CN215334765U - Pressure regulating controller with four-stage throttling seal - Google Patents

Abstract

The utility model discloses a pressure regulating controller with four-stage throttling sealing, and relates to the technical field of pressure regulating and stabilizing devices. The utility model designs a four-stage throttling sealing structure, two-stage throttling sealing is respectively arranged in a director and a voltage stabilizer of a voltage regulation controller, the air inlet end of the voltage stabilizer is communicated to the lower cavity of a diaphragm of a main voltage regulator and throttled by a four-stage valve clack during working, the flow speed is reasonably controlled in an internal passage, and the valve clack is favorably protected from being scoured and damaged under a high-pressure working condition. When the valve is closed, the four-stage valve clacks are closed at the same time, and the medium is prevented from leaking to the downstream through the command control system. When the pressure-stabilizing valve is opened, the pressure-stabilizing secondary valve clack and the commanding secondary valve clack are opened first, and the pressure-stabilizing primary valve clack and the commanding primary valve clack are opened again; the problem that under high pressure, the valve clack is easily washed and damaged, influences the throttling effect, reduces the pressure regulator precision and can not be tightly sealed after the pressure regulator is closed can be effectively solved.

Description

Pressure regulating controller with four-stage throttling seal

Technical Field

The utility model relates to a gas pressure regulating and stabilizing device, belongs to the technical field of automatic regulation of gas transmission pressure and stable output gas pressure, and particularly relates to a pressure regulating controller with four-stage throttling seal, which is particularly suitable for being installed and used on gas transmission pipelines of natural gas, liquefied gas, coal gas, CNG pressure regulating stations and the like.

Background

As people know, with the rapid development of petroleum and natural gas industry and urbanization construction in China, the construction process of urban gas transmission and distribution pipe network facilities is greatly promoted. According to investigation, at present, a relatively perfect gas transmission and distribution pipe network system is basically built in most cities, and the system plays a positive role in promoting 'coal gas changing' environmental protection engineering in the industrial production industry and the life of residents.

For the gas transmission work governing department, providing stable-pressure gas products for users is an important technical quality index for ensuring 'safe gas supply and gas utilization'. However, in the process of gas transmission and distribution, gas transmission pipe network equipment is inevitably influenced by objective factors such as an upper end gas source and lower end gas consumption change, so that gas transmission pressure fluctuates, and when the fluctuation range of the gas pressure exceeds the design allowable range, normal gas use of downstream users is influenced, and even production safety accidents are easily caused. In order to solve the problem, the most commonly used technical measure in the existing gas transmission industry is to install a set of pressure regulating control device on a gas transmission pipeline, and the pressure regulating working principle is as follows: the pressure in the pipe is fed back to the pressure regulating control device, and the pressure regulating control device regulates and controls the pressure fluctuation value of the output gas to be within an allowable range and enables the output gas to tend to be stable.

In order to ensure the stability and safety of downstream gas utilization, the pressure regulator needs to have higher regulation precision, stability of long-term work and can realize tight sealing after being closed. At present, pressure regulators below 4.0MPa are mainly produced at home, and pressure regulators of 4.0-10.0 MPa are produced by individual manufacturers, but due to the fact that innovative structural design is not available, adjustment accuracy under high pressure is not ideal, failure rate is high, and great trouble is caused for safe and stable operation of a natural gas transmission and distribution station. At present, the high-voltage pressure regulator mainly depends on import, and has the disadvantages of high price, long delivery period and high maintenance cost. And the director and the voltage stabilizer of the natural gas transmission and distribution station voltage regulator are provided with only one valve clack, namely, the valve clack is used as throttling and also used as closing seal. Under high pressure, the valve clack is easily washed and damaged, so that the throttling effect is influenced, the precision of the pressure regulator is reduced, and the valve clack cannot be tightly sealed after the pressure regulator is closed.

SUMMERY OF THE UTILITY MODEL

In order to overcome the defects and shortcomings in the prior art, the utility model provides the pressure regulating controller with the four-stage throttling seal, and aims to solve the problems that the valve clack of the pressure regulating controller in the prior art is easy to be washed and damaged under high pressure, the throttling effect is influenced, the precision of the pressure regulator is reduced, and the valve clack cannot be tightly sealed after the pressure regulator is closed. The four-stage throttling sealing structure is designed on the pressure regulating controller, two-stage throttling sealing is respectively arranged in the commander and the pressure stabilizer of the pressure regulating controller, the air inlet end of the pressure stabilizer is communicated to the lower cavity of the diaphragm of the main pressure regulator and throttled by the four-stage valve clack during working, the flow speed is reasonably controlled in an internal passage, and the valve clack is protected from being scoured and damaged under a high-pressure working condition. When the valve is closed, the four-stage valve clacks are closed at the same time, and the medium is prevented from leaking to the downstream through the command control system. The problem that under high pressure, the valve clack is easily washed and damaged, influences the throttling effect, reduces the pressure regulator precision and can not be tightly sealed after the pressure regulator is closed can be effectively solved.

In order to solve the problems in the prior art, the utility model is realized by the following technical scheme:

a pressure regulating controller with four-stage throttling sealing comprises a command valve and a pressure stabilizing valve, wherein the pressure stabilizing valve comprises a pressure stabilizing regulating spring assembly, a pressure stabilizing membrane assembly, a pressure stabilizing valve body, a pressure stabilizing primary valve clack and a pressure stabilizing secondary valve clack; a pressure stabilizing primary throttling cavity, a pressure stabilizing secondary throttling cavity and a pressure stabilizing tertiary throttling cavity are arranged in the pressure stabilizing valve, and the pressure stabilizing primary throttling cavity, the pressure stabilizing secondary throttling cavity and the pressure stabilizing tertiary throttling cavity are communicated in sequence; the pressure stabilizing primary throttling cavity is used for controlling the on-off of a communicating hole between the pressure stabilizing primary throttling cavity and the pressure stabilizing secondary throttling cavity; the pressure stabilizing secondary throttling cavity is used for controlling the on-off of a communicating hole between the pressure stabilizing secondary throttling cavity and the pressure stabilizing tertiary throttling cavity; the pressure stabilizing primary valve clack is connected with a pressure stabilizing primary valve rod, the pressure stabilizing primary valve rod extends towards the pressure stabilizing secondary throttling cavity to be contacted with the pressure stabilizing secondary valve clack, and when the pressure stabilizing primary valve clack and the pressure stabilizing secondary valve clack are both in a closed state, a set gap is formed between the top end of the pressure stabilizing primary valve rod and the bottom of the pressure stabilizing secondary valve clack; the pressure stabilizing secondary valve clack is connected with a pressure stabilizing secondary valve rod, and the upper end of the pressure stabilizing secondary valve rod extends to the lower cavity of the pressure stabilizing diaphragm and is connected with the pressure stabilizing diaphragm component; the pressure stabilizing adjusting spring assembly is arranged in the pressure stabilizing diaphragm upper cavity and connected with the pressure stabilizing diaphragm assembly;

the commanding valve comprises a commanding and adjusting spring assembly, a commanding piston assembly, a commanding valve body, a commanding primary valve clack and a commanding secondary valve clack, a commanding primary throttling cavity, a commanding secondary throttling cavity, a commanding tertiary throttling cavity, a commanding primary throttling cavity, a commanding secondary throttling cavity and a commanding tertiary throttling cavity are arranged in the commanding valve and are communicated in sequence; the command primary throttling cavity is used for controlling the on-off of a communication hole between the command primary throttling cavity and the command secondary throttling cavity; the commanding secondary throttling cavity is used for controlling the on-off of a communication hole between the commanding secondary throttling cavity and the commanding tertiary throttling cavity; the commanding first-stage valve clack is connected with a commanding first-stage valve rod, the commanding first-stage valve rod extends towards the commanding second-stage throttling cavity and is in contact with the commanding second-stage valve clack, and a set gap is formed between the top end of the commanding first-stage valve rod and the bottom of the commanding second-stage valve clack when the commanding first-stage valve clack and the commanding second-stage valve clack are both in a closed state; the commanding second-stage valve clack is connected with a commanding second-stage valve rod, the upper end of the commanding second-stage valve rod is connected with a commanding piston assembly, the commanding second-stage valve rod is connected with a commanding valve body in a sealing mode, and the commanding piston assembly is arranged in the commanding valve body in a sliding mode to form a piston lower cavity; the commanding and adjusting spring assembly is arranged on the piston upper cavity and is connected with the commanding piston assembly;

the pressure-stabilizing primary throttling cavity is provided with a connecting joint connected with the signal pipe, and the connecting joint is provided with a pressure-stabilizing damping hole; the upper pressure stabilizing diaphragm cavity of the pressure stabilizing valve and the lower piston cavity of the command valve are both communicated with the pressure of the downstream pipeline of the pressure regulator; the pressure stabilizing third-stage throttling cavity of the pressure stabilizing valve is communicated with the commanding first-stage throttling cavity of the command valve; and the commanding valve body is provided with a connecting interface I communicated with the commanding tertiary throttling cavity.

It works as follows: the inlet air of the pressure stabilizing valve is led out from an upstream pipeline of an inlet of a main valve by a signal pipe and enters a pressure stabilizing primary throttling cavity from a pressure stabilizing damping hole on a connecting joint, if the pressure of the pipeline on the inlet of the main valve is P1, the inlet pressure P1 forms a pressure stabilizing primary throttling pressure P3 which is lower than the inlet pressure P1 in the pressure stabilizing primary throttling cavity after being throttled by the pressure stabilizing damping hole of the connecting joint; the pressure stabilizing primary throttle valve is throttled by the pressure stabilizing secondary throttle cavity to form a pressure stabilizing secondary throttle pressure P4; the pressure stabilizing secondary valve clack enters the pressure stabilizing tertiary throttling cavity after throttling to form pressure stabilizing tertiary throttling pressure P5. Part of the pressure stabilizing tertiary throttling pressure P5 enters the lower cavity of the pressure stabilizing diaphragm to form upward force acting on the pressure stabilizing diaphragm; the other part enters a command primary throttling cavity of the command valve through the pressure stabilizing valve body and a process hole on the command valve body or through a connecting pipe; the command secondary throttle pressure P6 is formed by the command primary valve clack entering the command secondary throttle cavity; a command tertiary throttle pressure P7 is formed by the command tertiary throttle pressure P7 loaded to the lower cavity of the main valve diaphragm through a signal tube after the command secondary valve clack enters the command tertiary throttle cavity, and an upward force acting on the main valve diaphragm is formed.

The pipeline pressure P2 at the downstream of the main valve outlet is introduced into the upper cavity of the main valve diaphragm, the upper cavity of the pressure stabilizing diaphragm and the lower cavity of the piston by the signal pipe. The upper cavity of the main valve diaphragm acts on the main valve diaphragm to form a downward force, the upper cavity of the pressure stabilizing diaphragm acts on the pressure stabilizing diaphragm to form a downward force, and the lower cavity of the piston acts on the lower end of the piston to form an upward force.

The main valve of the pressure regulator is used for reducing the inlet pressure P1 and then delivering the pressure to the downstream, the downstream pressure is led by a signal pipe and fed back to a command valve, and the outlet pressure P2 is set by a command spring adjusting component of the command valve. During operation, the outlet pressure deviates from the set pressure P2, and the commanding piston assembly is driven to move to change the opening of the commanding first-stage valve clack and the commanding second-stage valve clack on the commanding valve, so that the pressure P7 finally loaded to the lower cavity of the main valve diaphragm is changed, the main valve diaphragm is driven to move, the main valve spool is driven to move, and the main valve outlet pressure of the pressure regulator is stabilized at the set pressure P2.

In order to better achieve the object of the utility model, the utility model also has the following technical characteristics:

and a commanding damping hole for communicating the piston lower cavity with the connecting interface I is arranged on the commanding valve body to form a slow release air channel structure. Compared with the prior art, the damping micropores which are arranged on the valve rod of the main valve and are used for communicating the upper cavity of the main valve diaphragm with the lower cavity of the main valve diaphragm are arranged on the command valve body, and the structural design can improve the pressure regulating response efficiency and precision of the pressure regulating controller.

The diameter of a pressure stabilizing damping hole in a connecting joint on the pressure stabilizing valve is larger than that of the command damping hole. The diameters of the pressure stabilizing damping hole on the pressure stabilizing valve and the command damping hole on the command valve are designed by matching the pressure difference between the inlet pressure P1 and the outlet pressure P2 of the main valve of the pressure regulator. The larger the pressure difference between the P1 and the P2 is, the relatively smaller the diameter of the pressure stabilizing damping hole is, and the relatively larger the diameter of the command damping hole is; the differential value between the pressure P5 entering the lower cavity of the pressure stabilizing valve diaphragm and the pressure P2 above the upper cavity of the pressure stabilizing valve diaphragm is relatively small, the differential value between the pressure P7 entering the lower cavity of the main valve diaphragm of the pressure regulator and the pressure P2 above the main valve diaphragm is relatively small, and the problem that the pressure regulator fails due to the fact that the main valve diaphragm is damaged due to overlarge differential pressure is avoided. No matter how the diameter of the pressure stabilizing damping hole is matched with that of the command damping hole, the diameter of the pressure stabilizing damping hole is always larger than that of the command damping hole.

The pressure difference between the two ends of the inlet and the outlet of the slow-release air passage formed by the damping hole is controlled and commanded to be 0.05MPa-0.10 MPa. The trial shows that: the optimized design for controlling the damping pressure drop of the command damping hole to be between 0.05MPa and 0.10MPa has an excellent flow-discharging slow-release effect, can effectively and slowly release the pressure transient amplitude of the pressure regulating air medium in the upper cavity of the main valve diaphragm and the lower cavity of the main valve diaphragm, can greatly improve the pressure change smoothness and stability of the pressure regulating air medium in the lower cavity of the main valve diaphragm, and improves the pressure regulating precision of the pressure regulator and the pressure stabilizing capacity of output air pressure.

The command valve and the pressure stabilizing valve are assembled together through screws, balance holes are formed in the command valve body and the pressure stabilizing valve body, and an upper pressure stabilizing membrane cavity of the pressure stabilizing valve is communicated with a lower piston cavity of the command valve.

And a command valve body of the command valve is provided with a connecting interface II communicated with the lower cavity of the piston.

And a pressure stabilizing valve body of the pressure stabilizing valve is provided with a connecting interface III communicated with the upper cavity of the pressure stabilizing membrane.

The pressure stabilizing valve body comprises a lower pressure stabilizing valve body, a middle pressure stabilizing valve body and an upper pressure stabilizing valve body, and a connecting joint is assembled on the lower pressure stabilizing valve body and forms a pressure stabilizing primary throttling cavity with the lower pressure stabilizing valve body; the pressure stabilizing lower valve body is assembled on the pressure stabilizing middle valve body, a pressure stabilizing secondary throttling cavity is formed between the pressure stabilizing lower valve body and the pressure stabilizing middle valve body, and the pressure stabilizing middle valve body is provided with the pressure stabilizing tertiary throttling cavity; the pressure stabilizing membrane component is assembled between the upper pressure stabilizing valve body and the middle pressure stabilizing valve body, and divides a cavity between the middle pressure stabilizing valve body and the upper pressure stabilizing valve body into an upper pressure stabilizing membrane cavity and a lower pressure stabilizing membrane cavity.

The commanding valve body comprises a commanding lower valve body, a commanding middle valve body and a commanding upper valve body, an end cover is assembled on the commanding lower valve body, and a commanding primary throttling cavity is formed between the end cover and the commanding lower valve body; the commanding lower valve body is assembled on the commanding valve body, and a commanding secondary throttling cavity is formed between the commanding lower valve body and the commanding valve body; a commanding third-stage throttling cavity is formed in the commanding valve body; the commanding piston assembly is assembled on the commanding valve body in a sliding mode, the commanding adjusting spring assembly is assembled between the commanding valve body and the commanding upper valve body, the upper end of the commanding adjusting spring assembly is connected with the commanding upper valve body, and the lower end of the commanding adjusting spring assembly acts on the commanding piston assembly.

Compared with the prior art, the beneficial technical effects brought by the utility model are as follows:

1. the utility model innovatively designs a command valve and a pressure stabilizing valve assembly respectively provided with two stages of throttling sealing valve clacks, and the command valve and the pressure stabilizing valve assembly achieve high-precision adjustment, zero-leakage sealing and long-term stable operation under the 10MPa high-pressure working condition through practical use tests.

2. In the utility model, the pressure stabilizing valve is provided with a primary valve clack and a secondary valve clack, when the pressure stabilizing valve is closed, a certain gap exists between the pressure stabilizing primary valve rod and the pressure stabilizing secondary valve clack, when the pressure stabilizing valve is opened, the pressure stabilizing secondary valve clack is firstly opened, and then the pressure stabilizing primary valve clack is opened. At the moment, the opening degree of the pressure stabilizing secondary valve clack is larger than that of the pressure stabilizing primary valve clack. The pressure stabilizing first-stage valve clack is used as a main throttle clack of the pressure stabilizing valve, the pressure stabilizing second-stage valve clack is used as an auxiliary throttle clack of the pressure stabilizing valve, and under the high-pressure working condition, the pressure stabilizing second-stage valve clack can achieve the tight sealing effect even if the pressure stabilizing first-stage valve clack is damaged.

3. In the utility model, the commanding valve is provided with a first-stage valve clack and a second-stage valve clack. When the valve is closed, a certain gap exists between the commanding first-stage valve rod and the commanding second-stage valve clack. When the valve is opened, the second-stage valve clack is commanded to be opened first, and the first-stage valve clack is commanded to be opened subsequently. At the moment, the opening degree of the commanding second-stage valve clack is larger than that of the commanding first-stage valve clack, the commanding first-stage valve clack is used as a main throttle clack of the commanding valve, the commanding second-stage valve clack is used as an auxiliary throttle clack of the commanding valve, and under the high-pressure working condition, the commanding second-stage valve clack can achieve a tight sealing effect even if the commanding first-stage valve clack is damaged.

4. In the utility model, the pressure regulating command controller composed of the command valve and the pressure stabilizing valve leads the gas inlet end of the pressure stabilizing valve to the lower cavity of the main valve membrane and throttles by the four-stage valve clack when in work, the flow speed is reasonably controlled in the internal passage, and the valve clack is protected from being scoured and damaged under the high-pressure working condition. When the valve is closed, the 4-stage valve is closed at the same time, and the medium is prevented from leaking to the downstream through the command control system.

5. In the utility model, the pressure stabilizing membrane upper cavity of the pressure stabilizing valve is led into the pipeline pressure P2 at the outlet of the pressure regulator, the pressure stabilizing membrane lower cavity of the pressure stabilizing valve is the three-stage throttling pressure P5 after three times of throttling, even under the high pressure working condition, the pressure stabilizing membrane of the pressure stabilizing valve is stressed into pressure difference, the pressure stabilizing membrane adopts a rubber membrane, and the pressure stabilizing valve is more sensitive to regulation. The commanding valve is designed into a piston structure and can bear higher outlet pressure.

6. In the utility model, the command valve and the pressure stabilizing valve can be adjusted by adopting the adjusting spring assembly, and the pressure stabilizing adjusting spring assembly of the pressure stabilizing valve is matched with the command adjusting spring assembly of the command valve, so that the fine adjustment of the outlet pressure can be realized, the adjustment is more sensitive and the precision is higher.

Drawings

FIG. 1 is a schematic diagram of a main sectional structure of a voltage regulator controller according to the present invention;

FIG. 2 is a schematic main sectional view of a pressure maintaining valve of the present invention;

FIG. 3 is a schematic view of a main section of a command valve of the present invention;

FIG. 4 is a schematic cross-sectional view of a pressure regulator formed by a pressure regulator controller coupled to a main valve according to the present invention;

reference numerals: 100. a pressure stabilizing valve 200, a command valve 300, a main valve 400 and a signal tube;

101. a pressure stabilizing adjusting spring assembly 102, a pressure stabilizing diaphragm assembly 103, a pressure stabilizing valve body 104, a pressure stabilizing primary valve clack 105, a pressure stabilizing secondary valve clack 106, a pressure stabilizing primary throttling cavity 107, a pressure stabilizing secondary throttling cavity 108, a pressure stabilizing tertiary throttling cavity 109, a pressure stabilizing primary valve rod 110, a pressure stabilizing secondary valve rod 111, a pressure stabilizing diaphragm lower cavity 112, a pressure stabilizing diaphragm upper cavity 113, a connecting joint 114, a pressure stabilizing damping hole 115, a pressure stabilizing lower valve body 116, a pressure stabilizing middle valve body 117, a pressure stabilizing upper valve body 118 and a connecting joint III;

201. a command adjusting spring assembly 202, a command piston assembly 203, a command valve body 204, a command first-stage valve clack 205, a command second-stage valve clack 206, a command first-stage throttling cavity 207, a command second-stage throttling cavity 208, a command third-stage throttling cavity 209, a command first-stage valve rod 210, a command second-stage valve rod 211, a piston lower cavity 212, a connection interface I, 213, a command damping hole 214, a balance hole 215, a connection interface II, 216, a command lower valve body 217, a command middle valve body 218, a command upper valve body 219 and an end cover;

301. a main valve diaphragm upper chamber 302, a main valve diaphragm lower chamber 303, a main valve diaphragm assembly 304, a main valve stem 305, a main valve spool 306, a main valve sleeve 307, a choke.

Detailed Description

The technical scheme of the utility model is further elaborated in the following by combining the drawings in the specification. Here, the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.

It should be noted that when an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present, unless the context clearly dictates otherwise.

Referring to the attached figure 4 in the specification, a pressure regulator structure is shown, and comprises a pressure regulating controller and a main valve 300, wherein the pressure regulator is mainly used for a natural gas transmission and distribution station, and is used for automatically regulating the pressure of incoming high-pressure gas at the upstream through the pressure regulator and then conveying the incoming high-pressure gas to a downstream user, and is a main device of the natural gas transmission and distribution station. Wherein the main valve 300 is used for regulating the gas medium pressure on the transmission and distribution pipeline; the pressure regulating controller is a pressure regulating command controller system consisting of a command valve 200 and a pressure stabilizing valve 100, and controls the opening and closing and the opening of a main valve 300 so as to control the gas medium pressure of the transmission and distribution pipeline.

The embodiment provides a command valve 200 and a pressure stabilizing valve 100 assembly respectively provided with two stages of throttling sealing valve clacks, and the practical use test shows that the high-precision adjustment, zero-leakage sealing and long-term stable operation are achieved under the 10MPa high-pressure working condition.

Referring to the specification, as shown in the attached fig. 1, 2 and 3, the pressure regulating controller with the four-stage throttling seal comprises a command valve 200 and a pressure stabilizing valve 100, wherein the pressure stabilizing valve 100 comprises a pressure stabilizing and regulating spring assembly 101, a pressure stabilizing membrane assembly 102, a pressure stabilizing valve body 103, a pressure stabilizing primary valve clack 104 and a pressure stabilizing secondary valve clack 105; a pressure stabilizing primary throttling cavity 106, a pressure stabilizing secondary throttling cavity 107 and a pressure stabilizing tertiary throttling cavity 108 are arranged in the pressure stabilizing valve 100, and the pressure stabilizing primary throttling cavity 106, the pressure stabilizing secondary throttling cavity 107 and the pressure stabilizing tertiary throttling cavity 108 are communicated in sequence; the pressure stabilizing primary valve clack 104 is arranged in the pressure stabilizing primary throttling cavity 106 and is used for controlling the connection and disconnection of a communication hole between the pressure stabilizing primary throttling cavity 106 and the pressure stabilizing secondary throttling cavity 107; the pressure stabilizing secondary throttling clack 105 is arranged in the pressure stabilizing secondary throttling cavity 107 and is used for controlling the connection and disconnection of a communicating hole between the pressure stabilizing secondary throttling cavity 107 and the pressure stabilizing tertiary throttling cavity 108; the pressure stabilizing primary valve clack 104 is connected with a pressure stabilizing primary valve rod 109, the pressure stabilizing primary valve rod 109 extends towards the pressure stabilizing secondary throttling cavity 107 to be contacted with the pressure stabilizing secondary valve clack 105, and when the pressure stabilizing primary valve clack 104 and the pressure stabilizing secondary valve clack 105 are both in a closed state, a set gap is formed between the top end of the pressure stabilizing primary valve rod 109 and the bottom of the pressure stabilizing secondary valve clack 105; the pressure stabilizing secondary valve clack 105 is connected with a pressure stabilizing secondary valve rod 110, and the upper end of the pressure stabilizing secondary valve rod 110 extends to a lower 111 cavity of the pressure stabilizing diaphragm and is connected with the pressure stabilizing diaphragm component 102; the pressure stabilizing adjusting spring assembly 101 is arranged in the pressure stabilizing membrane upper cavity 112 and is connected with the pressure stabilizing membrane assembly 102;

the commanding valve 200 comprises a commanding and adjusting spring assembly 201, a commanding piston assembly 202, a commanding valve body 203, a commanding primary valve clack 204 and a commanding secondary valve clack 205, wherein a commanding primary throttling cavity 206, a commanding secondary throttling cavity 207, a commanding tertiary throttling cavity 208, a commanding primary throttling cavity 206, a commanding secondary throttling cavity 207 and a commanding tertiary throttling cavity 208 are sequentially communicated; the command primary throttling valve 204 is assembled in the command primary throttling cavity 206 and is used for controlling the connection and disconnection of a communication hole between the command primary throttling cavity 206 and the command secondary throttling cavity 207; the commanding secondary throttle valve 205 is assembled in the commanding secondary throttle chamber 207 and is used for controlling the connection and disconnection of a communication hole between the commanding secondary throttle chamber 207 and the commanding tertiary throttle chamber 208; the commanding primary valve clack 204 is connected with a commanding primary valve rod 209, the commanding primary valve rod 209 extends towards the commanding secondary throttling cavity 207 and is in contact with the commanding secondary valve clack 205, and when the commanding primary valve clack 204 and the commanding secondary valve clack 205 are both in a closed state, a set gap is formed between the top end of the commanding primary valve rod 209 and the bottom of the commanding secondary valve clack 205; the commanding secondary valve clack 205 is connected with a commanding secondary valve rod 210, the upper end of the commanding secondary valve rod 210 is connected with a commanding piston assembly 202, the commanding secondary valve rod 210 is connected with a commanding valve body 203 in a sealing manner, and the commanding piston assembly 202 is arranged in the commanding valve body 203 in a sliding manner to form a piston lower cavity 211; the commanding and adjusting spring assembly 201 is arranged on the piston upper cavity and is connected with the commanding piston assembly 202;

the pressure-stabilizing primary throttling cavity 106 is provided with a connecting joint 113 connected with the signal pipe 400, and the connecting joint 113 is provided with a pressure-stabilizing damping hole 114; the upper pressure stabilizing diaphragm cavity 112 of the pressure stabilizing valve 100 and the lower piston cavity 211 of the commanding valve 200 are communicated with the pressure of the pipeline at the downstream of the pressure regulator; the pressure stabilizing tertiary throttling cavity 108 of the pressure stabilizing valve 100 is communicated with the commanding primary throttling cavity 206 of the commanding valve 200; and a connecting interface I212 communicated with the commanding tertiary throttling cavity 208 is arranged on the commanding valve body 203.

It works as follows: the inlet air of the pressure stabilizing valve 100 is led out from the upstream pipeline of the inlet of the main valve 300 by a signal tube 400 and enters the pressure stabilizing primary throttling cavity 106 from the pressure stabilizing damping hole 114 on the connecting joint 113, if the pressure of the pipeline on the inlet of the main valve 300 is P1, the inlet pressure P1 forms a pressure stabilizing primary throttling pressure P3 which is lower than the inlet pressure P1 in the pressure stabilizing primary throttling cavity 106 after being throttled by the pressure stabilizing damping hole 114 of the connecting joint 113; the pressure stabilizing primary throttling valve clack 104 throttles the pressure and then enters a pressure stabilizing secondary throttling cavity 107 to form a pressure stabilizing secondary throttling pressure P4; the pressure stabilizing secondary throttle flap 105 throttles the pressure and enters the pressure stabilizing tertiary throttle cavity 108 to form the pressure stabilizing tertiary throttle pressure P5. Part of the pressure stabilizing tertiary throttle pressure P5 enters a lower 111 cavity of the pressure stabilizing diaphragm to form an upward force acting on the pressure stabilizing diaphragm; the other part enters a commanding primary throttling cavity 206 of the commanding valve 200 through fabrication holes on the pressure stabilizing valve body 103 and the commanding valve body 203 or through a connecting pipe; the pilot secondary throttling pressure P6 is formed by the pilot primary valve clack 204 entering the pilot secondary throttling cavity 207; a commanded tertiary throttle pressure P7 is generated by the commanded secondary flapper 205 entering the commanded tertiary throttle chamber 208, and the commanded tertiary throttle pressure P7 is applied to the main valve diaphragm lower chamber 302 through the signal tube 400, creating an upward force on the main valve 300 diaphragm.

The line pressure P2 downstream of the main valve 300 outlet is introduced by the signal pipe 400 into the main valve diaphragm upper chamber 301, the regulator diaphragm upper chamber 112 and the piston lower chamber 211. A downward force is generated by the main valve diaphragm upper chamber 301 acting on the main valve 300 diaphragm, a downward force is generated by the regulator diaphragm upper chamber 112 acting on the regulator diaphragm, and an upward force is generated by the piston lower chamber 211 acting on the piston lower end.

The main valve 300 of the pressure regulator reduces the inlet pressure P1 and transmits it downstream, and uses the signal pipe 400 to draw the downstream pressure and feed it back to the pilot valve 200, and the outlet pressure P2 is set by the pilot spring adjusting component of the pilot valve 200. During operation, the outlet pressure deviates from the set P2 pressure, which drives the commanding piston assembly 202 to move and thereby changes the opening of the commanding primary and secondary flaps 204 and 205 on the commanding valve 200, causing the pressure P7 ultimately applied to the main valve diaphragm lower chamber 302 to change, thereby driving the main valve 300 diaphragm to move and thereby moving the main valve spool 305, and stabilizing the outlet pressure of the main valve 300 of the pressure regulator at the set pressure P2.

Referring to the attached fig. 4 of the specification, the voltage regulator is shown to perform the voltage regulating and stabilizing operation as follows:

the gas transmission operation manager firstly performs setting operation according to the transportation, distribution and gas transmission management operation regulation: the pressure regulating and stabilizing spring assembly 101 and the command regulating spring assembly 201 are regulated to regulate the output air pressure in the output main pipe of the pressure regulator to a rated output pressure value. Leading the output air pressure of the main output pipe of the pressure regulator to the upper cavity 301 of the main valve diaphragm of the pressure regulator, the upper cavity 112 of the pressure stabilizing diaphragm of the pressure stabilizing valve 100 and the lower cavity of the piston cavity of the command valve 200; the pressure at the inlet end of the pressure regulator throttled by the pressure stabilizing valve 100 and the commanding valve 200 is introduced into the main valve diaphragm lower cavity 302, and at this time, the main valve 300 diaphragm of the main valve 300 of the pressure regulator is in a balanced position state under the combined action of the air pressure in the main valve diaphragm upper cavity 301 and the main valve diaphragm lower cavity 302; the commanding piston assembly 202, the commanding secondary valve clack 205 and the commanding primary valve clack 204 of the commanding valve 200 are in a balanced position state under the combined action of the commanding and adjusting spring assembly 201 and the air pressure in the piston lower cavity 211; the pressure stabilizing diaphragm assembly 102, the pressure stabilizing primary valve flap 104 and the pressure stabilizing secondary valve rod 110 of the pressure stabilizing valve 100 are in a balanced position state under the combined action of the pressure stabilizing adjusting spring assembly 101 and the pressure in the pressure stabilizing diaphragm lower 111 cavity.

When the output air pressure of the lower end of the main valve 300 of the pressure regulator is reduced due to the increase of the amount of air used by a downstream user, the pressure P2 introduced into the upper cavity 301 of the main valve diaphragm, the lower piston cavity 211 and the upper pressure stabilizing diaphragm cavity 112 is reduced, at this time, the balance of the piston assembly in the command valve 200 is broken, the command piston assembly 202 moves downwards under the push of the command adjusting spring assembly 201 and drives the command first-stage valve flap 204 and the command second-stage valve flap 205 to move downwards to increase the opening of the command throttling, namely, an increased pressure regulating signal is input into the lower main valve diaphragm cavity 302 from the command third-stage throttling cavity 208 through the signal pipe 400 and is loaded on the diaphragm of the main valve 300, namely, the P7 pressure value is increased; since P2 is lowered, the "increased pressure regulating signal" will push the main valve diaphragm assembly 303 to move upward and drive the main valve spool 305 to move upward through the main valve stem 304, and when the main valve spool 305 moves upward, the opening degree of the orifice 307 of the main valve sleeve 306 is increased, so as to increase the output flow pressure of the main valve 300 until the output pressure is stabilized and reaches the set rated output pressure value.

Specifically, it is to be noted that: the 'increased pressure regulating signal' input into the lower cavity 302 of the main valve diaphragm is that a signal tube 400 leads a pipeline pressure signal air source at the front end of the inlet of the main valve 300 into the pressure stabilizing valve 100, passes through the pressure stabilizing primary throttling cavity 106, the pressure stabilizing secondary throttling cavity 107 and the pressure stabilizing tertiary throttling cavity 108, and leads the commanding primary throttling cavity 206, the commanding secondary throttling cavity 207 to the commanding tertiary throttling cavity 208; the formed voltage regulating signal. In the above process, the pressure signal source of the pipeline at the front end of the inlet of the main valve 300 is subjected to five-stage throttling and pressure reduction to form a 'pressure regulating signal'. Furthermore, during the whole pressure regulating operation through the primary pressure-stabilizing throttling cavity 106, the secondary pressure-stabilizing throttling cavity 107, the tertiary pressure-stabilizing throttling cavity 108, the primary commanding throttling cavity 206, the secondary commanding throttling cavity 207 and the tertiary commanding throttling cavity 208, the increased pressure regulating signal is formed under the combined influence of the pressure drop toggle signal output after the pressure drop toggle signal is fed back to the main valve 300 of the commanding piston lower cavity 211 and the upper pressure-stabilizing diaphragm cavity 112. Although the pressure regulating signal input into the lower cavity 302 of the main valve diaphragm is "increased", the "credited pressure regulating signal" is formed by a compound pressure regulating and stabilizing structure formed by serially connecting the pressure stabilizing damping hole 114, the pressure stabilizing primary valve flap 104, the pressure stabilizing secondary valve flap 105, the commanding primary valve flap 204 and the commanding secondary valve flap 205 through one pressure stabilizing throttling, two pressure stabilizing throttling, three pressure stabilizing throttling, one pressure regulating throttling and two pressure regulating throttling once. When the pressure regulating and stabilizing function is performed in the lower cavity 302 of the main valve diaphragm, the pressure regulating and stabilizing device has excellent pressure change smoothness and stability. The trial shows that: high-precision adjustment, zero-leakage sealing and long-term stable operation are achieved under the high-pressure working condition of 10 MPa.

When the downstream pressure of the gas transmission line at the lower end of the main valve 300 of the pressure regulator is sharply reduced due to a pipe burst accident, the air pressure of the signal pipe 400 introduced into the commanding valve 200 and the pressure stabilizing valve 100 is also rapidly reduced, and at the moment, the commanding and adjusting spring assembly 201 and the pressure stabilizing and adjusting spring assembly 101 push the commanding first-stage valve clack 204, the commanding second-stage valve clack 205, the pressure stabilizing first-stage valve clack 104 and the pressure stabilizing second-stage valve clack 105 to move upwards to close the commanding valve 200 and the pressure stabilizing valve 100 to rapidly cut off a front pressure signal air source. At the same time, the main valve diaphragm assembly 303 also moves downward rapidly under the action of the pressure difference between the upper main valve diaphragm chamber 301 and the lower main valve diaphragm chamber 302, and drives the main valve spool 305 to move downward through the main valve stem 304 to close the orifice 307 of the main valve housing 306, so as to close the main valve 300 of the pressure regulator for safety protection.

On the contrary, when the output air pressure at the lower end of the main valve 300 of the pressure regulator rises due to the decrease of the amount of air used by the downstream user, the signal tube 400 feeds back the fluctuation signals of the pressure rise of the downstream pipeline of the main valve 300 to the main valve diaphragm upper chamber 301, the piston lower chamber 211 of the commanding valve 200 and the pressure regulating diaphragm upper chamber 112 of the pressure regulating valve 100 respectively, in the same way as above: the piston assembly of the command valve 200 moves upward under the pressure of the piston lower cavity 211, which means that the command first-stage valve flap 204 and the command second-stage valve flap 205 move upward under the push of the command adjusting spring assembly 201 to reduce the opening of the command throttle, that is, a "reduced pressure regulating signal" is input into the main valve diaphragm lower cavity 302 from the command third-stage throttle cavity 208 and the signal pipe 400, because the pressure introduced into the main valve diaphragm upper cavity 301 is increased, the pressure in the main valve diaphragm lower cavity 302 is decreased, the main valve diaphragm assembly 303 moves downward under the action of the pressure difference between the main valve diaphragm upper cavity 301 and the main valve diaphragm lower cavity 302, and the opening of the throttle 307 of the main valve sleeve 306 is reduced, that is, the output flow pressure of the main valve 300 of the pressure regulator can be reduced until the output pressure tends to be stable and reaches the set rated output pressure.

As an embodiment of this embodiment, the pressure stabilizing valve 100 is provided with a primary valve flap and a secondary valve flap, and when closed, a certain gap exists between the pressure stabilizing primary valve rod 109 and the pressure stabilizing secondary valve flap 105, and when opened, the pressure stabilizing secondary valve flap 105 is opened first, and then the pressure stabilizing primary valve flap 104 is opened. At this time, the opening degree of the pressure-stabilizing secondary valve flap 105 is larger than that of the pressure-stabilizing primary valve flap 104. The pressure stabilizing first-stage valve clack 104 is used as a main throttle clack of the pressure stabilizing valve 100, the pressure stabilizing second-stage valve clack 105 is used as an auxiliary throttle clack of the pressure stabilizing valve 100, and under the high-pressure working condition, even if the pressure stabilizing first-stage valve clack 104 is damaged, the pressure stabilizing second-stage valve clack 105 can achieve the effect of tight sealing.

Further, the commanding valve 200 is provided with a primary flap and a secondary flap. When closed, there is a gap between the commanded primary valve stem 209 and the commanded secondary flap 205. When opened, the secondary flap 205 is directed to open first, and the first flap is directed to open next. At this time, the opening degree of the commanding second-stage valve flap 205 is larger than that of the commanding first-stage valve flap 204, the commanding first-stage valve flap 204 is used as a main throttle flap of the commanding valve 200, the commanding second-stage valve flap 205 is used as an auxiliary throttle flap of the commanding valve 200, and under a high-pressure working condition, even if the commanding first-stage valve flap 204 is damaged, the commanding second-stage valve flap 205 can achieve a tight sealing effect.

Furthermore, the pressure regulating command controller composed of the command valve 200 and the pressure stabilizing valve 100 leads the air inlet end of the pressure stabilizing valve 100 to the lower cavity 302 of the main valve diaphragm to be throttled by the four-stage valve clack when in work, the flow speed is reasonably controlled in an internal passage, and the valve clack is favorably protected from being scoured and damaged under the high-pressure working condition. When the valve is closed, the 4-stage valve is closed at the same time, and the medium is prevented from leaking to the downstream through the command control system.

And a commanding damping hole 213 for communicating the piston lower cavity 211 with the connecting interface I212 is formed in the commanding valve body 203 to form a slow air release channel structure. Compared with the prior art, the damping micropores which are arranged on the main valve rod 304 and are communicated with the main valve diaphragm upper cavity 301 and the main valve diaphragm lower cavity 302 are arranged on the command valve body 203, and the structural design can improve the pressure regulating response efficiency and precision of the pressure regulating controller.

The pressure stabilizing damping hole 114 in the connecting joint 113 on the pressure stabilizing valve 100 has a diameter larger than that of the command damping hole 213. The diameters of the pressure stabilizing orifice 114 of the pressure stabilizing valve 100 and the command orifice 213 of the command valve 200 are designed to match the pressure difference between the inlet pressure P1 and the outlet pressure P2 of the regulator main valve 300. The larger the pressure difference between P1 and P2, the smaller the diameter of the pressure stabilizing orifice 114, and the larger the diameter of the command orifice 213; the pressure regulator aims to ensure that the difference value between the pressure P5 entering the lower cavity of the diaphragm of the pressure stabilizing valve 100 and the pressure P2 above the upper cavity of the diaphragm of the pressure stabilizer is relatively small, and the difference value between the pressure P7 entering the lower cavity 302 of the main valve diaphragm of the pressure regulator and the pressure P2 above the upper cavity 301 of the main valve diaphragm is relatively small, so that the pressure regulator is prevented from being failed due to the fact that the diaphragm of the main valve 300 is damaged due to overlarge pressure difference. No matter how the diameter of the pressure stabilizing damping hole 114 and the diameter of the command damping hole 213 are matched, the diameter of the pressure stabilizing damping hole 114 is always larger than the diameter of the command damping hole 213.

The pressure difference between the two ends of the inlet and the outlet of the slow-release air passage formed by the damping hole 213 is controlled and commanded to be 0.05MPa-0.10 MPa. The trial shows that: the optimized design for controlling the damping pressure drop of the command damping hole 213 to be between 0.05MPa and 0.10MPa has an excellent flow discharge slow release effect, can effectively and smoothly release the pressure transient amplitude of the pressure regulating air medium in the main valve diaphragm upper cavity 301 and the main valve diaphragm lower cavity 302, can greatly improve the pressure change smoothness and stability of the pressure regulating air medium in the main valve diaphragm lower cavity 302, and improves the pressure regulating precision of the pressure regulator and the pressure stabilizing capability of output air pressure.

As another embodiment of this embodiment, referring to fig. 1 of the specification, the command valve 200 and the pressure stabilizing valve 100 are assembled together by screws, and the command valve body 203 and the pressure stabilizing valve body 103 are both provided with balance holes 214 to communicate the pressure stabilizing diaphragm upper cavity 112 of the pressure stabilizing valve 100 with the piston lower cavity 211 of the command valve 200.

Referring to fig. 2 and 3 of the specification, the pilot valve 200 and the pressure maintaining valve 100 may be separately provided and communicate through a signal pipe 400. Both the pilot valve 200 and the pressure maintaining valve 100 can independently introduce the pipeline pressure at the rear end of the main valve 300; the introduction of back-end line pressure by one of them places the lower piston chamber 211 of the command valve 200 in communication with the upper surge diaphragm chamber 112 of the surge valve 100.

At this time, the commanding valve body 203 of the commanding valve 200 is provided with a connecting interface II 215 communicated with the piston lower cavity 211. The pressure stabilizing valve body 103 of the pressure stabilizing valve 100 is provided with a connecting interface III 118 communicated with the pressure stabilizing membrane upper cavity 112.

Further, the pressure stabilizing valve body 103 includes a pressure stabilizing lower valve body 115, a pressure stabilizing middle valve body 116 and a pressure stabilizing upper valve body 117, and the connecting joint 113 is assembled on the pressure stabilizing lower valve body 115 to form the pressure stabilizing primary throttle chamber 106 with the pressure stabilizing lower valve body 115; the pressure stabilizing lower valve body 115 is assembled on the pressure stabilizing middle valve body 116, a pressure stabilizing secondary throttling cavity 107 is formed between the pressure stabilizing lower valve body 115 and the pressure stabilizing middle valve body 116, and the pressure stabilizing middle valve body 116 is provided with the pressure stabilizing tertiary throttling cavity 108; the pressure stabilizing diaphragm assembly 102 is assembled between the upper pressure stabilizing valve body 117 and the middle pressure stabilizing valve body 116, and the pressure stabilizing diaphragm assembly 102 divides a cavity between the middle pressure stabilizing valve body 116 and the upper pressure stabilizing valve body 117 into an upper pressure stabilizing diaphragm cavity 112 and a lower pressure stabilizing diaphragm cavity 111.

The commanding valve body 203 comprises a commanding lower valve body 216, a commanding middle valve body 217 and a commanding upper valve body 218, an end cover 219 is assembled on the commanding lower valve body 216, and a commanding primary throttling cavity 206 is formed between the end cover 219 and the commanding lower valve body 216; the commanding lower valve body 216 is assembled on the commanding middle valve body 217, and a commanding secondary throttling cavity 207 is formed between the commanding lower valve body and the commanding middle valve body 217; a commanding third-stage throttling cavity 208 is formed in the commanding middle valve body 217; the commanding piston assembly 202 is assembled on the commanding valve body 217 in a sliding mode, the commanding and adjusting spring assembly 201 is assembled between the commanding valve body 217 and the commanding valve body 218, the upper end of the commanding and adjusting spring assembly is connected with the commanding valve body 218, and the lower end of the commanding and adjusting spring assembly acts on the commanding piston assembly 202.

Claims (9)

1. A pressure regulating controller with four-stage throttling sealing comprises a command valve (200) and a pressure maintaining valve (100), and is characterized in that: the pressure stabilizing valve (100) comprises a pressure stabilizing adjusting spring assembly (101), a pressure stabilizing membrane assembly (102), a pressure stabilizing valve body (103), a pressure stabilizing primary valve clack (104) and a pressure stabilizing secondary valve clack (105); a pressure stabilizing primary throttling cavity (106), a pressure stabilizing secondary throttling cavity (107) and a pressure stabilizing tertiary throttling cavity (108) are arranged in the pressure stabilizing valve (100), and the pressure stabilizing primary throttling cavity (106), the pressure stabilizing secondary throttling cavity (107) and the pressure stabilizing tertiary throttling cavity (108) are communicated in sequence; the pressure stabilizing primary throttling valve clack (104) is arranged in the pressure stabilizing primary throttling cavity (106) and is used for controlling the connection and disconnection of a communication hole between the pressure stabilizing primary throttling cavity (106) and the pressure stabilizing secondary throttling cavity (107); the pressure stabilizing secondary throttling valve clack (105) is arranged in the pressure stabilizing secondary throttling cavity (107) and is used for controlling the connection and disconnection of a communicating hole between the pressure stabilizing secondary throttling cavity (107) and the pressure stabilizing tertiary throttling cavity (108); the pressure stabilizing primary valve clack (104) is connected with a pressure stabilizing primary valve rod (109), the pressure stabilizing primary valve rod (109) extends towards the pressure stabilizing secondary throttling cavity (107) to be contacted with the pressure stabilizing secondary valve clack (105), and when the pressure stabilizing primary valve clack (104) and the pressure stabilizing secondary valve clack (105) are both in a closed state, a set gap is formed between the top end of the pressure stabilizing primary valve rod (109) and the bottom of the pressure stabilizing secondary valve clack (105); the pressure stabilizing secondary valve clack (105) is connected with a pressure stabilizing secondary valve rod (110), and the upper end of the pressure stabilizing secondary valve rod (110) extends to a pressure stabilizing diaphragm lower cavity (111) and is connected with the pressure stabilizing diaphragm component (102); the pressure stabilizing adjusting spring assembly (101) is arranged in the pressure stabilizing membrane upper cavity (112) and is connected with the pressure stabilizing membrane assembly (102);

the commanding valve (200) comprises a commanding and adjusting spring assembly (201), a commanding piston assembly (202), a commanding valve body (203), a commanding first-stage valve clack (204) and a commanding second-stage valve clack (205), a commanding first-stage throttling cavity (206), a commanding second-stage throttling cavity (207) and a commanding third-stage throttling cavity (208) are arranged in the commanding valve (200), the commanding first-stage throttling cavity (206), the commanding second-stage throttling cavity (207) and the commanding third-stage throttling cavity (208) are communicated in sequence; the command primary throttling valve (204) is assembled in the command primary throttling cavity (206) and is used for controlling the connection and disconnection of a communication hole between the command primary throttling cavity (206) and the command secondary throttling cavity (207); the commanding secondary throttling valve (205) is assembled in the commanding secondary throttling cavity (207) and is used for controlling the connection and disconnection of a communication hole between the commanding secondary throttling cavity (207) and the commanding tertiary throttling cavity (208); the commanding first-stage valve clack (204) is connected with a commanding first-stage valve rod (209), the commanding first-stage valve rod (209) extends to the commanding second-stage throttling cavity (207) and is in contact with the commanding second-stage valve clack (205), and when the commanding first-stage valve clack (204) and the commanding second-stage valve clack (205) are both in a closed state, a set gap is formed between the top end of the commanding first-stage valve rod (209) and the bottom of the commanding second-stage valve clack (205); the commanding secondary valve clack (205) is connected with a commanding secondary valve rod (210), the upper end of the commanding secondary valve rod (210) is connected with a commanding piston assembly (202), the commanding secondary valve rod (210) is connected with a commanding valve body (203) in a sealing manner, and the commanding piston assembly (202) is arranged in the commanding valve body (203) in a sliding manner to form a piston lower cavity (211); the commanding and adjusting spring assembly (201) is arranged on the piston upper cavity and is connected with the commanding piston assembly (202);

a connecting joint (113) connected with the signal pipe (400) is arranged on the pressure-stabilizing primary throttling cavity (106), and a pressure-stabilizing damping hole (114) is arranged on the connecting joint (113); the upper pressure stabilizing membrane cavity (112) of the pressure stabilizing valve (100) and the lower piston cavity (211) of the command valve (200) are both communicated with the pressure of a downstream pipeline of the pressure regulator; a pressure stabilizing three-stage throttling cavity (108) of the pressure stabilizing valve (100) is communicated with a commanding first-stage throttling cavity (206) of the commanding valve (200); the commanding valve body (203) is provided with a connecting interface I (212) communicated with the commanding tertiary throttling cavity (208).

2. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: a commanding damping hole (213) which is communicated with the piston lower cavity (211) and the connecting interface I (212) is formed in the commanding valve body (203) to form a slow air release channel structure.

3. A pressure regulator controller having a four-stage throttle seal as set forth in claim 2, wherein: the diameter of a pressure stabilizing damping hole (114) in a connecting joint (113) on the pressure stabilizing valve (100) is larger than that of a command damping hole (213).

4. A pressure regulator controller having a four-stage throttle seal as claimed in claim 2 or 3, wherein: the pressure difference between the two ends of the inlet and the outlet of the slow-release air passage formed by the damping holes (213) is controlled and commanded to be 0.05MPa-0.10 MPa.

5. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: the command valve (200) and the pressure stabilizing valve (100) are assembled together through screws, balance holes (214) are formed in the command valve body (203) and the pressure stabilizing valve body (103), and a pressure stabilizing membrane upper cavity (112) of the pressure stabilizing valve (100) is communicated with a piston lower cavity (211) of the command valve (200).

6. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: a connecting interface II (215) communicated with the piston lower cavity (211) is arranged on a commanding valve body (203) of the commanding valve (200).

7. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: a pressure stabilizing valve body (103) of the pressure stabilizing valve (100) is provided with a connecting interface III (118) communicated with the pressure stabilizing membrane upper cavity (112).

8. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: the pressure stabilizing valve body (103) comprises a lower pressure stabilizing valve body (115), a middle pressure stabilizing valve body (116) and an upper pressure stabilizing valve body (117), the connecting joint (113) is assembled on the lower pressure stabilizing valve body (115), and a pressure stabilizing primary throttling cavity (106) is formed between the connecting joint and the lower pressure stabilizing valve body (115); the pressure stabilizing lower valve body (115) is assembled on the pressure stabilizing middle valve body (116) to form a pressure stabilizing secondary throttling cavity (107) with the pressure stabilizing middle valve body (116), and the pressure stabilizing middle valve body (116) is provided with the pressure stabilizing tertiary throttling cavity (108); the pressure stabilizing membrane assembly (102) is assembled between the upper pressure stabilizing valve body (117) and the middle pressure stabilizing valve body (116), and the pressure stabilizing membrane assembly (102) divides a cavity between the middle pressure stabilizing valve body (116) and the upper pressure stabilizing valve body (117) into an upper pressure stabilizing membrane cavity (112) and a lower pressure stabilizing membrane cavity (111).

9. A pressure regulator controller having a four-stage throttle seal as set forth in claim 1, wherein: the commanding valve body (203) comprises a commanding lower valve body (216), a commanding middle valve body (217) and a commanding upper valve body (218), an end cover (219) is assembled on the commanding lower valve body (216), and a commanding primary throttling cavity (206) is formed between the end cover (219) and the commanding lower valve body (216); the commanding lower valve body (216) is assembled on the commanding middle valve body (217), and a commanding secondary throttling cavity (207) is formed between the commanding lower valve body and the commanding middle valve body (217); a commanding third-stage throttling cavity (208) is formed in the commanding middle valve body (217); the commanding piston assembly (202) is assembled on the commanding middle valve body (217) in a sliding mode, the commanding adjusting spring assembly (201) is assembled between the commanding middle valve body (217) and the commanding upper valve body (218), the upper end of the commanding adjusting spring assembly is connected with the commanding upper valve body (218), and the lower end of the commanding adjusting spring assembly acts on the commanding piston assembly (202).

Images