invention, and that various changes and modifications may be made without departing from the spirit and scope of the invention as defined by the appended claims. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims (10)

1. A high pressure difference water control piston type pressure reducing valve comprises a main valve (1); the main valve (1) comprises a main valve body (11); the main valve body (11) is a hollow cavity with an inlet flow passage (12) and an outlet flow passage (13), and a main valve clack (14) for controlling the opening degree of the flow passage is arranged in the main valve body (1); the main valve clack (14) is fixedly connected with a piston (17) in a piston cylinder (16) on the main valve body (11) through a valve rod (15); the lower chamber of the piston (17) is communicated with the outlet flow passage (13),
the method is characterized in that: the device also comprises a pilot valve (2); the pilot valve (2) comprises a pilot valve body (21); the pilot valve body (21) is a hollow cavity with an inlet channel (22) and an outlet channel (23); the inlet channel (22) is communicated with the upper chamber of the piston (17); the outlet channel (23) is communicated with the outlet flow channel (13); the upper chamber of the piston (17) is communicated with the inlet flow passage (12); and a control structure which closes the pilot valve (2) when the pressure of the outlet flow channel (13) is less than the set pressure so as to increase the opening degree of the main valve clack (14) and opens the pilot valve (2) when the pressure of the outlet flow channel (13) is greater than the set pressure so as to reduce the opening degree of the main valve clack (14) is arranged in the pilot valve body (21).
2. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: the control structure comprises an upper flap (24); a hollow flow passage (26) communicated with the inlet channel (22) and the outlet channel (23) is arranged in the pilot valve body (21); the upper valve clack (24) is a block structure which can move in the hollow flow passage (26) to control opening and closing, and a pressure adjusting structure used for adjusting water pressure in the hollow flow passage (26) is arranged in the hollow flow passage (26) below the upper valve clack (24).
3. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 2, wherein: the pressure regulating structure comprises a lower valve flap (25); the lower valve clack (25) is a block structure which can move in the hollow flow passage (26) and is arranged at intervals with the upper valve clack (24), and the lower valve clack (25), a bottom cover (27) at the lower end of the hollow flow passage (26) and the pilot valve body (21) form a control chamber with variable volume; the control chamber is in communication with the outlet flow passage (13).
4. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 2 or 3, wherein: and a pressure setting structure for adjusting the set pressure is arranged on the pilot valve body (21) above the upper valve clack (24).
5. The high differential pressure, water controlled piston type pressure reducing valve as defined in claim 4, wherein: the pressure setting structure comprises an adjusting screw (28), a spring seat (29) and a spring (210); one end of the adjusting screw (28) penetrates through a valve cover (211) at the upper end of the pilot valve body (21) and is fixedly connected with a spring seat (29) in the pilot valve body (21); one end of the spring (210) is fixed on the spring seat (29), and the other end is connected with the upper valve clack (24).
6. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: the main valve clack (14) is a hollow squirrel cage structure fixed at the end part of the valve rod (15), and a plurality of overflowing slotted holes are formed in the circumferential side wall of the main valve clack (14).
7. The high differential pressure, water controlled piston type pressure reducing valve as defined in claim 6, wherein: the circumferential side wall of the main valve clack (14) is provided with a plurality of strip-shaped through holes (18) which are uniformly arranged at intervals along the circumferential direction.
8. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 6 or 7, wherein: the cross-sectional area of one end of the main valve flap (14) far away from the valve rod (15) is smaller than that of the axial end of the piston (17).
9. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: and a throttle valve (19) is arranged on a communication pipeline between the inlet flow channel (12) and the upper chamber of the piston (17).
10. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 3, wherein: and a sealing ring (212) is arranged between the circumferential side walls of the upper valve clack (24) and the lower valve clack (25) and the hollow flow channel (26).
CN201911135864.3A 2019-11-19 2019-11-19 High-pressure-difference water-control piston type pressure reducing valve Pending CN111043365A (en)

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CN201911135864.3A CN111043365A (en) 2019-11-19 2019-11-19 High-pressure-difference water-control piston type pressure reducing valve

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Application Number Priority Date Filing Date Title
CN201911135864.3A CN111043365A (en) 2019-11-19 2019-11-19 High-pressure-difference water-control piston type pressure reducing valve

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112618921A (en) * 2020-12-23 2021-04-09 四川大学华西医院 Three-cavity two-bag tube for dynamically monitoring pressure of air bag based on flexible sensing material
CN113028127A (en) * 2021-05-31 2021-06-25 沈阳航天新光集团有限公司 Gas cavity volume adjustable structure of non-mechanical gas pressure reducer
CN113431934A (en) * 2021-07-28 2021-09-24 吴江市东吴机械有限责任公司 Pilot operated safety valve
CN117469447A (en) * 2023-12-28 2024-01-30 斯丹德汽车系统（苏州）有限公司 Pressure limiting valve and output stability control method thereof

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112618921A (en) * 2020-12-23 2021-04-09 四川大学华西医院 Three-cavity two-bag tube for dynamically monitoring pressure of air bag based on flexible sensing material
CN113028127A (en) * 2021-05-31 2021-06-25 沈阳航天新光集团有限公司 Gas cavity volume adjustable structure of non-mechanical gas pressure reducer
CN113431934A (en) * 2021-07-28 2021-09-24 吴江市东吴机械有限责任公司 Pilot operated safety valve
CN113431934B (en) * 2021-07-28 2023-01-06 吴江市东吴机械有限责任公司 Pilot operated safety valve
CN117469447A (en) * 2023-12-28 2024-01-30 斯丹德汽车系统（苏州）有限公司 Pressure limiting valve and output stability control method thereof
CN117469447B (en) * 2023-12-28 2024-04-16 斯丹德汽车系统（苏州）有限公司 Pressure limiting valve and output stability control method thereof

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