KR101773042B1 - High differential pressure expansion valve for re-liquefy of precise fine flow control is possible cryogenic high pressure gas - Google Patents

Abstract

The present invention relates to a high differential pressure expansion valve to re-liquefy cryogenic high pressure gas capable of realizing precise fine flow control without concerns about high abrasion, breakage, or excessive generation of noise. According to the present invention, the expansion valve comprises: a valve body including an inlet part, an outlet part, and a cage reception part; a cylindrical cage assembly including inner and outer seat cages, a seat ring member, and a seat cage assembly; a hood member fixated and coupled to the valve body when fixating and receiving the seat cage assembly and the cylindrical cage assembly in the cage reception part; and a stem and micro plug member received inside the seat cage assembly and the cylindrical cage assembly to increase/decrease the area of a fine passage through a change of an opening rate through vertical movement with a pick ring disposed therebetween, to adjust the flow rate passing the fine passage.

Description

TECHNICAL FIELD [0001] The present invention relates to a high-pressure expansion valve for re-liquefaction of a cryogenic high-pressure gas capable of precise micro-flow control. BACKGROUND OF THE INVENTION 1. Field of the Invention [0002]

The present invention relates to a high-pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of precise micro-flow control, and more particularly, to a high-pressure expansion valve for cryogenic high-pressure gas such as a liquefied natural gas (LNG) Pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of precise micro-flow control at a reduced pressure of a high-pressure gas passing through a high-pressure expansion valve for re-liquefying the gasified gas through decompression.

In recent years, inexpensive natural gas, which is inexpensive with oil, has been widely used as an energy source. These natural gases are made from liquefied natural gas to cool down to about -162 ° C under atmospheric pressure to reduce their volume through condensation to facilitate storage and transport. Liquefied natural gas has a volume of about 1/600 of that of natural gas under atmospheric pressure, which is very convenient for transportation and storage.

In recent years, the use of liquefied natural gas has been expanding, including the use of high-pressure liquefied natural gas as fuel instead of conventional diesel fuel. In the case of cryogenic high-pressure gas such as liquefied natural gas, surplus gas is generated during transportation, storage or use, and it is necessary to re-liquefy and store and use it.

A high differential pressure valve using the line-Thomson effect has been used for re-liquefaction of cryogenic high-pressure gas.

A representative example of such a high differential pressure valve is "High Differential Pressure Control Valve for Offshore Plant" of Patent Document 1 to be described later and "Disk Laminated High Differential Pressure Control Valve for Offshore Plant" of Patent Document 2.

The above Patent Documents 1 and 2 include a disc laminate for utilizing the fluid flow principle in accordance with the line-Thomson effect of the high differential pressure valve. The disc stacking body reduces the moving speed of the fluid while increasing the length and the passing area of the flow path for reducing the pressure of the inflow fluid so that the disc stacking body can be separated from each other And a plurality of discs each having a connection groove connecting the two flow grooves or one or both of the connection grooves are stacked.

However, in the case of a disk stack composed of a plurality of stacked disks, precise stacking is difficult when the working dimensions of the disks are different, and precise alignment at the time of stacking is not easy even if there is no problem with the machining dimensions. That is, when the machining dimensions of the respective stacked disks are different or precision alignment is not properly performed, the flow path is opened or closed by inserting it into the inner hollow portion of the disk stack body and reciprocating in the longitudinal direction to regulate the flow rate There is a problem that the plunger of the disk stack body easily wears or breaks due to friction with the disk stack body or causes severe noise.

In addition, since the diameter of the end of the plunger and the stem is substantially constant along the longitudinal direction of the stem, it is difficult to precisely control the opening or closing of the microchannel so that the flow rate can not be controlled properly. Lt; / RTI >

In addition, the disc laminate should be depressurized by the high pressure fluid alone, and if the pressure difference required to reduce the pressure is 300 bar or more, the disc laminate and the plunger cause severe wear or noise due to excessive pressure difference. .

KR 10-1356123 B1 KR 10-1376093 B1

Accordingly, it is an object of the present invention to solve the above problems and to provide a high pressure differential valve which is capable of changing the disc structure having a passage for reducing pressure in a high differential pressure valve, Pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control without causing wear, breakage or excessive noise.

Another problem to be solved by the present invention is to solve the above problems and to precisely control the opening or closing of the flow path so that it is possible to control the fine flow rate of the differential pressure valve even under the micro flow rate passing condition. Valve.

Another problem to be solved by the present invention is to solve the above problems and to provide a high pressure differential valve which is capable of reducing the pressure of the fluid sequentially in a plurality of spaces in the high differential pressure valve, Pressure expansion valve for re-liquefaction of a cryogenic high-pressure gas capable of precise micro-flow control capable of decreasing the amount of the micro-flow.

According to an aspect of the present invention, there is provided a high pressure differential expansion valve for re-liquefying a cryogenic high pressure gas, the valve body comprising an inlet portion, a discharge portion and a cage accommodating portion, A plurality of first fluid pass holes formed at predetermined intervals in a part of the first fluid pass hole passing from an outer diameter toward the inner seat cage receiving hole, a plurality of first fluid pass holes formed at predetermined intervals from the inner diameter of the outer sheet cage, A micro plug hole is formed which is coupled to the outer sheet cage in a state in which a part thereof is accommodated in the inner seat cage receiving hole so as to have a connection groove and which penetrates the inside in the vertical direction and penetrates from the outer diameter toward the micro plug hole, It is located in a straight line with the fluid passage hole A seat cushion assembly having a seat cushion having an inner seat cage, a seat ring member coupled with the inner seat cage, and a pick ring positioned between the inner seat cage and the seat ring member, A lower portion fixedly coupled to the upper portion of the seat cage assembly and having an outer cylindrical cage and at least one inner cylindrical cage vertically laterally received within the outer cylindrical cage and having at least one inner cylindrical cage and at least one inner cylindrical cage, Wherein a plurality of third fluid passing holes are formed at predetermined intervals in the radial direction from an outer diameter of the cylindrical cage assembly, , A bonnet member which is fixedly coupled to the valve body in a state where the base and seat cage assemblies and the cylindrical cage assembly are fixedly received in the cage accommodating portion and accommodated in the seat cage assembly and the cylindrical cage assembly, And a stem and a micro plug member having a stem and a micro plug for adjusting a flow rate passing through the micro flow channel by increasing or decreasing an area of the micro flow channel through a change in opening ratio with the pick via the micro plug, A first flow rate adjusting groove and a second flow rate adjusting groove are formed on at least a portion of the outer peripheral surface of the body corresponding to the two directions, respectively, as the distance from the stem increases.

The first flow rate adjusting groove and the second flow rate adjusting groove may be formed to have different opening rates.

The first flow rate adjusting groove may include an inclined groove whose opening rate increases as the distance from the stem increases, and a flat groove whose opening rate is maintained constant.

As described above, according to the high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control according to the present invention, precision alignment can be performed through the modified side- There is an advantageous effect that there is no fear of abrasion, breakage or excessive noise generation.

According to the present invention, there is provided a high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control, wherein the first flow rate control groove and the second flow rate control groove, It is possible to precisely control the opening or closing of the flow path through the up and down movement of the micro plug formed in a part thereof, and it is advantageous in that the precision flow rate of the differential pressure valve can be controlled even under the micro flow rate passing condition.

According to the present invention, there is provided a high-pressure expansion valve for re-liquefying a cryogenic high-pressure gas according to the present invention, wherein a plurality of pressure-sensitive cages are provided so as to successively reduce the pressure, And an advantageous effect of reducing the noise inducing phenomenon.

1 and 2 are an exploded cross-sectional view and an assembled cross-sectional view, respectively, of a high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control according to an embodiment of the present invention;
FIG. 3 is an enlarged view of the 'A' region of FIG. 2,
FIG. 4 is a partially cutaway perspective view of the inner and outer seat cages, which are the ends of the high-pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of controlling the micro-flow rate according to an embodiment of the present invention;
FIG. 5 is a partially cutaway perspective view of a cylindrical cage assembly, which is a part of a high pressure differential expansion valve for re-liquefying a cryogenic high pressure gas capable of precise minute flow rate control according to an embodiment of the present invention;
6 and 7 are a perspective view and a plan view of a stem and micro plug member of a high pressure differential expansion valve for cryogenic high pressure gas re-lubrication capable of precise micro flow rate control according to an embodiment of the present invention,
FIG. 8 is a graph showing the results of the micro-flow rate control according to the opening ratio change between the pick-up, the stem, and the micro-plug member during the depressurization process using the high-pressure expansion valve for cryogenic high- A coupling section for explaining a process to be performed,
FIG. 9 is a partially cutaway perspective view for explaining a first pressure reduction process in internal and external seat cages, which is a part of a high pressure differential expansion valve for re-liquefaction of a cryogenic high pressure gas capable of precise minute flow rate control according to an embodiment of the present invention;
10 is a cross-sectional view taken along line BB 'of FIG. 9,
11 is a partial cutaway perspective view for explaining a second pressure reduction process in a cylindrical cage assembly, which is a part of a high pressure differential expansion valve for re-liquefaction of cryogenic high pressure gas capable of precise minute flow rate control according to an embodiment of the present invention,
12 is a cross-sectional view cut along the line CC 'in FIG.

BRIEF DESCRIPTION OF THE DRAWINGS The advantages and features of the present invention, and how to accomplish them, will become apparent by reference to the embodiments described in detail below with reference to the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, but may be implemented in various other forms, and it should be understood that the present embodiment is intended to be illustrative only and is not intended to be exhaustive or to limit the invention to the precise form disclosed, To fully disclose the scope of the invention to a person skilled in the art, and the invention is only defined by the scope of the claims.

Like reference numerals refer to like elements throughout the specification. The embodiments described herein will be described with reference to an ideal cross-sectional view, an enlarged view, and a partially cutaway perspective view of the present invention.

Hereinafter, the construction and operation method of the high-pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of controlling the micro-flow rate according to the embodiment of the present invention will be described in detail with reference to the accompanying drawings. So that it can be easily carried out by the owner.

Hereinafter, a high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control according to an embodiment of the present invention will be described in detail with reference to FIGS. 1 to 7. FIG.

1 and 2 are an exploded cross-sectional view and an assembled cross-sectional view, respectively, of a high pressure differential expansion valve for re-liquefying cryogenic high-pressure gas capable of precise minute flow rate control according to an embodiment of the present invention. FIG. 4 is a partially cutaway perspective view of an inner and an outer seat cage, which are the ends of a high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control according to an embodiment of the present invention. 6 and 7 are partial cutaway perspective views of a cylindrical cage assembly which is a part of a high differential pressure expansion valve for re-liquefaction of a cryogenic high pressure gas capable of precise minute flow rate control according to an example, Fig. 2 is a perspective view and a plan view of a stem and micro plug member of a high differential pressure expansion valve for re-liquefaction of cryogenic high-pressure gas which can be controlled.

1 to 7, the high differential pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of precise micro-flow control according to an embodiment of the present invention includes a valve body 100, a seat cage assembly 200, Assembly 300, a cage spacer 400, a bonnet member 500, and a spar and micro plug member 600.

The valve body 100 is formed such that the inlet 110 through which the vaporized fluid flows and the outlet 120 through which the re-liquefied fluid is discharged correspond to both sides of the valve body 100, And a cage accommodating portion 130 having an open upper portion.

The seat cage assembly 200 is accommodated in a lower portion of the cage accommodating portion 130 and firstly reduces the high pressure gas introduced through the inlet portion 110. [ To this end, the seat cage assembly 200 includes an outer seat cage 210, an inner seat cage 230, a pick ring 250 and a seat ring member 270.

The outer seat cage 210 includes an outer seat cage body 212 generally cylindrical in shape. The outer sheet cage body 212 is formed with an inner seat cage receiving hole 214 through which the inside of the outer seat cage body 212 penetrates in the vertical direction and has a first fluid passage hole 216 are formed at predetermined intervals.

The inner seat cage 230 is formed in a generally cylindrical shape and a part of the inner seat cage 230 is accommodated in the inner seat cage accommodating hole 214 so as to have a flow path connecting groove 246 with a predetermined spacing from the inner diameter of the outer seat cage body 212 An inner seat cage body 232, a lower seat portion 233, and a seat ring member engagement portion 238 which are mutually coupled with the outer seat cage 210 by a fixing method such as welding.

The inner sheet cage body 232 is formed with a micro plug through hole 234 penetrating the inside of the inner seat cage body 232 in the up and down direction. The inner sheet cage body 232 is penetrated from the outer diameter toward the micro plug through hole 234, And a plurality of second fluid pass holes (236) which are not located on a straight line are formed at predetermined intervals.

The lower seating portion 233 is connected to the lower portion of the inner seat cage body 232 by a diameter larger than the diameter of the inner seat cage body 233 to close the lower portion of the micro plug passage 234, 232 of the outer sheet cage body 212. As shown in FIG.

The seat ring member engaging portion 238 is integrally coupled to the upper portion of the inner seat cage body 232 and the inner seat cage body 232 to have a diameter smaller than that of the inner seat cage body 232. [ A threaded portion is formed on the outer diameter of the seat ring member coupling portion 238 and a micro plug through hole 234 penetrating in the up and down direction is similarly formed. ).

The seat ring member 270 includes a seat ring body 272 in which a seat cage engagement groove 276 and a pick receiving recess 275 and a micro plug through hole 274 are sequentially formed from the bottom to the top in the vertical direction do.

The seat cage engaging groove 276 is formed with a thread corresponding to the outer diameter thread of the seat ring member engaging portion 238 so that the seat cushion engaging portion 238 is received and coupled to the seat ring body 272 do.

The pick receiving groove 275 has a smaller diameter than the seat cage engaging groove 276 at the upper portion of the seat cage engaging groove 276 to receive and engage the pick 250.

The micro plug through hole 274 is formed in the upper portion of the pick receiving groove 275 so as to pass through the smaller diameter than the pick receiving groove 275 in the up and down direction.

An upper coupling end 278 is formed at the upper outer diameter of the seat ring member 270, and a gasket coupling end 277 is formed at the lower outer diameter.

The gasket coupling end 277 is seated on the lower end of the cage receiving portion 130 of the valve body 100 so that the seat cage assembly 200 can directly open the fluid between the inlet portion 110 and the discharge portion 120 .

The peeling ring 250 is made of a material resistant to abrasion, friction or chemical such as natural rubber, synthetic rubber or synthetic resin and has an inner seat cage 230, a seat ring member 270 and a stem and a micro plug member 600 ) Reduce clearance of assembly and engagement tolerances. Accordingly, the pick 250 performs an auxiliary function of reducing the passage pressure of the fluid so as to be close to the zero leak during the closing operation of the valve, and precisely controls the flow rate at the time of controlling the minute passing flow rate .

The cylindrical cage assembly 300 is accommodated in a central portion of the cage receiving portion 130 while the lower portion thereof is fixedly coupled to the upper portion of the seat cage assembly 200. The cylindrical cage assembly 300 secondly reduces the pressure-reduced gas that has been firstly reduced in pressure by the seat cage assembly 200. When the secondary pressure is reduced, the pressure of the fluid of the primary pressure-reduced gas is further reduced, and the vaporization gas is re-circulated. To this end, the cylindrical cage assembly 300 includes an outer cylindrical cage 312 and at least one inner cylindrical cage 313 vertically laterally received within the outer cylindrical cage 312.

The outer cylindrical cage 312 and the inner cylindrical cage 313 have a plurality of third fluid pass holes 316 formed at equal intervals in the inner diameter direction from the outer diameter at predetermined intervals, (316) are connected to each other by fixing means such as welding with mutual misalignment so that the flow path cross-sectional area of the passage hole (316) of mutually contacting portions is reduced.

The outer cylindrical cage 312 has an upper coupling end 318 recessed along the upper periphery thereof and a lower coupling end 317 protruding along the lower periphery thereof. The lower coupling end 317 is interlockingly engaged with the upper coupling end 278 of the seat ring member 270. The innermost inner cylindrical cage 313 is formed with a stem passing hole 314 penetrating in the vertical direction. Accordingly, since the inner cylindrical cage 313 does not have a machining error in the vertical direction or a stacking error due to stacking of the disk stacked body as in the prior art, the stem 650 does not interfere with the vertical movement of the stem 650, There is an advantageous effect that it is possible to solve the problem that it easily wears or breaks due to friction between the cylindrical cages 313 or causes severe noise.

The cage spacer 400 is formed with a stem through hole 414 in the up and down direction and has a protruded lower coupling end 417 at the lower circumferential portion thereof to engage with the upper coupling end 318 of the outer cylindrical cage, And a spacer body 412 which is formed of a metal.

The cage spacer 400 may be formed by filling the space between the bonnet member 500 and the cylindrical cage assembly 300 when the bonnet member 500 to be described later is coupled to the valve body 100 to stably accommodate the cylindrical cage assembly 300 Fix and prevent flow.

The bonnet unit 500 includes a bonnet body 510 having a stem passage hole 514 formed therein and having a lower pressing part 512 protruded downward. The bonnet member 500 is inserted into the upper portion of the valve body 100 in a state where the lower pressing portion 512 contacts the upper surface of the cage spacer 400 to press the cage spacer 400 in the downward direction, And are fixedly coupled by fixing means. Accordingly, the seat cage assembly 200, the cylindrical cage assembly 300, and the cage spacer 400 are held and fixed at predetermined positions of the cage receiving portion 130 by the bonnet member 500, and unnecessary flow is prevented .

The stem and micro plug member 600 includes a rod-shaped stem 650 and a micro-plug 610 with the stem 650 extending downward.

The stem 650 is vertically moved in the vertical direction while being accommodated in the stem through holes 314, 414, and 514 by vertically moving members (not shown).

The micro plug 610 moves up and down in the micro plug through holes 234 and 274 through the vertical movement of the stem 650.

The micro plug 610 is formed at a part of the outer circumferential surface of the micro plug body 612 in which the rounding portion 613 is formed at the end of the micro plug body 612 in the both directions, An adjusting groove 614 and a second flow adjusting groove 616 are formed. By forming the two flow rate adjusting grooves 614 and 616, it is possible to control the flow rate at a specific position in the vertical direction of the micro plug 610, thereby changing the micro-opening rate as a whole. This is the main function of the valve to regulate the flow, which can be advantageously applied in the fine adjustment of the flow rate. In this embodiment, The first flow regulating groove 614 and the second flow regulating groove 616 are formed to have different opening rates.

The first flow rate regulating groove 614 is a groove in which a part of the outer periphery of the micro plug body 612 is flatly cut. The inclined groove 614a whose opening rate increases as the distance from the stem 650 increases, And a flat groove 614b which is held. The portion of the flat groove 614b does not change its opening rate by itself but changes the opening ratio of the second flow adjusting groove 616 of the corresponding height, so that the micro opening rate change as a whole occurs.

The second flow rate adjusting groove 616 is formed in the second flow rate adjusting groove 614 so that a portion of the outer circumference of the micro plug body 612 opposite to the first flow rate adjusting groove 614 is formed so as to increase the opening rate away from the stem 650, ) Home. It goes without saying that the V-cut groove can be changed into a shape such as a U-cut or a W-cut under a condition that the opening rate is increased.

The reason why the first flow rate adjusting groove 614 and the second flow rate adjusting groove 616 are formed at different vertical ratios is that the first flow rate regulating groove 614 and the second flow rate regulating groove 616 are different from each other, And the micro-plug 610, the flow velocity and the flow rate deviation may be reduced as much as possible, and the flow rate and the flow rate variation may be minimized to pass through the cylindrical cage assembly 300 ). ≪ / RTI >

Accordingly, when the micro plug 610 moves downward, the opening rate is reduced and a very fine flow path is formed between the micro plug 610 and the pick 250. Therefore, the gas that is primarily decompressed through the seat cage assembly 200 has a constant flow rate Only the minute flow rate passes through the flow path. Conversely, when the micro plug 610 moves upward, the opening ratio is increased, and a wider flow path is formed between the micro-plug 610 and the pick 250, so that the gas primarily depressurized through the seat cage assembly is more The flow rate passes through the flow path. The area of the micro flow path can be precisely increased or decreased by changing the opening ratio due to the shape of the first flow rate adjusting groove 614 and the second flow rate adjusting groove 616 through the movement of the micro plug 610 up and down, The flow rate can be adjusted.

In contrast to the present embodiment, the first flow rate adjusting groove 614 and the second flow rate adjusting groove 616 are formed in the micro plugs 614 and 616 under the condition that the opening rate is increased at least in part as the distance from the stem 650 is increased, And may be formed as a flat groove or an inclined groove formed in the same part of the outer circumference of the body 612.

Hereinafter, a method of operating the high-pressure expansion valve for re-liquefying cryogenic high-pressure gas capable of precise micro-flow control according to an embodiment of the present invention will be described in detail with reference to FIGS. 8 to 12.

FIG. 8 is a graph showing the results of the micro-flow rate control according to the change of the opening ratio between the pick-up, the stem and the micro-plug member during the depressurization process using the high-pressure expansion valve for cryogenic high- FIG. 9 is a sectional view showing a first pressure reducing process in the inner and outer sheet cages, which is a part of the high pressure differential expansion valve for re-liquefying cryogenic high pressure gas, which can control the fine flow rate according to an embodiment of the present invention. FIG. 10 is a cross-sectional view taken along line BB 'of FIG. 9, and FIG. 11 is a partially cutaway perspective view for explaining the high-pressure expansion for re-liquefaction of cryogenic high-pressure gas according to an embodiment of the present invention, A partial cutaway perspective view for explaining the second pressure reducing process in the cylindrical cage assembly, which is the sun block of the valve, 12 is a cross-sectional view cut along the line C-C 'in FIG.

8 to 10, when the cryogenic high pressure gas requiring re-injection is introduced into the valve body 100 through the inlet 110, the first fluid passage hole 216, The passage connecting groove 246 and the second fluid passing hole 236 in this order. At this time, the high-pressure gas that has passed through the first fluid passage hole 216 can not be directly introduced into the second fluid passage hole 236, but hits the outer peripheral wall of the inner seat cage body 232 and then flows along the oil passage connection groove 246 And then escapes into the inner diameter of the inner sheath body 232 through the second fluid passage hole 236. [ Accordingly, the length of the passage of the high-pressure gas is increased, the volume of the high-pressure gas is expanded, and the flow velocity is lowered, so that the primary pressure of the high-pressure gas is reduced.

The first decompressed gas flows through the micro flow path between the pick 250 and the micro plug 610 as shown in Figs. 8 and 11 and 12, and changes in the opening rate due to the change in the position of the micro plug 610 in the up- And then passes through the inner cylindrical cage 313 of the cylindrical seat cage assembly 300 and the third fluid passing hole 316 of the outer cylindrical cage 312. [ The gas that has passed through the third fluid passage hole 316 of the innermost cylindrical cage 313 is guided to the inner cylindrical cage 313 after the third fluid passage hole 316 of the innermost cylindrical cage 313 contacts the outer diameter, The first fluid pass hole 316 and the third fluid pass hole 316 of the second fluid pass hole 316 are formed in the same direction as the first fluid pass hole 316, And then sequentially moved in the same manner by the next inner cylindrical cage 313 to finally exit the third fluid passage 316 of the outer cylindrical cage 312 to the discharge section 120. Therefore, the length of the passage is increased by the third fluid holes 316, which are offset from each other, of the cylindrical seat cage assembly 300, and the volume of the first reduced pressure gas is further expanded and the flow velocity is lowered. And the re-liquefied gas is discharged through the discharging unit 120. In this case,

As described above, according to the present invention, the high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of controlling the micro-flow rate can be controlled by a high-pressure expansion valve for re-liquefying cryogenic high- It is possible to precisely align the stem and the micro-plug member 600 without interfering with each other through the structure of the decompression-reducing sheet cage assembly 200 and the cylindrical cage assembly 300, thereby facilitating the opening or closing of the micro flow path for fine flow rate control, There is an advantageous effect that there is no fear of breakage or excessive noise generation.

According to the present invention, there is provided a high-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control, comprising: a first flow rate control groove 614 and a second flow rate control groove 614, The opening or closing of the micro flow path formed between the micro flow path 616 and the pick 500 through the up and down movement of the micro plug 612 formed on a part of the outer diameter can be precisely controlled, There is an advantageous effect that control can be performed.

According to the present invention, there is provided a high pressure differential expansion valve for re-liquefying cryogenic high-pressure gas, which is capable of controlling the minute flow rate of the cigarette according to the present invention, comprising a plurality of pressure-sensitive cage assemblies 200 and a plurality of cylindrical cage assemblies 300, The pressure reduction is performed through the first and second pressure reducing processes, thereby reducing the excessive pressure difference before and after the decompression, thereby reducing the wear and noise inducing phenomenon.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, Of the right.

The present invention is a very useful invention that can be widely used in industrial fields related to storage and transportation or fuel use through re-liquefaction of cryogenic high-pressure gas such as liquefied natural gas.

100: valve body 110: inlet
120: discharging part 130: cage accommodating part
200: seat cage assembly 210: outer seat cage
212: outer seat cage body 214: inner seat cage seat
216: first fluid passage hole 230: inner sheet cage
232: Inner seat cage body 233: Lower seat part
234, 274: Micro plug passage hole 236: Second fluid passage hole
238: seat ring member engaging portion 239:
246: channel connection groove 250:
270: seat ring member 272: seat ring body
275: picking receiving groove 276: seat cage engaging groove
277: gasket coupling end
278, 318: upper coupling end 300: cylindrical cage assembly
312: outer cylindrical cage 313: inner cylindrical cage
314, 414, 514: stem passing hole 316: third fluid passing hole
317, 417: lower coupling stage
400: cage spacer 412: spacer body
500: bonnet member 510: bonnet body
512: lower pressing portion 600: stem and micro plug member
610: Micro plug 612: Micro plug body
613: Rounding unit 614: First flow rate adjusting groove
614a: inclined groove 614b: flat groove
616: second flow control groove 650: stem

Claims (3)

A valve body having an inlet portion, a discharge portion and a cage receiving portion,
An outer sheet cage in which a plurality of first fluid passing holes are formed at a predetermined interval, the first fluid passing holes passing through the inner sheet cage receiving hole from an outer diameter of the inner sheet cage receiving hole, A micro plug hole is formed which is coupled to the outer sheet cage in a state in which a part of the micro plug hole is accommodated in the inner sheet cage accommodating hole so as to have a flow path connecting groove with a predetermined spacing therebetween, A plurality of second fluid pass holes penetrating toward the plug passing hole and not positioned in a straight line with the first fluid passing hole are formed at predetermined intervals to form an inner seat cage, a seat ring member coupled to the inner seat cage, The seat cage and the seat ring member A seat cage assembly having a pick located between,
A lower portion fixedly coupled to the upper portion of the seat cage assembly and having an outer cylindrical cage and at least one inner cylindrical cage vertically laterally received within the outer cylindrical cage and having at least one inner cylindrical cage and at least one inner cylindrical cage, Wherein a plurality of third fluid passing holes are formed at predetermined intervals in the radial direction from an outer diameter of the cylindrical cage assembly, ,
A bonnet member fixedly coupled to the valve body in a state where the seat cage assembly and the cylindrical cage assembly are fixedly received in the cage accommodating portion,
A stem accommodating the inside of the seat cage assembly and the cylindrical cage assembly and adjusting a flow rate through the micro flow path by increasing or decreasing the area of the micro flow path by changing the opening ratio between the pick and the up / And a micro plug member
/ RTI >
The micro-
The first flow rate adjusting grooves and the second flow rate adjusting grooves are formed in at least a part of the outer peripheral surface of the micro plug body in the opposite direction from the stem,
High-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control. The method of claim 1,
Wherein the first flow rate adjusting groove and the second flow rate adjusting groove are formed to have different opening rates
High-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control. 3. The method according to claim 1 or 2,
The first flow control groove
An inclined groove whose opening rate increases as the distance from the stem increases and a flat groove whose opening rate is kept constant
High-pressure expansion valve for re-liquefaction of cryogenic high-pressure gas capable of precise micro-flow control.

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