KR101578778B1 - Concentric Circle Dual Valve type Pressure Relief Valve having Safety Function - Google Patents

Concentric Circle Dual Valve type Pressure Relief Valve having Safety Function Download PDF

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Publication number
KR101578778B1
KR101578778B1 KR1020140092393A KR20140092393A KR101578778B1 KR 101578778 B1 KR101578778 B1 KR 101578778B1 KR 1020140092393 A KR1020140092393 A KR 1020140092393A KR 20140092393 A KR20140092393 A KR 20140092393A KR 101578778 B1 KR101578778 B1 KR 101578778B1
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KR
South Korea
Prior art keywords
valve
main valve
sub
overpressure
inlet
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KR1020140092393A
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Korean (ko)
Inventor
서호철
박현영
김봉기
임현수
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세종공업 주식회사
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Priority to KR1020140092393A priority Critical patent/KR101578778B1/en
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Publication of KR101578778B1 publication Critical patent/KR101578778B1/en

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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
    • 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
    • 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
    • F16K17/08—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 providing a large discharge passage

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

According to the present invention, a concentric dual valve type pressure relief valve having a safety function comprises: a valve body having an outlet cover (20) coupled to an exit side of an inlet manifold (10) so as to form an overpressure discharge path to resolve overpressure (overload); and a main valve (40) and a sub valve (50) provided in a concentric type on the overpressure discharge path. In a dual valve type of the main valve (40) and the sub valve (50), compact can be realized due to size downsizing. In particular, in case of resolving failing in the main valve (40) or insufficient overpressure of the main valve (40), fail-safe can be realized through the sub valve (50) and further, extremely low temperature operation stability can be significantly improved by reducing an external contact area and a size of the volume to seal a path of the main valve (40) and the sub valve (50).

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a pressure relief valve comprising a concentric double valve having a safety function,

The present invention relates to a pressure relief valve, and more particularly, to a pressure relief valve that is compact in size due to downsizing of an entire size, safe in operation at a cryogenic temperature as well as in operation stability by fail- To a pressure relief valve composed of a concentric double valve to which a function is added.

In general, the use of a pressure relief valve (PRV) is to prevent system damage from overpressure (or excessive pressure). To this end, the PRV has a valve between the inlet to which the pressure is applied and the outlet to which the pressure is discharged, and the valve is opened by the overpressure caught in the inlet, thereby ejecting the overpressure caught in the inside to the outside.

Therefore, the PRV is installed in a pressure vessel or piping where fluid movement is present, thereby preventing damage to the system from overpressure that exceeds the set point.

When such a PRV is applied to a FPS (Fuel Processing System) of a fuel cell vehicle having a high-pressure vessel and a high-pressure piping line, very strict requirements are applied to the PRV to prevent system damage.

As a strict requirement, the valve operation stability is maintained at cryogenic temperature. For this reason, the PRV for FPS is double action due to the increase in the number of valves, thereby ensuring high reliability in comparison with the general PRV with fail-safe have.

As an example of this, there is a PRV for FPS in which two valves are arranged side by side with a path between an inlet through which pressure (or pressure) is applied and an outlet through which pressure is ejected.

Korean Patent Publication No. 10-2011-0062012 (June 10, 2011)

However, by applying two valves arranged side by side adjacent to the PRV, the FPS layout will be affected by the PRV, resulting in an increase in the external package associated with the valve with a complicated structure, and an increase in the overall size of the PRV when the FPS is applied There is no other choice.

In particular, the two valves arranged side-by-side cause an external contact area and a volume increase at the inlet of the pressurized inlet to increase the risk of freezing which deteriorates the cryogenic operating performance, The risk of system damage will also increase.

In view of the above, the present invention provides a double valve that is not concentric with the main valve and the sub-valve and does not expand the valve occupancy width, thereby achieving compactness by size downsizing, (Fail-safe) through the sub-valve in case of insufficient overpressure of the main valve or failure of the main valve, as well as the size of the external contact area and volume for sealing the passage between the main valve and the sub-valve. The present invention provides a pressure relief valve composed of a concentric double valve with a safety function that is greatly improved.

In order to achieve the above object, the present invention provides a pressure relief valve comprising a concentric double valve to which a safety function is added, comprising: a valve body having an overpressure discharge path, And a main valve and a sub-valve concentrically provided in the pressure discharge path; The main valve closing the overpressure inlet of the overpressure discharge path and being arranged in a straight line section from the overpressure inlet toward the overpressure outlet of the overpressure discharge path; Wherein the sub valve is housed in the internal space of the main valve so as to close the main valve aperture of the main valve and to be spaced apart from the overpressure outlet so as to be collinear with the overpressure inlet, And is concentric with the main valve in the internal space.

The overpressure inlet is blocked by a main valve quadring which is in close contact with the periphery of the inlet, and the main valve quadring is fitted in the main valve. The main valve aperture of the main valve is cut off by a sub-valve quadring that is tightly fitted around the through-hole, and the sub-valve quadring is fitted to the sub-valve.

Wherein the main valve includes a main valve poppet which is formed in a double concentric circle shape through which the main valve hole communicated with the sub valve is passed and blocks the over-pressure inlet, a poppet body having an internal space in which the sub valve is accommodated, A main valve spring having an elastic pressure equivalent to an operating pressure of the main valve poppet 41, and a main valve spring bolt fixed to the inner surface of the valve body. Wherein the double concentric shape of the main valve poppet comprises a first concentric circle having a diameter inserted into the overpressure inlet and a second concentric circle having a diameter close to the overpressure inlet so as to cover the overpressure inlet, Is fitted with a main valve quadring which blocks the overpressure inlet. And the main valve quadring is fitted into the recessed groove around the over-pressure inlet. The main valve spring is a cylindrical compression coil spring, and the main valve spring bolt is screwed with the valve body to support the main valve spring.

Wherein the sub-valve includes a sub-valve poppet which is formed in a double-concentric circle shape and blocks the main valve aperture, a sub-valve spring having an elastic pressure corresponding to an operating pressure of the sub-valve poppet, And a sub valve spring bolt integrally formed with the main valve poppet and fixed to the inner surface of the poppet body accommodating the sub valve. Wherein the double concentric circle shape of the sub valve poppet comprises a first concentric circle having a diameter inserted into the main valve through hole and a second concentric circle having a diameter close to the main valve through hole so as to cover the main valve through hole, A sub valve quadring for blocking the main valve aperture is fitted. And the sub valve quadring is fitted into the recessed groove around the main valve through-hole. The sub valve spring is a cylindrical compression coil spring, and the sub valve spring bolt is screwed with the poppet body to support the sub valve spring.

The valve body includes an inlet manifold forming the overpressure inlet and an outlet cover forming the overpressure outlet, and the outlet cover is engaged with the inlet manifold on the opposite side of the overpressure inlet. The inlet manifold includes a manifold body having a hollow cylindrical shape in which the main valve and the sub-valve are housed, an inlet nipple forming the over-pressure inlet, and a manifold body outlet through which the introduced over- A connecting flange for forming a connecting flange; Wherein the outlet cover comprises a cover body coupled to the connecting flange, an insert boss protruding from the cover body to be inserted into the manifold body, and an outlet nipple protruding from the cover body to be exposed to the outside, The through bore of the insert boss and the outlet nipple penetrates the overpressure outlet.

A stepped groove is formed around the overpressure inlet of the inlet nipple and the main valve quadring sandwiched between the main valve and the inlet is in close contact with the groove.

An O-ring is provided at a joint portion of the inlet manifold and the outlet cover, and the O-ring is inserted into a groove that is concentrically formed in the connecting flange.

The present invention is suitable as a PRV (Pressure Relief Valve) for a FPS (Fuel Processing System) that requires strict performance conditions because the main valve and the sub valve for solving overpressure act as double valves. The FPS layout can be installed without any influence on the FPS layout since the FPS is compacted by size downsizing in a coaxial-in-series arrangement.

In the present invention, since the main valve and the sub valve constitute a double valve, the failure of the main valve and the fail-safe after the main valve is opened and the pressure is stable, the general PRV High contrast can be secured.

In addition, the present invention can greatly improve the operational stability under extreme low temperature, which brings about freezing by increasing the operating stability by reducing the outer contact area and the volume size of the sub valve compared to the main valve.

FIG. 1 is a sectional view of a pressure relief valve constituted by a concentric double valve to which a safety function according to the present invention is added, FIG. 2 is a sectional view of a pressure relief valve composed of a concentric double valve to which a safety function according to the present invention is added, FIG. 3 is a diagram illustrating a state in which overpressure is relieved by normal operation of the main valve according to the present invention. FIG. Pressure relief state due to the fail-safe operation of the compressor.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings, which illustrate exemplary embodiments of the present invention. The present invention is not limited to these embodiments.

1 shows a sectional configuration of a pressure relief valve (PRV) to which a safety function according to the present embodiment is added.

As shown, the PRV includes an inlet manifold 10, an outlet cover 20, an O-ring 30, a main valve 40 acting as a double valve, and a sub-valve 50. In particular, the inlet manifold 10 and the outlet cover 20 are integrally formed to form a valve body, thereby forming an overpressure discharge path for introducing overpressure equal to or greater than a set value into the atmosphere. The main valve (40) and the sub valve (50) are concentrically arranged in the overpressure discharge path.

Specifically, the inlet manifold 10 receives the pressure formed inside the pressure vessel or the pipe in which the PRV is installed, is caught by the inlet, and the overpressure is released through the opening of the main valve 40 or the subvalve 50. The inlet manifold 10 has a hollow cylindrical shape and has a manifold body 11 in which the main valve 40 and the sub-valve 50 are accommodated as an internal space, and a pressure (or overload) An inlet nipple 13 forming an inlet to be introduced into the folded body 11 and a connecting flange 13 forming an outlet of the manifold body through which the overpressure introduced into the internal space of the manifold body 11 is discharged through the inlet nipple 13, (15). A stepped trench is formed on the main valve seat surface through which the main valve 40 is closely contacted in the internal space of the manifold body 11 through the inlet nipple 13 so that the main valve poppet 41 of the main valve 40 . In the state where the cover body 21 of the outlet cover 20 is in close contact with the connecting flange 15, grooves into which the O-rings 30 are inserted are cut into concentric circles. The cover body 21 of the outlet cover 20 can be seated in the groove. Particularly, the connecting flange 15 of the inlet manifold 10 and the cover body 21 of the outlet cover 20 can be fixed by welding.

Specifically, the outlet cover 20 ejects the overpressure introduced into the inlet manifold 10 to the outside to lower the overpressure to a set pressure (or set load). The outlet cover 20 is inserted into the manifold body 11 of the inlet manifold 10 and the cover body 21 inserted into the groove of the connecting flange 15 of the inlet manifold 10, The insert boss 23 integrally protruding from the cover body 21 so as to act as a passage through which the introduced pressure and pressure are exerted and the cover body 21 integrally projecting from the insert boss 23 And a protruded outlet nipple 25. Therefore, the discharge passage penetrates through the cover body 21, the insert boss 23, and the outlet nipple 25, and the overpressure is ejected to the outside.

Specifically, the O-ring 30 is padded at a joint portion between the inlet manifold 10 and the outlet cover 20, thereby sealing the air-tightness of the over-pressure discharge passage formed by the inlet manifold 10 and the outlet cover 20 Respectively. For this purpose, the O-ring 30 is made of a material having elastic deformation. In particular, the O-ring 30 is positioned in the groove of the connecting flange 15 of the inlet manifold 10 so as to enhance the hermeticity of the overpressure discharge passage, and the outlet cover 20 and inlet manifold 10 And receives a pressing force by the cover body (21) when engaged.

More specifically, the main valve 40 is separated from the inlet nipple 13 by the overpressure applied to the inlet nipple 13 of the manifold body 11, and thereby the overpressure is introduced into the internal space of the inlet manifold 10 Thereby forming a passage. To this end, the main valve 40 is set to have an operating pressure smaller than an overpressure (or overload).

Specifically, the sub-valve 50 is positioned in the through-hole of the main valve 40 so as to be over-pressurized. When the main valve 40 is not open due to overpressure, And flows into the inner space of the inlet manifold 10 from the inlet nipple 13. Therefore, in the sub-valve 50, a fail-safe substitute for the failure of the main valve 40 is implemented.

2 shows an exploded configuration of the inlet manifold 10, the outlet cover 20, the O-ring 30, the main valve 40, and the sub-valve 50. FIG.

The main valve 40 includes a main valve poppet 41, a main valve quadring 43, a main valve spring 45, and a main valve spring bolt 47 as shown in FIG.

The main valve poppet 41 forms a main valve through hole having a double concentric circle shape and a double concentric circle shape with a different diameter. For example, the biconcave concentric shape is composed of a first concentric circle having a diameter inserted into the through hole of the inlet nipple 13, and a second concentric circle having a diameter close to the through hole so as to cover the through hole of the inlet nipple 13. Therefore, The main valve poppet 41 is operated in a double-concentric circle shape by being pressed against the inlet pressure of the inlet nipple 13 by being in close contact with the overpressure hole of the inlet nipple 13 in the inner space of the inlet manifold 10. In addition, the main valve poppet 41 further has a cylindrical poppet body 41-1 having an internal space, and the internal space of the poppet body 41-1 is connected to the main valve poppet 41, The sub valve 50 accommodated in the poppet body 41-1 blocks the main valve aperture of the main valve poppet 41 by communicating with the through hole. Therefore, the main valve 40 can implement fail-safe by the sub-valve 50 at the time of failure or after the normal opening thereof and the pressure is sustained.

The main valve quad ring 43 is fitted in the first concentric circle inserted into the overpressure through-hole of the inlet nipple 13 of the double concentric circle of the main valve poppet 41. Therefore, the main valve quad ring 43 is inserted into the groove concentrically formed around the overpressure hole of the inlet nipple 13, thereby improving the airtightness of the main valve poppet 41. Particularly, since the main valve quad ring 43 is in contact with the groove to block the overpressure through-holes of the inlet nipple 13, the main valve 40 has a contact area and a volume size formed with the inlet nipple 13 at a minimum size Can be reduced.

The main valve spring 45 is a cylindrical compression coil spring and sets an elastic force applied to the main valve poppet 41 to apply an operating pressure smaller than the overpressure. Therefore, the main valve spring 45 is positioned between the main valve poppet 41 and the main valve spring bolt 47 in a state of wrapping the poppet body 41-1.

The main valve spring bolt 47 is screwed into the outer circumferential surface of the body having a hole at the center and assembled into the internal space of the manifold body 11 using a screw formed on the inner surface of the manifold body 11. Therefore, the main valve spring bolt 47 can be varied in the compression force for pressing the main valve spring 45 to adjust the assembly position using the screw.

The sub valve 50 includes a sub valve poppet 51, a sub valve quadring 53, a sub valve spring 55, and a sub valve spring bolt 57.

The sub valve poppet 51 has a double concentric circle shape with different diameters. For example, the biconcave concentric shape may be formed by a first concentric circle having a diameter inserted into the main valve through hole of the main valve poppet 41, The sub valve poppet 51 is in close contact with the main valve aperture of the main valve poppet 41 in the internal space of the poppet body 41-1 by using the double concentric circle shape, 41 by the overpressure of the inlet nipple 13. Therefore, the sub-valve 50 can relieve overpressure by fail-safe when the main valve 40 fails or after the main valve 40 is opened and the pressure continues. In addition, the sub valve poppet 51 is further provided with a double concentric poppet rod 51-1 having a different diameter, so that the sub valve spring 55 maintains a stable assembled state.

The sub valve quad ring 53 is fitted in a first concentric circle inserted into the main valve aperture of the double valve concentric main valve poppet 41 of the sub valve poppet 51. Therefore, the sub valve quad ring 53 is inserted into the groove concentrically formed around the main valve aperture of the main valve poppet 41, thereby improving airtightness of the sub valve poppet 51. Particularly, when the sub valve quad ring 53 contacts the groove and blocks the main valve aperture of the main valve poppet 41, the sub valve 50 can minimize the contact area and the volume size formed with the main valve poppet 41, Size can be reduced.

The sub valve spring 55 is a cylindrical compression coil spring and sets an elastic force applied to the sub valve poppet 51 to apply an operating pressure smaller than an overpressure. Therefore, the sub valve spring 55 is positioned between the sub valve poppet 51 and the sub valve spring bolt 57 in a state in which the poppet rod 51-1 is wrapped.

The sub valve spring bolt 57 is screwed into the outer circumferential surface of the body formed with a hole at the center and assembled into the internal space of the poppet body 41-1 by using a screw formed on the inner surface of the poppet body 41-1 . Therefore, the sub-valve spring bolt 57 can be varied in the adjustment of the assembling position using the screw by the compressive force pressing the sub-valve spring 55.

On the other hand, Fig. 3 shows the overpressure relieved state by the normal operation of the main valve 40. Fig.

As shown in the figure, when the overpressure is formed in the high-pressure vessel or the high-pressure piping line (for example, the FPS (Fuel Processing System) of the fuel cell vehicle) in which the PRV is installed, the inlet nipple 13 of the inlet manifold 10, The main valve 40 is switched over to the overpressure state. In addition, the sub-valve 50 receives overpressure through the main valve aperture in a state where the main valve aperture formed in the main valve poppet 41 of the main valve 40 is closed.

The overpressure pushes the main valve poppet 41 out of the overpressure through-hole of the inlet nipple 13 by overcoming the resistance of the main valve spring 45 and pushing of the main valve poppet 41 pushes the inlet nipple 13, So that the main valve 40 is brought into an operating state by separating the main valve quadring 43 from the overpressure through-hole of the main valve 40.

The operation of the main valve 40 as described above means forming the overpressure discharge passage for the overflow of the overpressure. Therefore, the overpressure is introduced into the internal space of the manifold body 11 through the gap formed between the main valve poppet 41 and the inlet nipple 13, and the overpressure introduced into the internal space is transmitted to the inlet manifold 10, Flows through the through hole of the main valve spring bolt (47) provided at the outlet portion of the outlet cover (20).

Then, the overpressure is introduced into the through hole of the insert boss 23 and exits through the cover body 21 and the through hole leading to the outlet nipple 25, so that the outlet of the overpressure discharge passage is led out through the outlet cover 20 As shown in FIG.

By the operation of the PRV, the overpressure formed in the high-pressure vessel or the high-pressure piping line is lowered to the set value again, thereby preventing the system damage by the high-pressure vessel or the high-pressure piping line.

4 shows the overpressure relieved state by the operation of the sub-valve 50, which means a fail-safe spherical shape by the sub-valve 50. In FIG. In this state, an overpressure equal to or higher than a set value is formed in the high-pressure vessel or the high-pressure piping line (for example, FPS (Fuel Processing System) of the fuel cell vehicle) Means that the main valve 40 is not operated or the main valve 40 is opened and the overpressure is continued so that additional overpressure relief is required. In the following description, it is assumed that the stick state of the main valve 40 due to the failure of the main valve 40 is assumed.

The overpressure is introduced into the main valve through hole of the main valve poppet 41 by the stick of the main valve 40 so that the sub valve 50 is switched to the overpressure state.

The overpressure pushes the sub valve poppet 51 out of the main valve aperture of the main valve poppet 41 by overcoming the resistance of the sub valve spring 55 and the pushing of the sub valve poppet 51 pushes the main valve poppet 51 The sub-valve quadring 53 is separated from the through-hole of the sub-valve 41 so that the sub-valve 50 is switched to the operating state.

The operation of the sub-valve 50 as described above means formation of an overpressure discharge passage for the external discharge of overpressure. Therefore, the overpressure is introduced into the internal space of the poppet body 41-1 through the gap formed between the sub valve poppet 51 and the main valve poppet 41, and the overpressure introduced into the internal space is transmitted to the poppet body 41 -1 through the through hole of the sub valve spring bolt 57 provided at the outlet portion of the main valve spring bolt 47 and then flows to the outlet cover 20 through the through hole of the main valve spring bolt 47 .

Then, the overpressure is introduced into the through hole of the insert boss 23 and exits through the cover body 21 and the through hole leading to the outlet nipple 25, so that the outlet of the overpressure discharge passage is led out through the outlet cover 20 As shown in FIG.

By the operation of the PRV, the overpressure formed in the high-pressure vessel or the high-pressure piping line is lowered to the set value again, thereby preventing the system damage by the high-pressure vessel or the high-pressure piping line.

As described above, the pressure relief valve composed of the concentric double valve to which the safety function according to the present embodiment is added is directed toward the outlet of the inlet manifold 10 so as to form an overpressure discharge path for overpressure (overload) The main valve 40 and the sub valve 50 concentrically provided in the pressure discharge path and the valve body composed of the combined outlet cover 20 and the main valve 40 and the sub valve 50 of the sub valve 50, The size reduction is achieved by size downsizing even when the main valve 40 fails or the main valve 40 fails to relieve the pressure of the main valve 40 due to fail safe through the sub valve 50 Fail-Safe, as well as greatly reducing the size of the external contact area and volume for sealing the passage between the main valve 40 and the sub-valve 50, greatly improving the cryogenic operating stability.

10: inlet manifold 11: manifold body
13: inlet nipple 15: connecting flange
20: Outlet cover 21: Cover body
23: insert boss 25: outlet nipple
30: O-ring 40: Main valve
41: main valve poppet 41-1: poppet body
43: main valve quadring 45: main valve spring
47: Main valve spring bolt
50: Sub-valve 51: Sub-valve Poppet
51-1: Poppet rod 53: Subvalve quadring
55: Sub valve spring 57: Sub valve spring bolt

Claims (15)

A valve body having an overpressure discharge path formed by injecting overpressure equal to or greater than a preset value into the atmosphere; a main valve and a subvalve concentrically provided in the overpressure discharge path;
The main valve closing the overpressure inlet of the overpressure discharge path and being arranged in a straight section toward the overpressure outlet of the overpressure discharge path at the overpressure inlet;
Wherein the sub valve is housed in the internal space of the main valve so as to close the main valve aperture of the main valve and to be spaced apart from the overpressure outlet so as to be collinear with the overpressure inlet, Concentric with the main valve in the internal space;
Wherein the main valve aperture of the main valve is blocked by a sub-valve quadring that is closely attached around the aperture, and the sub-
Pressure relief valve consisting of a concentric double valve with added safety function.
[3] The apparatus of claim 1, wherein the overpressure inlet is blocked by a main valve quadring which is in close contact with the periphery of the inlet, and the main valve quadring is fitted to the main valve. Pressure Relief Valve.

delete [2] The apparatus of claim 1, wherein the main valve includes a main valve poppet which is formed in a double concentric circle shape through which the main valve aperture blocked by the sub valve penetrates and blocks the over-pressure inlet, A main valve spring having an elastic pressure corresponding to an operating pressure of the main valve poppet, and a main valve spring bolt fixed to an inner surface of the valve body. Pressure relief valve.
[5] The apparatus of claim 4, wherein the double concentric shape of the main valve poppet comprises a first concentric circle having a diameter inserted into the overpressure inlet, and a second concentric circle having a diameter close to the overpressure inlet so as to cover the overpressure inlet And a main valve quadring for blocking the overpressure inlet is inserted into the first concentric circle. The pressure relief valve according to claim 1, wherein the main relief valve comprises a concentric double valve added with a safety function. The pressure relief valve according to claim 5, wherein the main valve quadring is closely fitted into a groove formed in the periphery of the overpressure inlet.
[5] The centrifugal type double valve according to claim 4, wherein the main valve spring is a cylindrical compression coil spring, and the main valve spring bolt is screwed to the valve body to support the main valve spring. Made pressure relief valve.
The sub-valve according to claim 1, wherein the sub-valve includes a sub-valve poppet which is formed in a double concentric circle and blocks the main valve aperture, a sub-valve spring having an elasticity pressure corresponding to an operating pressure of the sub-valve poppet, Wherein the sub valve spring bolt is integrally formed with the main valve poppet of the main valve and fixed to the inner surface of the poppet body in which the sub valve is accommodated.

The sub valve of claim 8, wherein the double concentric circle of the sub valve poppet comprises a first concentric circle having a diameter inserted into the main valve through hole and a second concentric circle having a diameter close to the main valve through hole so as to cover the main valve through hole And a sub-valve quadring for blocking the main valve hole is inserted into the first concentric circle.
[12] The pressure relief valve as claimed in claim 9, wherein the sub valve quadring is closely fitted to the grooved groove around the main valve through hole.
[Claim 8] The centrifugal type double valve according to claim 8, wherein the sub valve spring is a cylindrical compression coil spring, and the sub valve spring bolt is screwed to the poppet body to support the sub valve spring. Made pressure relief valve.
[3] The apparatus of claim 1, wherein the valve body comprises an inlet manifold defining the overpressure inlet and an outlet cover forming the overpressure outlet, the outlet cover including an inlet manifold Pressure relief valve comprising a concentric double valve with added safety function.
[12] The inlet manifold according to claim 12, wherein the inlet manifold comprises a hollow cylindrical shape and has an internal space therein with a manifold body in which the main valve and the sub-valve are accommodated, an inlet nipple forming the over-pressure inlet, A connecting flange forming a manifold body outlet;
Wherein the outlet cover comprises a cover body coupled to the connecting flange, an insert boss protruding from the cover body to be inserted into the manifold body, and an outlet nipple protruding from the cover body to be exposed to the outside, Wherein the insert boss and the outlet nipple are formed with concentric double valves to which a safety function is added.
[14] The safety function according to claim 13, wherein a stepped groove is formed around the overpressure inlet of the inlet nipple, and a main valve quadring fitted to the main valve is in close contact with the periphery of the inlet. A pressure relief valve consisting of a concentric double valve added.
[Claim 14] The method according to claim 13, wherein an O-ring is provided at a joint portion between the inlet manifold and the outlet cover, and the O-ring is inserted into a groove concentrically formed in the connecting flange. A pressure relief valve consisting of a valve.
KR1020140092393A 2014-07-22 2014-07-22 Concentric Circle Dual Valve type Pressure Relief Valve having Safety Function KR101578778B1 (en)

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KR1020140092393A KR101578778B1 (en) 2014-07-22 2014-07-22 Concentric Circle Dual Valve type Pressure Relief Valve having Safety Function

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108167486A (en) * 2017-12-27 2018-06-15 应鸿 The hot water water supply installation saved water and energy
US10403912B2 (en) 2016-04-26 2019-09-03 Hyundai Motor Company Anode discharge valve for fuel cell system
KR20220075006A (en) 2020-11-26 2022-06-07 팍스텍(주) Proportional Pressure setting Relief Valve
CN114645959A (en) * 2021-11-24 2022-06-21 厦门劲博汇科技有限公司 Automobile, automobile seat, massager and rapid pressure relief device
KR102521583B1 (en) * 2021-12-16 2023-04-13 한국자동차연구원 Double Check Valve

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JP2008176693A (en) 2007-01-22 2008-07-31 Neriki:Kk Pressure reducing valve
JP2014055619A (en) 2012-09-11 2014-03-27 Yamada Seisakusho Co Ltd Relief valve device

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JP2008176693A (en) 2007-01-22 2008-07-31 Neriki:Kk Pressure reducing valve
JP2014055619A (en) 2012-09-11 2014-03-27 Yamada Seisakusho Co Ltd Relief valve device

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10403912B2 (en) 2016-04-26 2019-09-03 Hyundai Motor Company Anode discharge valve for fuel cell system
CN108167486A (en) * 2017-12-27 2018-06-15 应鸿 The hot water water supply installation saved water and energy
KR20220075006A (en) 2020-11-26 2022-06-07 팍스텍(주) Proportional Pressure setting Relief Valve
CN114645959A (en) * 2021-11-24 2022-06-21 厦门劲博汇科技有限公司 Automobile, automobile seat, massager and rapid pressure relief device
WO2023093264A1 (en) * 2021-11-24 2023-06-01 王翠玲 Automobile, automobile seat, massager, and rapid pressure relief apparatus
CN114645959B (en) * 2021-11-24 2024-03-22 厦门劲博汇科技有限公司 Automobile, automobile seat, massager and quick pressure relief device
KR102521583B1 (en) * 2021-12-16 2023-04-13 한국자동차연구원 Double Check Valve
WO2023113268A1 (en) * 2021-12-16 2023-06-22 한국자동차연구원 Double check valve

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